錄一 :中文文獻(xiàn)  一、聯(lián)動(dòng)可能被定義為固體的，或鏈接，其中每一個(gè)環(huán)節(jié)，是連接通過引腳連接（鉸鏈）或滑動(dòng)關(guān)節(jié)至少有兩個(gè)人組合。為了滿足這一定義，必須形成一個(gè)聯(lián)動(dòng)層出不窮，或關(guān)閉，或一個(gè)封閉的鏈條鏈系列。很明顯，有許多鏈接鏈的行為從為數(shù)不多的不同。這就提出了一個(gè)非常重要的問題，關(guān)于為運(yùn)動(dòng)中的一臺(tái)機(jī)器傳輸給聯(lián)動(dòng)的適用性。這是否適當(dāng)取決于鏈接的數(shù)量和接頭數(shù)量。               二、自由度。一個(gè)三桿機(jī)構(gòu)（含連在一起的三間酒吧）顯然是一個(gè)僵化的框架，沒有相對(duì)運(yùn)動(dòng)之間的聯(lián)系是可能的。來描述一個(gè)四連桿機(jī)構(gòu)，有 必要才知道之間的任何連接兩個(gè)角度的聯(lián)系的相對(duì)位置。  （包括固定鏈接 OQ 的，在圖 5c機(jī)制四個(gè)環(huán)節(jié)，因此是一個(gè)四連桿機(jī)構(gòu)。）這種聯(lián)系是說，有一個(gè)自由度。兩個(gè)角度都必須在指定的五桿機(jī)構(gòu)的聯(lián)系的相對(duì)位置，它有兩個(gè)自由度  三、單自由度運(yùn)動(dòng)的聯(lián)系，制約，也就是說，對(duì)所有的鏈接上所有的點(diǎn)都認(rèn)為是固定的，確定的其他鏈接路徑。路徑是最容易掌握的或假設(shè)上的路徑是必要的聯(lián)系是固定的，然后移動(dòng)的方式與約束兼容其他環(huán)節(jié)的可視化。  四、四桿機(jī)構(gòu)。當(dāng)一個(gè)約束聯(lián)系的成員之一，是固定的，聯(lián)動(dòng)機(jī)制，執(zhí)行變成了機(jī)器中的一個(gè)有用的機(jī)械功能 的能力。在針腳連接聯(lián)系的輸入（驅(qū)動(dòng)器）和輸出（跟隨者）鏈接通常樞連接到固定的聯(lián)系 ;連接鏈路（耦合器）通常不投入，也沒有輸出。由于任何一個(gè)鏈接可以是固定的，如果鏈接的不同長度，四個(gè)機(jī)制，用不同的輸入輸出關(guān)系，每一個(gè)都可以得到以四桿機(jī)構(gòu)。這四個(gè)機(jī)制是說是基本的聯(lián)動(dòng)反轉(zhuǎn)。  五、當(dāng)最短的鏈接圖 11（上）是固定的，鏈接 B 和 D 可以完成革命。這就是所謂的拖鏈接機(jī)制。如果曲柄在一個(gè)恒定速度 b 旋轉(zhuǎn)，曲軸 D 將在同一方向旋轉(zhuǎn)的速度也不同。通過自身或與其他機(jī)制系列，拉桿可以提供有用的運(yùn)動(dòng)效果。在圖中，曲柄 B 是司機(jī)，在一個(gè)統(tǒng)一的旋轉(zhuǎn)速度逆時(shí)針 ;曲柄 D 掃過的角度，這是只有 50 度掃描。這意味著，曲柄 d 將曲柄移動(dòng)速度比 b 當(dāng)移動(dòng)從 B 到 B'和比  掃過的角度，這是只有 50 度掃描。這意味著，曲柄 d 將曲柄移動(dòng)速度比 b 當(dāng)移動(dòng)從 B 到 B'和比 B 更 快速移動(dòng)時(shí)來自 B 到 B 如果曲柄 D 組附加到一個(gè)沙在包裝機(jī)英尺，例如，其議案，這與一些升油墨的比例幾乎是停頓或停留，緩慢的部分可利用的，必須在一個(gè)緩慢的速度進(jìn)行執(zhí)行操作。  六、四桿機(jī)構(gòu)第二反演得到利用最短的鏈接作為司機(jī)。如圖（下），連一個(gè)可以顯示完整的革命，而對(duì)面的鏈接，這可能是為 B， C 或 D，只能通過振蕩角。這就是所謂的曲柄搖桿機(jī)構(gòu)，它是產(chǎn)生振蕩運(yùn)動(dòng)有快速回報(bào)的行動(dòng)裝置，結(jié)合有用的結(jié)果的事實(shí)，對(duì)于逆時(shí)針旋轉(zhuǎn)的，振蕩的 C 從 B 到 B 的對(duì)應(yīng)角 1，而從 B'to 乙振蕩對(duì)應(yīng) angle 2。由于曲軸在一個(gè)恒定的速度 旋轉(zhuǎn)， 1 較大 than 2，搖臂將需要更長的時(shí)間由右擺動(dòng)比其他的方式離開了。機(jī)器上做有益的工作只有在活躍的成員是在一個(gè)方向移動(dòng)，快速回裝置的成員迅速返回其初始位置。  七、在極端的立場所示，虛線在圖（下），曲柄和連桿一個(gè)鏈路 B 一字排開（共線），如果 C 組的搖桿驅(qū)動(dòng)程序，意味著將要進(jìn)行的追隨者提供鏈接過去這些死的立場。在腳踏式磨石腳踏板連接，連接 C 和砂輪軸連接答磨刀石的角動(dòng)量是利用過去的死進(jìn)行位置的鏈接。  八、在四桿機(jī)構(gòu)，最短的鏈接是第三反演耦合器，以及其他運(yùn)動(dòng)的聯(lián)系只能振蕩。這就是所謂的雙搖桿機(jī)構(gòu)。  九、機(jī)構(gòu) 綜合。圖形和分析方法，可以很容易地確定聘用的位移，速度，以及在一個(gè)聯(lián)動(dòng)機(jī)制的聯(lián)系加速。設(shè)計(jì)，或綜合的聯(lián)系，以滿足特定的要求是要困難得多。沒有設(shè)計(jì)一個(gè)拖放鏈接機(jī)制，以滿足輸入與輸出關(guān)系給予頻譜已知的方法。認(rèn)為做的最好的表現(xiàn)是調(diào)查一個(gè)特定的配置所選號(hào)碼的特點(diǎn)，并挑選了最佳。  十、在曲柄搖桿機(jī)構(gòu)的設(shè)計(jì)人員可以控制的搖桿和振蕩，角度在一定程度上的快速回報(bào)率。曲柄搖桿位移，速度，和加速度不能關(guān)聯(lián)  十一、如果在一個(gè)四桿機(jī)構(gòu)的曲柄，總要在相同或旋轉(zhuǎn)方向相反，如果他們輪換限于大大低于 180 度，它可能會(huì)關(guān)聯(lián)曲柄在三，四輪換， 五，或即使是大量的職位。這兩種方法的分析和圖形制作提供的相關(guān)性   十二、圖 12（左）顯示了函數(shù)發(fā)生器，相關(guān)的曲柄旋轉(zhuǎn) b 在與旋轉(zhuǎn) 60 度以上 D 系列曲軸 70 度的范圍。這樣的相關(guān)關(guān)系，以滿足與 X 為Y = X2 的不同 從 1 到 6 和 Y 從 1 到 36。  b 的曲柄轉(zhuǎn)動(dòng)的機(jī)械模擬 X 的，而旋轉(zhuǎn)曲柄 D 是 Y的模擬 X 和 Y之間的關(guān)系是準(zhǔn)確的在 X= 1.19， 2.54， 4.46，和5.81;在它是錯(cuò)誤的，但這個(gè)錯(cuò)誤已經(jīng)被最小化的其他職位上述精確點(diǎn)多的間距。  十三、函數(shù)發(fā)生器不是通常用來表示兩個(gè)功能相關(guān)的變量，如 X 和 Y在圖12（左）所示的規(guī)模通常不提供相應(yīng)的值，他們已被添加到帶出一個(gè)最重要特征函數(shù)發(fā)生器，即規(guī)模是統(tǒng)一的，也就是說，在平等的師畢業(yè)。這意味著，由于為 70 度，而 Y范圍為 35，每兩個(gè)度旋轉(zhuǎn)曲柄 對(duì)應(yīng)一個(gè) Y的單位，如果 D是用來操作響應(yīng) B 信號(hào) 從一個(gè)閥門，相應(yīng)的三維旋轉(zhuǎn)到一個(gè)給定的 Y的變化是在同一個(gè)范圍內(nèi)的所有點(diǎn)。  十四、曲柄滑塊倒置。當(dāng)在一個(gè)四桿機(jī)構(gòu)的引腳連接都是由一名滑動(dòng)聯(lián)合取代，一個(gè)有用的一些機(jī)制，可從產(chǎn)生的聯(lián)系。在圖 13（上）之間的聯(lián)系 1 和 4是一個(gè)滑動(dòng)的接縫，允許 4 座，在幻燈片中鏈接的插槽連接 1。這將不作任何區(qū)別，運(yùn)動(dòng)學(xué)，如果鏈路是在一個(gè) 4 孔或槽滑動(dòng)鏈接 1。  十五、如果鏈接圖 13（上） 1 是固定的，由此產(chǎn)生的曲柄滑塊機(jī)構(gòu)如圖 13（中心）。這是一個(gè)往復(fù)引擎機(jī)制。該塊 4 代表活塞 ;鏈接 1 所示，陰影，是塊，它包含在 A 和汽缸的曲軸軸承 ;鏈接 2 是曲軸與 連桿連接 3。偏軸軸承是在 B 點(diǎn)，在三腕銷軸承活塞的行程兩次 AB 公司，扔的曲柄。   十六、曲柄滑塊機(jī)構(gòu)提供的手段轉(zhuǎn)換成曲軸的，或在一臺(tái)泵曲軸的旋轉(zhuǎn)運(yùn)動(dòng)，旋轉(zhuǎn)運(yùn)動(dòng)的活塞的運(yùn)動(dòng)用在往復(fù)式發(fā)動(dòng)機(jī)活塞成一個(gè)移動(dòng)式的議案。在圖13（中心），當(dāng) B 在位置 B'時(shí)，會(huì)干擾連桿曲柄如果兩個(gè)人在同一平面上。這個(gè)問題解決了發(fā)動(dòng)機(jī)和水泵來抵消從曲軸軸承曲柄銷軸承。通過使用一個(gè)地方的偏心和連桿機(jī)構(gòu)曲柄，沒有補(bǔ)償是必要的和非常小的拋出可以得到。  十七、在圖 13（下）在 B 點(diǎn)的偏軸軸承已成為一個(gè)巨大的圓形磁盤在 A 無所不能帶有偏心或扔 AB 型。連桿偏心桿，已成為一個(gè)帶的環(huán)繞和偏心幻燈片。在中部和底部圖圖 13 運(yùn)動(dòng)學(xué)等效的機(jī)制。通過固定鏈接 2， 3， 4 而不是鏈接 1，在圖 13 個(gè)連鎖有其他倒（上）獲得。  十八、空間聯(lián)系。所考慮的聯(lián)系，到目前為止已全部平面，也就是說， 它們的運(yùn)動(dòng)一直局限在單一的平面或平行平面和軸平行，他們就可以了?？臻g之間的聯(lián)系在三個(gè)層面，用于非平行軸之間傳遞運(yùn)動(dòng)。雖然一些使用多年的著名空間聯(lián)動(dòng)機(jī)制是特殊形式的聯(lián)系，但直到 20 世紀(jì) 50 年代的約 kinematicians 發(fā)展成為嚴(yán)重的描述，分析和綜合這些聯(lián)系程序感興趣。雖然在這一領(lǐng)域取得了一些進(jìn)展，許多問題仍未解決。  十九、而一個(gè)平面連桿，或許可以用一個(gè)二維繪圖和分析，并與平面的幾何結(jié)構(gòu)合成的，這不是一個(gè)空間的聯(lián)系成為可能。至少有兩種觀點(diǎn)都是需要定義在三維空間的鏈接和其他方面復(fù)雜的速度和加速度分析。因此，空 間聯(lián)系的分析涉及到高等數(shù)學(xué)的使用。  二十、在平面上的聯(lián)系，只有兩種類型的連接器或接縫，即針或關(guān)節(jié)鉸鏈和滑動(dòng)接頭（ crossheads）。由于需要 2 個(gè)元素，使聯(lián)合， kinematicians 稱之為運(yùn)動(dòng)“對(duì)?！耙虼?，一針聯(lián)合是一個(gè)旋轉(zhuǎn)，或把對(duì)和一個(gè)滑動(dòng)的接縫，是一個(gè)移動(dòng)副。在空間上的聯(lián)系還有另外一些對(duì)，即一對(duì)圓筒，它允許兩個(gè)相對(duì)平移和旋轉(zhuǎn)，螺旋對(duì)（螺絲和螺母），以及球形對(duì)（球窩關(guān)節(jié)）。   附錄 1:英文文獻(xiàn)  Linkages(連桿機(jī)構(gòu) ) 1  A linkage may be defined as an assemblage of solid bodies, or links, in which each link is connected to at least two others by pin connections (hinges) or sliding joints. To satisfy this definition, a linkage must form an endless, or closed, chain or a series of closed chains. It is obvious that a chain with many links will behave differently from one with few. This raises the vitally important question regarding the suitability of a given linkage for the transmission of motion in a machine. This suitability depends on the number of links and the number of joints. 2  Degrees of freedom. A three-bar linkage (containing three bars linked together) is obviously a rigid frame; no relative motion between the links is possible. To describe the relative positions of the links in a four-bar linkage it is necessary only to know the angle between any two of the links. (Including the fixed link OQ, the mechanism in Figure 5C has four links and is thus a four-bar linkage.) This linkage is said to have one degree of freedom. Two angles are required to specify the relative positions of the links in a five-bar linkage; it has two degrees of freedom. 3  Linkages with one degree of freedom have constrained motion; i.e., all points on all of the links have paths on the other links that are fixed and determinate. The paths are most easily obtained or visualized by assuming that the link on which the paths are required is fixed, and then moving the other links in a manner compatible with the constraints. 4  Four-bar mechanisms. When one of the members of a constrained linkage is fixed, the linkage becomes a mechanism capable of performing a useful mechanical function in a machine. On pin-connected linkages the input (driver) and output (follower) links are usually pivotally connected to the fixed link; the connecting links (couplers) are usually neither inputs nor outputs. Since any of the links can be fixed, if the links are of different lengths, four mechanisms, each with a different input-output relationship, can be obtained with a four-bar linkage. These four mechanisms are said to be inversions of the basic linkage. 5  When the shortest link a in Figure 11 (top) is fixed, links b and d can make complete revolutions. This is known as a drag-link mechanism. If crank b rotates at a constant speed, the crank d will rotate in the same direction at a varying speed. By itself, or in series with other mechanisms, the drag link can provide useful kinematic effects. In the figure, crank b is the driver, rotating counterclockwise at a uniform rate; crank d is the follower. Both cranks make a complete revolution in the same time, but while b sweeps out the angle , which is 150 degrees the follower d sweeps out the angle , which is only 50 degrees. This means that crank d will move more slowly than crank b when moving from B to B and more quickly than b when moving from B to B. If crank d were attached to a sha ft in a packaging machine, for example, the slow part of its motion, which with some l ink proportions is almost a pause or a dwell, could be utilized for performing operations that must be done at a slow speed.  6  The second inversion of the four-bar mechanism is obtained by using the shortest link a as the driver. As shown in Figure (bottom), link a can make complete revolutions while the opposite link, which may be either b, c, or d, can only oscillate through the angle . This is called the crank-rocker mechanism; it is a useful device for producing oscillatory motion combined with a quick-return action that results from the fact that for counter-clockwise rotation of a, the oscillation of c from B to B corresponds with angle 1 , while oscillati on from Bto B corresponds with angle2 . Since crank a rotates at a constant speed and 1 is greater than2 , the rocker will take longer to swing from right to left than the other way. On machines that do useful work only when the active members are moving in one direction, quick-return devices return the members quickly to their initial position. 7  In the extreme positions, shown dotted in Figure (bottom), the crank a and the coupler link b are lined up (collinear), and if the rocker c were the driver, means would have to be provided to carry the follower link a past these dead positions. On foot-operated grindstones the foot pedal is attached to link c and the grindstone shaft to link a. The angular momentum of the grindstone is utilized to carry the links past the dead positions. 8  On the third inversion of the four-bar mechanism, the shortest link a is the coupler; and the other moving links can only oscillate. This is called the double-rocker mechanism. 9  Linkage synthesis. Graphical and analytical methods can be readily employed for determining the displacement, velocity, and acceleration of the links in a linkage mechanism. The design, or synthesis, of linkages to satisfy specific requirements is much more difficult. There is no known method for designing a drag-link mechanism to satisfy a given spectrum of input-output relationships. The best that can be done is to survey the performance characteristics of a selected number of specific configurations and pick the optimum. 10  On the crank-rocker mechanism the designer can control the angle of oscillation of the rocker and, to a degree, the quick-return ratio. The crank and rocker displacements, velocities, and accelerations cannot be correlated. 11  If the cranks in a four-bar mechanism always rotate in the same or in opposite directions, and if their rotations are limited to considerably less than 180 degrees, it may be possible to correlate the crank rotations in three, four, five, or even a larger number of positions. Both analytic and graphic methods are available for making the correlations. 12  Figure 12 (left) shows a function generator that correlates the rotation of crank b  over a 60-degree range with the rotation of crank d over a 70-degree range. The correlation is such as to satisfy the relationship Y=X2, with X varying from 1 to 6 and Y from 1 to 36. The rotation of crank b is the mechanical analogue of X, while the rotation of crank d is the analogue of Y. The relation between X and Y is accurate at X=1.19, 2.54, 4.46, and 5.81; at other positions it is in error, but the error has been minimized by the odd spacing of the above precision points.  13  A function generator is not ordinarily used to indicate corresponding values of two functionally related variables such as X and Y. The scales shown in Figure 12 (left) are not usually provided; they have been added to bring out the most important feature of a function generator, namely, that the scales are uniform; i.e., graduated in equal divisions. This means that, since is 70 degrees and the range of Y is 35, each two-degree rotation of crank d corresponds with one unit of Y, and if d is used to operate a valve in response to a signal from b, the rotation of d corresponding to a given change in Y is the same at all points in the range. 14  Slider-crank inversions. When one of the pin connections in a four-bar linkage is replaced by a sliding joint, a number of useful mechanisms can be obtained from the resulting linkage. In Figure 13 (top) the connection between links 1 and 4 is a sliding joint that permits block 4 to slide in the slot in link 1. It would make no difference, kinematically, if link 4 were sliding in a hole or slot in link 1. 15  If link 1 in Figure 13 (top) is fixed, the resulting slider-crank mechanism is shown in Figure 13 (center). This is the mechanism of a reciprocating engine. The block 4 represents the piston; link 1, shown shaded, is the block that contains the crankshaft bearing at A and the cylinder; link 2 is the crankshaft and link 3 the connecting rod. The crankpin bearing is at B, the wrist pin bearing at C. The stroke of the piston is twice AB, the throw of the crank.  16  The slider-crank mechanism provides means for converting the translatory motion of the pistons in a reciprocating engine into rotary motion of the crankshaft, or the rotary motion of the crankshaft in a pump into a translatory motion of the pistons. In Figure 13 (center), when B is in position B, the connecting rod would interfere with the crank if  both were in the same plane. This problem is solved in engines and pumps by offsetting the crankpin bearing from the crankshaft bearing. By using an eccentric-and-rod mechanism in place of a crank, no offsetting is necessary and very small throws can be obtained. 17  In Figure 13 (bottom) the crankpin bearing at B has become a large circular disk pivoted at A with an eccentricity or throw AB. The connecting rod has become the eccentric rod with a strap that encircles and slides on the eccentric. The mechanisms in the center and bottom drawings of Figure 13 are kinematically equivalent. By fixing links 2, 3, and 4 instead of link 1, there other inversions of the linkage in Figure 13 (top) are obtained.  18  Space linkages. All of the linkages considered so far have been planar; i.e., their motions have been confined to a single plane or to parallel planes, and the shafts they connect have