200923197 九、發明說明： 【發明所屬之技術領域】 本發明係關於—種提高輸㈣㈣㈣產生裝置，特別 是指-種在有限空間下’減少側向分力㈣，增進輸出功 率’具有低轉速、高扭力’以及減少震動的動能產生裝置。 【先前技術】 傅統的引擎運作模式如圖二十三所示，當汽缸燃燒時，200923197 IX. Description of the Invention: [Technical Field] The present invention relates to a device for improving the transmission of (four) (four) (four), in particular, to reduce the lateral component (4) in a limited space, and to increase the output power 'with a low rotational speed, High torque 'and kinetic energy generation device that reduces vibration. [Prior Art] The engine operating mode of Fu Tong is shown in Figure 23. When the cylinder is burning,
係由》飞知活塞χ;1推動—傳動^丰趣· it 得動件U帶動曲柄軸x3旋轉以產逢 動能輸出。但以傳動件x2而言，由於傳動件^的活動方令 具有相當大的側壓角度’故產生相當大的側向分力，造成智 體動能的損耗；另夕卜’傳統引擎在上死點時，其施力點X 與曲柄軸X3的慣性力量會相互抵消’不僅造成動能的損耗’ 更會弓丨起震盪現象，導致引擎損壞，壽命減短❶ 再者，傳統的引擎每-次行程必須經過進氣、壓縮、爆 炸、排氣四項動作，此時曲柄已繞輸出軸轉動兩圈，即每二 爆炸行程必須推動引擎輸出兩轉，故輸出扭力較低，因此引 擎必須提高轉速，或是加大汽缸容量’方可提供較大的扭力 給引擎使用。 二十四所示之美國專 偏心輪8上，該偏心 利 坊間有許多引擎的改良方案，如圖 US4，044，629，其曲柄軸5套置在— 輪8則在外齒輪7中，當外齒輪7嚙合内齒輪15轉動時 藉由偏心輪8可修正軸心6的施力方向，以裎古 J以提间Μ擎效能 200923197 又如圖一十五之美國專利us 4,〇73，196，复 ± ，、肀曲柄軸26以 一懸# 40a連接一外齒輪43a繞行内齒輪 轉動，再由外 齒輪轴心37進行動能傳輸，藉由懸臂4〇& ^ , 蹩輛心3?的施 力方向，以提高引擎效能。 唯前述兩件習知技術仍無法完全解決傳統弓I擎的側壓 損耗與震㈣缺點。故其汽缸每—次爆炸仍須帶動引擎 輸出兩轉’使該引擎轉速、體積無法縮減 ， 饰出的扭力仍 f) 然偏低。 另外，針對結構與引擎近似的「空壓機」結構，如圖二 十六A所示台灣專利證號〇623〇5的，，一種汽虹活塞每上下一 次可暫停一次的構造”之結構圖，圖二 β為相似專利之 動作圖’其具有一殼套5，該殼套5内緣設置有-内齒輪3, 該内齒輪3上嚙合有一外齒輪2 ’該外齒輪2上連接有一副 曲轴卜該副曲轴1 一端則連接有活塞與連桿6,而外齒輪田2 b U下軸12穿置在主曲軸4傳遞動能輸出，藉由内齒輪3 .與外齒輪2的轉動互補作用，得到活塞與連桿6上下一次可 暫分一次的構造，增加進氣儲能。 唯根據本㈣明人詳測之結果’前述空壓機結構僅為理 論設計’而欠缺實際測試，如本案發明人根據圖二十六a、 圖一十’、B所導出之軌跡圖二十六c，其中軌跡線⑽即表現 該圖二十六A的實際軌跡’點pl(三角形）是圖二十六A外齒 200923197 輪2繞行内齒輪3圓周18D。的施力點Α位置，點Μ則為· 。的施力點Α位置，事實顯示，該空壓機結構的執跡線以在 點P卜P3仍有未完行程，即點pl並非施力點a最低的位置， 而是在240。時的點p2(四方形）位置。換言之該空壓機結 構的活塞與連桿6们【〜删。的儲能過程，仍有上下動作， 並非如圖二十六"間三個圖例所表現平衡的儲能狀態。實It is driven by the "flying piston"; 1 push - transmission ^ Fengqu · it The moving part U drives the crank shaft x3 to rotate to produce kinetic energy output. However, in the case of the transmission member x2, since the movement of the transmission member has a considerable lateral pressure angle, a considerable lateral component force is generated, resulting in loss of intellectual kinetic energy. In addition, the conventional engine is dead. When the point is applied, the inertial force of the force point X and the crankshaft X3 will cancel each other 'not only the loss of kinetic energy', but also the shock phenomenon, resulting in engine damage and shortened life. Furthermore, the traditional engine every time The stroke must pass four actions of intake, compression, explosion and exhaust. At this time, the crank has been rotated twice around the output shaft, that is, every two explosion strokes must push the engine output for two revolutions, so the output torque is low, so the engine must increase the speed. Or increase the cylinder capacity to provide greater torque for the engine. On the American eccentric wheel 8 shown in the twenty-fourth, there are many engine improvement schemes in the eccentric plaque, as shown in Fig. 4, 044, 629, the crankshaft 5 is placed on the wheel 8 in the external gear 7, when When the gear 7 meshes with the internal gear 15 and rotates, the eccentric wheel 8 can correct the direction of the force applied to the shaft 6 to make the performance of the core 6200923197 and the US patent us 4, 〇73, 196 as shown in FIG. The complex crankshaft 26 is connected by a suspension #40a to an external gear 43a for rotation around the inner gear, and then the external gear shaft 37 performs kinetic energy transmission, by means of the cantilever 4〇&^, the center of the car 3? The direction of the force to improve engine performance. Only the two conventional techniques described above still cannot completely solve the side pressure loss and the shock (4) of the traditional bow engine. Therefore, every cylinder of the cylinder still needs to drive the engine to output two revolutions, so that the engine speed and volume cannot be reduced, and the torque is still f). In addition, the structure of the "air compressor" similar to the structure and engine, as shown in Figure 26A, Taiwan Patent No. 〇623〇5, a structure of a structure in which a steam-red piston can be suspended once and for all. Fig. 2 is a similar patent action diagram 'having a casing 5, the inner edge of the casing 5 is provided with an internal gear 3, and the internal gear 3 is meshed with an external gear 2' The crankshaft has a piston and a connecting rod 6 connected to one end of the auxiliary crankshaft 1 , and the outer gear shaft 2 b U lower shaft 12 passes through the main crankshaft 4 to transmit a kinetic energy output, and the internal gear 3 complements the rotation of the external gear 2 . The structure that the piston and the connecting rod 6 can be temporarily divided once and once is obtained, and the energy storage of the intake air is increased. Only according to the result of the detailed test of the above (four), the air compressor structure is only theoretical design, and the actual test is lacking, such as the present case. The inventor according to Fig. 26a, Fig. 10', B derived trajectory map twenty-six c, wherein the trajectory line (10) is the actual trajectory of the figure 26A' point pl (triangle) is Figure twenty Six A external teeth 200923197 Wheel 2 around the inner gear 3 circumference 18D. , the point is the position of the force application point, the fact that the structure of the air compressor structure is still at the point P P3 still has not completed the journey, that is, the point pl is not the lowest position of the force point a, and It is the position of p2 (quadruple) at 240. In other words, the piston and connecting rod of the air compressor structure [~ delete the energy storage process, there is still up and down movement, not as shown in Figure 26] The equilibrium energy storage state of the three legends.
Ο 際上’該圖二十六A中間三個圖例的活塞與連桿6並非等 長，否則無法顯示三組活塞與連桿6在同一水平高度的假 象。因此’該空壓機結構在刚_。的運行過程中仍有耗 能，而無法達成所需的提高儲能功率。 再者’該活塞與連桿6完成—次上下行程時，該外齒輪 2需繞行内齒輪3兩周’但事實上，由於内齒輪3與外齒輪 2的比例’該外齒輪2本身已轉動三周。即外齒輪2自轉三 周方能完成—次儲能動作，其過程仍屬耗能，無法達到預期 的提馬儲能功效。 另外，本案發明人進一步研究，其中軌跡線dl為施力 點A下降之設計，而軌跡線d3〜d4則為施力點a上移的設計， 因此圖二十六C共產生四條軌跡線d卜d4。我們發現，無論 何種設計，其預設最低位置‘點Pi t在同一水平線上，而實 際最低點P2則根據施力點a的位置而有所調整，即該空壓 機結構進行「空壓機每轉動兩周方能加壓儲能一次」的專利 200923197 特欲時’仍會產生動能的損耗。故，該空壓機結構無法提高 有效儲能，而為不成熟的設計。 如圖二十七A、B、C所示’該參考案1具有一軸心齒 輪31、一施力軸51，以及一固定齒輪2和一活動齒輪3的 一嚙合點9二處關鍵點，且固定齒輪2和活動齒輪3的齒輪 比為3 : 2 ;當一活塞7爆炸動能經一連桿6加壓於該施力軸 .51時，其慣量包括由該施力軸51向該軸心齒輪31方向施壓 ( ' (施力線〇 1 )，以及該嚙合點9反作用力向該軸心齒輪3 1方 向施壓（施力線02)疊加形成，其疊加後的力量並經由該軸心 齒輪31向傳動軸齒輪42方向輪出（施力線〇3)，故輸出的力 量遠大於習知結構。而該施力線〇1與施力線〇2之間自然形 成有一夾角，藉由槓桿原理得將力量疊加，亦避免動能損耗。 而該引證1的該連桿6側壓角度變化非常小，使大部份 慣量可作為推動該活動齒輪3與一飛輪5旋轉的動力，減少 側向分力的浪費，該活動齒輪3與該飛輪5係朝反方向轉動， 形成該施力袖51的軌跡線a形狀。 唯該引證1的力量配置尚有改善空間，其最主要問題如 圖二十七c所示，其系統運轉時，僅由固定齒輪2和活動齒 輪3的嚙合方式維持穩定’由於齒輪間的餘隙以及運轉方 式，此响合固定方法相當不穩’可能產生震動箅又接— 别号+穩定的因 素，影響系統精密度以及使用壽命。另者，因該連桿β所直 200923197 接加壓的施力線(Π短於反作用力的施力線〇2,若能加大該 施力線(Π的幅度，則輪出力量可得到更大的效能。況且， 該施力線03的長度短於施力線〇2，根據槓桿原理，該施力 線〇2必須提供更大的力量，方能維持傳動軸齒輪仏的有效 輸出’使其動力輸出效能降低。 另外，又如申凊人另一國際專利pcT/CN2〇〇6/〇〇2i〇6之「動 at·產生專置」專利案（參考案2) ’其藉由結構改良，同樣提供 另一種習用缺失的解決方案。 戈圖一十八A、B所示，該參考案2具有一傳動軸42、 施力轴5卜以及-固定齒輪2和一活動齒輪3的喷合點9 三處關鍵點，且固定齒輪2和活動齒輪3的齒輪比為3 : 2; ‘活塞％爆炸動敗•經—連桿6加壓於該施力軸51時，其慣 量包括由該施力軸51向該傳動軸42方向施壓（施力線01)， 以及由3亥口齒合，點9反作用力向該傳動車由42方向施壓（施力線 2)疊加’其疊加後的力量並經由該傳動件*向該傳動轴 方向輸出（施力線03)，故輸出的力量遠大於習知結構；而該 施力線01與&力、線〇2之間自然形成一爽角，以利藉由横桿 原理將力量疊加’藉由槓桿原理得將力量疊加，亦避免動能 損耗。 藉由則述結構，當該活塞7a爆炸時，其動能經該連桿6 加壓於该施力軸51上，而該連桿6的側壓角度變化非常小， 200923197 使大部份慣量可作為推動該活動齒輪3與-飛輪5旋轉的動 力，減少側向分力的浪費；當該活動齒輪3繞行該固定齒輪 2轉動時，該活動齒輪3與該飛輪5係朝反方向轉動，使該施 力軸51形成執跡線a的形狀。 同樣也4引《且2在系統運轉時，僅由齒輪喃合方式維 持穩定’使系統運轉時可能產生震動等不穩定的因素，影響 系統精密度以及使用壽命；而該引證2由連桿6所直接加: 的施力線01短於反作用力的施力線。2,若能加大該施力線 。1的幅度’則輸出力量可得到更大的效能。再者，該施力線 〇3的長度短於施力線02，故該施力線〇2必須提供更大的力 量，方能維持傳動轴42的有效輸出，使其動力輸出效能仍 會b偏低。 尚 案 而發明人再接再厲，經由前述發明經驗繼續 有其它解決之道’可為動能產生裝置提供最 研究，發現 佳的改良方 【發明内容】 本發蚊主要目的即在於提供_種提高輸出 月b產线置，其爆炸行程密集，可在較低的轉速下得到較= 的輸出功率，形成低轉速、高扭力的結構。 门 本發明之另一目的即在於提供— 月匕產生裝置，其施力轴慣量角度變 動 罕乂！，減少震盪 200923197 損耗，提高動能輪出。 捉向輸出功率的動 ^產生裝置’其藉由内外套合方式 動 π负丨良工間内配置最夕 的汽缸，使其整體輸出動能大增。 夕 本發明之下一 能產生裝置，其適 結構或其它動力機 目的即在於提供_ 種提高輪出功率 用於各種立式、臥式弓丨擎 械0 的動 甚至於空壓機The pistons of the three figures in the middle of the figure 26A are not equal in length to the connecting rod 6, otherwise the three groups of pistons and the connecting rod 6 at the same level cannot be displayed. Therefore, the air compressor structure is just _. There is still energy in the operation, and the required energy storage power cannot be achieved. Furthermore, when the piston and the connecting rod 6 are completed - the upper and lower strokes, the external gear 2 needs to bypass the inner gear 3 for two weeks'. However, due to the ratio of the internal gear 3 to the external gear 2, the external gear 2 itself has Turn for three weeks. That is to say, the external gear 2 can be completed for three weeks to complete the energy storage operation, and the process is still energy-consuming and cannot achieve the expected energy storage effect of the horse. In addition, the inventor of the present invention further studied that the trajectory line dl is a design in which the force point A is lowered, and the trajectory lines d3 to d4 are the design in which the force point a is moved upward, so that the figure 26 C generates four track lines d. Bu d4. We found that, regardless of the design, the preset minimum position 'point Pi t is on the same horizontal line, and the actual lowest point P2 is adjusted according to the position of the force application point a, that is, the air compressor structure performs "air pressure" The patent 200923197, which is capable of pressurizing and storing energy once every two revolutions of the machine, still produces kinetic energy loss. Therefore, the air compressor structure cannot improve the effective energy storage, but is an immature design. As shown in FIG. 27A, B, and C, the reference 1 has a pivot gear 31, a force applying shaft 51, and a key point of a meshing point 9 of a fixed gear 2 and a movable gear 3, And the gear ratio of the fixed gear 2 and the movable gear 3 is 3:2; when the explosive kinetic energy of a piston 7 is pressurized to the urging shaft .51 via a connecting rod 6, the inertia thereof includes the urging shaft 51 to the shaft gear Pressing in the direction of 31 ( ' (force line 〇 1 ), and the reaction force of the meshing point 9 is superposed on the direction of the shaft gear 3 1 (the force line 02), and the superimposed force passes through the axis The gear 31 rotates in the direction of the transmission shaft gear 42 (the force application line 〇3), so the output force is much larger than the conventional structure, and the urging line 〇1 and the urging line 自然2 naturally form an angle with the lever The principle is to superimpose the force and avoid the kinetic energy loss. The change of the lateral pressure angle of the connecting rod 6 of the reference 1 is very small, so that most of the inertia can be used as the driving force for rotating the movable gear 3 and the flywheel 5, reducing the lateral direction. The waste of the component force, the movable gear 3 and the flywheel 5 are rotated in opposite directions to form the rail of the force sleeve 51 The shape of the line a. Only the power configuration of the reference 1 has room for improvement, and the most important problem is shown in Figure 27 c. When the system is in operation, only the meshing manner of the fixed gear 2 and the movable gear 3 is maintained stable due to The clearance between the gears and the way of operation, the fixing method is quite unstable, which may cause vibration and connection. The other factors are stable and affect the precision and service life of the system. 200923197 Connected to the applied force line (Π is shorter than the force applied line 〇2, if you can increase the force line (the amplitude of the Π, the wheel force can get more performance. Moreover, the force line 03 The length is shorter than the force line 〇2. According to the principle of the lever, the force line 〇2 must provide more force to maintain the effective output of the drive shaft gear ' to reduce its power output performance. Another international patent, pcT/CN2〇〇6/〇〇2i〇6, is a patent application (Reference 2). It also provides another solution for the lack of use by structural improvement. This figure is shown in Figure 18A and B. The test case 2 has a transmission shaft 42, a force applying shaft 5, and three key points of the injection point 9 of the fixed gear 2 and a movable gear 3, and the gear ratio of the fixed gear 2 and the movable gear 3 is 3:2; When the piston 6 is pressed against the urging shaft 51, the inertia thereof is pressed by the urging shaft 51 toward the transmission shaft 42 (the force applying line 01), and the gear is engaged by 3 laps. Point 9 reaction force is applied to the transmission vehicle from the direction of 42 (the force application line 2) to superimpose the superimposed force and output to the transmission shaft direction via the transmission member* (the force application line 03), so the output force is large In the conventional structure; and the force line 01 and the & force, the line 自然 2 naturally form a cool angle, in order to superimpose the force by the principle of the crossbar 'to superimpose the force by the principle of the lever, and also to avoid kinetic energy loss . By the structure, when the piston 7a explodes, its kinetic energy is pressurized to the urging shaft 51 via the connecting rod 6, and the lateral pressure angle of the connecting rod 6 changes very little, and 200923197 makes most of the inertia available. As a driving force for rotating the movable gear 3 and the flywheel 5, the waste of the lateral component is reduced; when the movable gear 3 rotates around the fixed gear 2, the movable gear 3 and the flywheel 5 rotate in opposite directions. The force applying shaft 51 is formed into the shape of the stub line a. The same is also referred to as "and 2 when the system is running, only the gear is tempered to maintain stability" so that the system may generate vibration and other unstable factors, affecting the system precision and service life; and the reference 2 by the connecting rod 6 The direct applied force line 01 is shorter than the force applied line of the reaction force. 2. If you can increase the force line. The magnitude of 1 'outputs power for greater performance. Moreover, the length of the urging line 〇3 is shorter than the urging line 02, so the urging line 必须2 must provide more force to maintain the effective output of the transmission shaft 42 so that the power output performance is still low. . The inventor has continued to work hard and continue to have other solutions through the aforementioned invention experience. 'The most research can be provided for the kinetic energy generating device, and the best improvement is found. [Inventive content] The main purpose of the mosquito is to provide an increase in output month b. The production line is dense, and the explosion stroke is dense, and the output power of the lower = can be obtained at a lower rotation speed, forming a structure with low rotation speed and high torque. Door Another object of the present invention is to provide a lunar raft generating device whose urging axis inertia angle is changed! , reduce shocks 200923197 Loss, improve kinetic energy rotation. The generator generating device that captures the output power is moved by the inner casing to move the π negative cylinder into the innermost cylinder, so that the overall output kinetic energy is greatly increased. The present invention can produce a device, and its suitable structure or other power machine is to provide an increase in wheel power for various vertical and horizontal bowing engines 0 or even air compressors.
〇 種提咼輸出功率的動 多角度、多軌跡線分 本發明之又一目的即在於提供— 能產生裝置，其汽缸配置可為多汽缸、 別運轉，使其輸出總力大增。 可達成別述目的之提高輸出功率的動能產生裝置，包括 有一機殼，該機殼-側《有1定齒輪，該时齒輪齒形 朝内，相對在該較齒輪内側設置有—活動齒輪，該活動齒 輪齒形向夕卜，使該固定齒輪與活動齒輪可相互嚙合傳動，且 忒固定齒輪與活動齒輪的齒輪比為3:1;在該機殼内部樞設有 -傳動件’該傳動件與機殼之間配置有波司（Bush)，並由該 傳動件由活動齒輪帶動旋轉，經延伸_輸出軸以輸出動力； 而活動齒輪外側固定連接有一飛輪，使該飛輪與活動齒輪同 步轉動°亥飛輪一端設置有施力軸，該施力軸上軸設有連 桿，該連桿一端軸設在飛輪施力軸上，其另一端則軸設在汽 缸的活塞上，藉此，當該汽缸内部爆炸時，令活塞在汽缸壁 200923197 上往復運動，其動力經由連桿帶動飛輪與活動齒輪旋轉，以 進行動能輸出。由於該波司結構的設計，使傳動件與機殼的 結合更為穩定’可承受高迷旋轉的壓力而不震動，維持產口 的正常動能輸出與穩定性；而由連桿加壓的施力線強度大巾: 增加，連帶使輸出動力較先前技術更為優異；同時，在本^ 明的結構特性下，各汽去广 + 订程在同一時間會同時向輸出軸中 •心'方向推進或遠離，故各汽虹的配重（飛輪）在任—時間皆能 D 互相維持平衡’減少震盪與動力損耗。 【實施方式】 請參閱圖二至圖六所示，本發明係提供—種提高輸出功 率的動此產生裝置’主要包括有一機般1、-固定齒輪2、 -活動齒輪3、一傳動件4、一飛輪5與_連桿“ 該固定齒輪2係設置在機殼卜側，其齒形朝内，該活 動盘輪3料《固定齒輪2内側，其齒形向外，使該固定 ϋ齒輪2與活動齒輪3可相互喷合傳動，且該固定齒輪2與活 • ^齒輪3的齒輪比為3:1 ;而該傳動件4係㈣在機殼！内 卩並可轉動’以連接__輸出轴43作為動能輸出，·該傳動件* 7機殼！接觸面設置有波司（Bush)4u(如圖二、圖三A)，以 提门傳動件4轉動的穩定性，為防止該波司41工受麼而偏 移’該傳動件4外環設置有—凸緣412，使該凸緣412嵌入 波司41”，並在該凸緣412與波司411之間留置有餘隙 12 200923197 413，可用來填充潤滑油，該波司411在與機殼丨之間同樣 設置凸緣414(如圖二A、圖二B) ’以進—步強化結構；該傳 動件4朝活動齒輪3的軸心位置穿入並樞設有一傳動軸42 , 使該傳動軸42、活動齒輪3皆包含在固定齒輪2的體積範圍 内，而該活動齒輪3的轴心與傳動軸42接觸面設置有波司 軸承44以利轉動；該飛輪5係固定連接在活動齒輪3外側， 使該飛輪5與活動齒輪3同步轉動；該飛輪5 一端設置有施 丨 力軸51，該連桿6則軸設在施力軸η上，各連桿6除一端 軸设在飛輪施力軸5 1上，其另一端則軸設在汽缸（圖未示出） 的活塞7a〜7f上，使活塞7a〜7f在汽缸壁上往復運動，讓活 塞7a〜7f經由連桿6帶動飛輪5與活動齒輪3旋轉，以進行 動能傳輸。 明參閱圖一 a，前述設計可應用在不同引擎設計中，本 實施例係以較為複雜的V式引擎說明，在該v式引擎確定可 ^ 行的情形下’其餘引擎的設計即不成問題，例如圖一B所示 的傳統直立式引擎，或其它引擎結構。 請參閱圖二A、圖二B，前述波司411的造型，尚可改 為在傳動件4外圍設置環形槽415，而在波司411内緣設置 凸緣416，同樣使該凸緣416插入環形槽415中定位，而該 環形槽4 1 5底部可預留餘隙以填充潤滑油。同樣地，該波司 411亦可在與機殼1之間設置凸緣414,使該凸緣插入機殼1 13 200923197 内以強化固定。 藉由前述的設計，以該活塞7a為 炸所產生的動能帶動，經連桿6向施力：，其係由汽缸内爆 與活動齒輪3會以傳動轴42為轴進51加壓’該飛輪5 活動⑹繞著固定齒輪2内緣旋轉丁，：，使該飛輪5與 動力輸出。 μ輪出軸43則可作 又如圖七、圖八所示，其中該傳 ^ η 輪4 5，β ^ 可設置有軸心齒 w動齒輪3則直接嚙合軸 汽缸叙士及丄 间物45進仃傳動，故 傳動齒Γ 齒輪3同步帶動轴心齒輪45旋轉，經由 ㈣45進仃動力傳輸。而該活動齒輪3與軸心齒輪45 的μ數可以調整，以變化轉動速度， 精以传到所需的速度與 力量，以適合不同的使用目的。 藉由前述本發明的特徵’本發明的傳動方式如圖九至圖 十七所不’其以該活動齒輪3直接嚙合軸心齒輪Μ方式進 仃說明。其中具有傳動車由42、施力轴51，以及固定齒輪2 矛’舌動齒輪3的〇§合點9三處關鍵點；當活塞7a爆炸動能 經連桿6加壓於施力軸51時，其慣量包括由該施力軸51向 該傳動軸42方向施壓（施力線01)，以及由該嚙合點9反作 用力向該傳動軸42方向施壓（施力線〇2)疊加形成，並將疊 加後的力量由傳動件4向該傳動軸42方向施壓（施力線03)， 故輸出的力量遠大於習知結構；而該施力線與施力線〇2 14 200923197 之間形成有一办& 角’以利藉由槓桿原理將力量疊加，而藉由 本發明的纟士描^ ° ” &力線0 1大於施力線02，較圖二十四A、 B、c與围二Δ ^ — Α、Β的先前技藝可以提供更大的輸出力 里 力線03的長度遠大於圖二十四A、b、c與圖 十五A、B的先前技藝，根據槓桿原理得知，轴心施力臂 愈長的工具，其輸出各丄 ^ 力量愈大，使輸出軸43輸出動力更大。 藉由則述結構’當活塞7a爆炸時，其動能經連桿6加壓 於施力轴5 1上’而該連桿6的側壓角度變化非常小，使大 部份慣量可作為推動活動齒輪3與飛輪5旋轉的動力，減少 侧向分力的浪費；當活動齒輪3繞行固定齒輪2轉動時，該 活動齒輪3與飛輪5係朝及 朝反方向轉動，使該施力軸51形成 如圖十八軌跡線a的形狀。 藉由前述軌跡線a的描述，本發明可形成多汽缸、多角 度與多軌跡的配置模式，如圖 Ο 圖/、所不為一個六汽缸引 擎，其汽缸配置相對每一傳翻4 得動轴齒輪42方向配合有兩個， 各汽缸以傳動軸42為軸承6〇。配 ή χ ^ 便具呈現如圖六的軌跡 線分佈，由於各施力軸51呈亡《 μ 具有残之軌料，故運作時可 平穩進行且不會發生„ ,且各仏㈣ 前述六汽缸引擎包括有四個傳動轴们走轉方向，故 配置如圖五中的活塞7a、7c、7e位置，各傳動〜:: 互呈120。配置，即每一汽飯擔負三分之-的動能輪出二 15 200923197 —汽缸開始爆炸行程時，其活塞7a在上、下行程間活動的 執跡線a變化如圖九至圖十一所示，此慣量路徑產生如圖十 八所示的慣量行程執跡區段s，此慣量行程軌跡區段s近似 直線，可將連桿6的大部份慣量施予活動齒輪3轉動，減少 側向分力的損耗；而當活塞7a到達行程末端減緩活動時， 其軌跡線a變化如圖十二所示，進入如圖十八的執跡區段p 此時該連桿6會偏向第二汽缸處推進，對第二汽缸進行壓 縮，然後該第二汽缸進入爆炸行程如圖十三至圖十七，使該 第二汽缸的活塞7c對第三汽缸進行壓縮，此時第一汽缸的 活塞7“到退以進行排氣；如此’當活塞7產生最大慣量推 力時，可將大部份慣量推力施予活動齒輪3進行轉動，故可 大幅提高本發明的動能輸出。前述活塞％、7心^則形成另 一動力行程，其軌跡線與7a、7c、7e相差6(r角度。 同時，無論汽缸如何配置，請參考圖六的執跡線，各汽 d缸行程在同-時間會同時向輸_43中心方向推進或遠 離’故各汽缸的配重（飛給c；、A k . 飛輪5)在任一時間皆能維持平衡，減 少震盪與動力損耗。 ' 再者，傳統引擎必須進行進氣、壓縮、爆炸、排氣四項 動作來完成…欠行程，即料每輸I轉僅為1/2次爆炸的 力量，故引擎轉速要更快，曰私山上 更肖且輸出扭力較低；而本發明每— 動力行程係同時配置二個汽▲ 個π缸，各汽缸依序進行爆炸，即每 16 200923197 次爆炸僅轉動120。，其力量相當龐大，加上本發明損失動能 較低，故本發明可達到低轉速、高扭力的功能。 另外’如、圖十九所示’經由前述完成之本發明 提咼輪出功率的動能產生裝置，主要係應用在不同的需求 上，其中藉由改變施力軸51的高低度，例如圖十九的施力 軸5 1即略低於圖十八，可以改變軌跡區段t的變化，反之亦 然，藉此可視需求改變其軌跡線a、b的變化。 又如圖二十所示，將該施力軸51的高度降得更低，則本 發明亦可由其它動力裝置推動傳動軸42旋轉，再將動力經 由活動齒輪3、飛輪5、施力軸51、連桿6，最後由活塞乃 壓縮汽缸進行能量輸出，即應用在空壓機結構中，讓動能得 輸回活塞7進行壓縮輸出能量。又，本發明的汽缸數係以三 的倍數量設計，若減少其數量，使其平衡感下降，則會產生 震動效果，亦可應用在按摩椅或震動裝置等結構中。當然， 亦可如圖十七所示因施力轴51高度調低形成如圖二十的軌 跡線c，端看使用者需要。 凊參閱圖二~f--、圖二+ -邮- , —十—所不，本發明的汽缸以及其 活塞7a〜7f、連桿6相對每—傳動軸42係以三的倍數設置， 如圖式之六汽缸結構’可分配成兩組對稱並轉動180。角設置 在機殼i兩端，並使相對稱的汽缸進行相同之行程藉以平 衡並加倍力量旋轉活動齒輪3,此結構適用於汽缸平躺的立 17 200923197 臥式引擎甚至於空壓 式引擎，故本發明可適用於各種立式 機、壓縮機中。 另外，前述活塞7a位於行程始點時，該傳動軸或軸 心齒輪46(嚙合點9)’得相對於連桿6向施力點^延伸方向 預先偏轉有一角度，使該施力線〇1與施力 <間开> 成一 夾角，使施力線01與施力線〇2產生力量叠加效果。 藉由前述的實施例，本發明較f用技術請參閱圖十八與 圖二十四a、b、c與圖二十五Α、Β_知結構比較，本發 明的3:1齒輪比與前述兩習知專利的3:2齒輪比之實際應用 情形’其主要差異性有二： “ 其-是具有波司設置’使傳動件4得以穩定固定在機殼 1内’得在高速巨大壓力的情形下，維持整個結構的穩定性， 避免不必要的震動損耗，亦可維持產品的使用壽命； 其一在於施力線變化，由圖中得知，本發明的主要施力 線01較反作用力施力、線G 2為長，此意味汽缸經由連桿^專 遞到輸出軸43的力量更大，故得到較高的輸出動力；同時 X包力線03的長度遠大於先前技藝，根據槓桿原理得知， 也力漳愈長的工具’其輸出力量愈大，使輸出車由43輪 力更大》 另外，在本發明的結構下，無論汽缸如何配置，各汽缸 仃程在同一時間會同時向輸出軸43中心方向推進或遠離，动 Multi-angle, multi-track line for extracting output power Another object of the present invention is to provide a device capable of generating a multi-cylinder cylinder with a multi-cylinder configuration, so that the total output is greatly increased. A kinetic energy generating device capable of achieving an output power for improving the output, comprising a casing having a fixed gear, wherein the gear tooth shape is inward, and a movable gear is disposed on the inner side of the gear. The movable gear tooth shape is arranged such that the fixed gear and the movable gear can mesh with each other, and the gear ratio of the fixed gear to the movable gear is 3:1; a transmission member is pivoted inside the casing. A bush is arranged between the piece and the casing, and the transmission member is rotated by the movable gear, and the extension_output shaft is used to output power; and a flywheel is fixedly connected to the outer side of the movable gear to synchronize the flywheel with the movable gear. One end of the rotating Hefei wheel is provided with a force applying shaft, and the shaft of the force applying shaft is provided with a connecting rod, one end of the connecting rod is arranged on the flywheel applying shaft, and the other end is arranged on the piston of the cylinder, thereby When the internal explosion of the cylinder, the piston reciprocates on the cylinder wall 200923197, and the power thereof rotates the flywheel and the movable gear via the connecting rod to perform kinetic energy output. Due to the design of the Boss structure, the combination of the transmission member and the casing is more stable. It can withstand the high rotational pressure without vibration, maintaining the normal kinetic energy output and stability of the production port; The strength of the force line is increased: the addition of the belt makes the output power more excellent than the prior art; at the same time, under the structural characteristics of the present invention, the steam is widened and the schedule is simultaneously directed to the output shaft at the same time. Advancing or moving away, the weights (flywheels) of each steam rainbow can maintain balance with each other during the time-times to reduce shock and power loss. [Embodiment] Referring to FIG. 2 to FIG. 6 , the present invention provides a device for improving output power, which mainly includes a machine like 1. a fixed gear 2 , a movable gear 3 , and a transmission member 4 . , a flywheel 5 and a _ link "the fixed gear 2 is arranged on the side of the casing, the tooth shape is inward, and the movable wheel 3 is made "the inner side of the fixed gear 2, the tooth shape is outward, so that the fixed ϋ gear 2 and the movable gear 3 can be sprayed and driven to each other, and the gear ratio of the fixed gear 2 to the movable gear 3 is 3:1; and the transmission member 4 is (four) in the casing! _ output shaft 43 as kinetic energy output, · the transmission member * 7 casing! The contact surface is provided with Bush 4u (Figure 2, Figure 3A), to improve the stability of the door transmission 4 rotation, to prevent The boss 41 is biased by the 'the outer ring of the transmission member 4 is provided with a flange 412, the flange 412 is embedded in the boss 41", and a clearance is left between the flange 412 and the washer 411. 12 200923197 413, can be used to fill the lubricating oil, the Boss 411 is also provided with a flange 414 between the casing ( (as shown in Figure 2A, Figure 2B) The transmission member 4 penetrates and pivots a transmission shaft 42 toward the axial center of the movable gear 3, so that the transmission shaft 42 and the movable gear 3 are all included in the volume range of the fixed gear 2, and the movable gear 3 The axis of the shaft and the drive shaft 42 are provided with a boston bearing 44 for rotation; the flywheel 5 is fixedly coupled to the outside of the movable gear 3 to rotate the flywheel 5 synchronously with the movable gear 3; the flywheel 5 is provided with a force-applying shaft at one end thereof 51. The connecting rod 6 is disposed on the urging shaft η. Each of the connecting rods 6 is disposed on the flywheel urging shaft 51, and the other end is disposed on the piston 7a of the cylinder (not shown). On the 7f, the pistons 7a to 7f are reciprocated on the cylinder wall, and the pistons 7a to 7f are caused to rotate the flywheel 5 and the movable gear 3 via the link 6 to perform kinetic energy transmission. Referring to FIG. 1a, the foregoing design can be applied to different engine designs. This embodiment is described by a relatively complicated V-type engine. In the case where the v-type engine is determined to be OK, the design of the remaining engines is not a problem. For example, the traditional upright engine shown in Figure 1B, or other engine architecture. Referring to FIG. 2A and FIG. 2B, the shape of the aforementioned boss 411 may be changed to an annular groove 415 at the periphery of the transmission member 4, and a flange 416 at the inner edge of the boss 411, and the flange 416 is also inserted. The annular groove 415 is positioned in the bottom, and a clearance is reserved at the bottom of the annular groove 4 15 to fill the lubricating oil. Similarly, the boss 411 can also be provided with a flange 414 between the casing 1 and the flange 1 into the casing 1 13 200923197 for reinforcement. With the aforementioned design, the kinetic energy generated by the explosion of the piston 7a is driven by the connecting rod 6; the cylinder implosion and the movable gear 3 are pressed by the transmission shaft 42 as the shaft 51. The flywheel 5 is movable (6) around the inner edge of the fixed gear 2, and the flywheel 5 is output with power. The μ wheel output shaft 43 can be as shown in FIG. 7 and FIG. 8 respectively, wherein the transmission η wheel 4 5, β ^ can be provided with the shaft center tooth and the moving gear 3 directly meshes the shaft cylinder and the stalker and the stalk 45 drive transmission, so the drive gears 3 synchronously drive the shaft gear 45 to rotate, through (4) 45 into the power transmission. The μ number of the movable gear 3 and the shaft gear 45 can be adjusted to change the rotational speed to achieve the required speed and force to suit different purposes. The present invention is characterized in that the transmission mode of the present invention is as shown in Figs. 9 to 17 and the movable gear 3 directly engages the spindle gear Μ. There are three key points of the transmission vehicle 42, the urging shaft 51, and the fixed gear 2 spear's spur gear 3; when the piston 7a kinetic energy is pressurized by the connecting rod 6 to the urging shaft 51 The inertia includes pressing the urging shaft 51 toward the transmission shaft 42 (the urging line 01), and applying a pressing force (the urging line 〇2) in the direction of the transmission shaft 42 by the reaction force of the engagement point 9 is formed. And the superimposed force is pressed by the transmission member 4 in the direction of the transmission shaft 42 (the force application line 03), so that the output force is much larger than the conventional structure; and the applied force line and the force application line 〇 2 14 200923197 are formed. There is a & angle ' to facilitate the superposition of forces by the principle of leverage, and by the gentleman of the present invention, ^ ° & force line 0 1 is greater than the force line 02, compared with Figure 24 A, B, c and The prior art of 二 Δ ^ Α, Β can provide greater output force. The length of the force line 03 is much larger than the previous technique of Figure 24 A, b, c and Figure 15 A, B, according to the principle of leverage. It is known that the longer the tool of the axial force applying arm, the greater the output of each tool, and the greater the output power of the output shaft 43. When the piston 7a explodes, its kinetic energy is pressurized on the urging shaft 5 1 via the connecting rod 6 and the lateral pressure angle of the connecting rod 6 changes very small, so that most of the inertia can be used as the moving movable gear 3 and the flywheel. 5 rotating power, reducing the waste of the lateral component force; when the movable gear 3 rotates around the fixed gear 2, the movable gear 3 and the flywheel 5 are rotated toward and in the opposite direction, so that the force applying shaft 51 is formed as shown in FIG. The shape of the trajectory a. By the description of the trajectory a, the present invention can form a multi-cylinder, multi-angle and multi-track configuration mode, as shown in Fig. /, not a six-cylinder engine, and its cylinder configuration is relatively One transmission 4 has two shafts 42 in the direction of the shaft gear 42. Each cylinder has a transmission shaft 42 as a bearing 6〇. With the ή χ ^, the trajectory line distribution as shown in Fig. 6 is presented, and the force-applying shaft 51 is dead. μ has a residual rail material, so it can be operated smoothly and does not occur „, and each 仏 (4) The aforementioned six-cylinder engine includes four propeller shafts in the direction of rotation, so the pistons 7a, 7c are arranged as shown in Figure 5. 7e position, each drive ~:: is 120. Configuration, that is, each kiln is responsible for three-points of kinetic energy rotation 2 15 200923197 - when the cylinder starts the explosion stroke, the piston 7a changes between the upper and lower strokes of the execution line a as shown in Figure 9 to Figure 11 The inertia path generates an inertia stroke tracking section s as shown in FIG. 18, and the inertia stroke path section s is approximately straight, and most of the inertia of the connecting rod 6 can be applied to the movable gear 3 to rotate, reducing the lateral direction. The loss of the component force; when the piston 7a reaches the end of the stroke to slow down the activity, the trajectory a changes as shown in Fig. 12, and enters the obstruction section p as shown in Fig. 18, and the link 6 is biased toward the second cylinder. At the point of advancement, the second cylinder is compressed, and then the second cylinder enters an explosion stroke as shown in FIG. 13 to FIG. 17, so that the piston 7c of the second cylinder compresses the third cylinder, and at this time, the piston 7 of the first cylinder "To retreat to exhaust; so when the piston 7 produces the maximum inertia thrust, most of the inertia thrust can be applied to the movable gear 3 for rotation, so that the kinetic energy output of the present invention can be greatly improved. The pistons %, 7 ^ forms another dynamic journey, The trajectory is different from 7a, 7c, and 7e by 6 (r angle. At the same time, no matter how the cylinder is configured, please refer to the trajectory of Figure 6. The stroke of each steam d cylinder will advance or move away from the center of the _43 at the same time. 'Therefore, the counterweights of each cylinder (flying to c;, A k. flywheel 5) can maintain balance at any time, reducing shock and power loss. 'Furthermore, the traditional engine must carry out intake, compression, explosion, exhaust Four actions to complete... Under-travel, that is, the power of only 1/2 explosion per I, so the engine speed is faster, the smuggling mountain is more sloppy and the output torque is lower; and the per-power stroke of the present invention At the same time, two steam ▲ π cylinders are arranged, and each cylinder is exploded in sequence, that is, only 120 rotations per 16 200923197 explosions. The power is quite large, and the loss kinetic energy of the invention is low, so the invention can achieve low speed. The function of the high-torque force. In addition, as shown in FIG. 19, the kinetic energy generating device for improving the power of the wheel through the above-mentioned completed invention is mainly applied to different requirements, wherein the force applying shaft 51 is changed by High and low, such as Figure 19 The urging axis 51 is slightly lower than that of FIG. 18, and the change of the trajectory section t can be changed, and vice versa, thereby changing the change of the trajectory lines a and b according to the demand. The height of the force shaft 51 is lowered lower, and the present invention can also be driven by other power devices to rotate the transmission shaft 42, and then the power is transmitted via the movable gear 3, the flywheel 5, the force applying shaft 51, the connecting rod 6, and finally the piston is compressed by the piston. The energy output is applied in the air compressor structure, so that the kinetic energy is returned to the piston 7 for compression output energy. Moreover, the number of cylinders of the present invention is designed in three times the number, and if the number is reduced, the balance is reduced. It will produce a vibration effect, and can also be applied to a structure such as a massage chair or a vibrating device. Of course, as shown in FIG. 17, the height of the force applying shaft 51 is lowered to form a trajectory line c as shown in FIG. User needs. Referring to Figure 2~f--, Figure 2+-mail-, -10-, the cylinder of the present invention and its pistons 7a-7f, and the connecting rod 6 are arranged in multiples of three with respect to each of the drive shafts 42, such as The six-cylinder structure of the figure can be assigned to two sets of symmetry and rotated 180. The angle is set at both ends of the casing i, and the symmetrical cylinders perform the same stroke to balance and double the force to rotate the movable gear 3. This structure is suitable for the cylinder lying flat 17 200923197 horizontal engine or even air compressor. Therefore, the present invention can be applied to various vertical machines and compressors. In addition, when the piston 7a is located at the starting point of the stroke, the transmission shaft or the shaft gear 46 (engagement point 9)' is pre-deflected with respect to the extension direction of the connecting rod 6 by an angle, so that the urging line 与1 and Applying force <opening> into an angle, so that the force line 01 and the force line 〇2 generate a force superposition effect. With the foregoing embodiments, the present invention compares the techniques of f with reference to FIG. 18 and FIG. 24 a, b, c and FIG. 25, and the structure of the 3:1 gear ratio of the present invention. The practical application of the 3:2 gear ratio of the two conventional patents has two main differences: "It has a Boss setting to enable the transmission member 4 to be stably fixed in the casing 1". In the case of the whole structure, the stability of the entire structure is maintained, unnecessary vibration loss is avoided, and the service life of the product is maintained. One of them is the change of the applied force line. It is known from the figure that the main force line 01 of the present invention is more reactive. The force applied and the line G 2 are long, which means that the cylinder has a greater power transmitted to the output shaft 43 via the connecting rod ^, so that a higher output power is obtained; and the length of the X-packing force line 03 is much larger than the prior art, according to the lever The principle is that the longer the tool is, the larger the output force is, the more the output car is made up of 43 wheels. In addition, under the structure of the present invention, regardless of the cylinder configuration, each cylinder process will be at the same time. Simultaneously pushing or moving away from the center of the output shaft 43
1S 200923197 故各汽缸的配重在任—時間皆能維持平衡，亦可減少震盪與 動力損耗。 上列詳細說明係針餅太恭_ 對本發明之一可行實施例之具體説 明，惟該實施例並非用以up生,丨士 ^ 乂限制本發明之專利範圍，凡未脫離 本發明技藝精神所為之箄钕眚竑十_ Φ . ^ Α 寻政貫施或變更’均應包含於本案之 專利範圍中。 【圖式簡單說明】1S 200923197 Therefore, the counterweight of each cylinder can maintain balance during any time and time, and can reduce vibration and power loss. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT A detailed description of one of the possible embodiments of the present invention is not intended to be used in the present invention, and is not intended to limit the scope of the invention, and the scope of the invention is not limited by the spirit of the invention.箄钕眚竑 _ _ Φ . ^ 寻 寻 贯 贯 或 or change 'all should be included in the scope of the patent. [Simple description of the map]
請參閱以下有關本發明一較佳實施例之詳細說明及其附 圖，將可進-步瞭解本發明之技術内容及其目的功效，有關 該實施例之附圖為： 圖一 Α為本發明的結構立體圖； 圖- B為-種習用的直立式汽缸結構立體圖; 圖一為本發明的傳動軸結構立體分解視圖； 圖二A為圖二的波司結構例變化圖； 圖二B為®1 :的波司結構例剖視圖； 圖二為本發明的結構正視圖； 圖一 A為圖二的波司結構例剖視圖； 圖四為本發明的V6型汽缸配置結構側視圖； 圖五為本發明含活塞、連桿的結構正視圖； 圓八為本發明的V6型雙軌汽缸活動軌跡圖； 圖七為本發明的另一傳動軸結構變化例正視圖 19 200923197 圖八為本發明的另一傳動軸結構變化例側視圖； 圖九〜圖十七為本發明的動作順序圖； 圖十八為本發明的運動軌跡分析圖； 圖十九為本發明的施力軸高度調低軌跡分析圖； 圖十為本發明的施力袖高度更低的軌跡分析圖； 圖二十一為本發明另一實施例的結構正視圖； 圖二十二為本發明另一實施例的雙組汽缸配置結構側視 面 · f\ 圃， 圖一十二為習知曲柄軸汽缸的動作示意圖； 圖一十四為US 4, 044, 629的結構示意圖； igt 一 —十五為us 4, 073, 1 96的結構示意圖； 圖一十六A為台灣專利62305的結構示意圖； 圖~~十六B為台灣專利623〇5的動作示意圖； 圖—丨 一十六C為台灣專利62305的軌跡分析圖；The detailed description of the preferred embodiment of the present invention and the accompanying drawings will be further understood, and the technical contents of the present invention and the purpose of the present invention will be further understood. FIG. Fig. B is a perspective view of a conventional vertical cylinder structure; Fig. 1 is a perspective exploded view of the transmission shaft structure of the present invention; Fig. 2A is a variation diagram of the waveguide structure of Fig. 2; Fig. 2B is a diagram 1 is a cross-sectional view of the structure of the Boss; FIG. 2 is a front view of the structure of the present invention; FIG. 1A is a cross-sectional view of the Boss structure of FIG. 2; FIG. 4 is a side view of the configuration of the V6 type cylinder of the present invention; A front view of a structure including a piston and a connecting rod; a circular octagon is a movable trajectory diagram of a V6 type double-track cylinder of the present invention; and FIG. 7 is a front view of another transmission shaft structural change of the present invention. 19 200923197 FIG. 8 is another embodiment of the present invention. FIG. 9 is a side view of the operation of the present invention; FIG. 18 is a motion sequence analysis diagram of the present invention; FIG. Figure 10 is Figure 21 is a front elevational view of another embodiment of the present invention; Figure 22 is a side view of a two-group cylinder configuration structure according to another embodiment of the present invention. f\ 圃, Fig. 12 is a schematic view of the operation of a conventional crankshaft cylinder; Fig. 14 is a schematic structural view of US 4, 044, 629; igt 1-5 is a schematic structural view of us 4, 073, 1 96; Figure 16A is a schematic diagram of the structure of Taiwan Patent 62305; Figure ~~16B is the schematic diagram of the operation of Taiwan Patent 623〇5; Figure-丨16C is the trajectory analysis diagram of Taiwan Patent 62305;
Cfe：5/ 圖 JL· I i - 、B、c 為 PCT/CN2005/00 0 992 的結構示意圖； 圆 一 ' —十八A、B為PCT/CN2006/0021 06的結構示意圖。 【主要元件符號說明】 1 機殼 2 固定齒輪 3 活動齒輪 4 傳動件 411 波司 412 凸緣 413 餘隙 414 凸緣 20 200923197 415 環形槽 42 傳動軸 44 波司軸承 5 飛輪 6 連桿 9 p齒合點 a,b，c 執跡線 t 轨跡區段 x2 傳動件 x4 施力點 pi ~ p3點 416 凸緣 43 輪出軸 45 軸心齒輪 51 施力軸 7a~7f 活塞 01,02,03施力線 S 慣量行程區段 xl 活塞 x3 曲柄軸 d 1〜d 4軌跡線 21Cfe: 5/ Figure JL· I i - , B, c are schematic diagrams of PCT/CN2005/00 0 992; circle one '- eighteen A, B is the structural diagram of PCT/CN2006/0021 06. [Main component symbol description] 1 Enclosure 2 Fixed gear 3 Movable gear 4 Transmission 411 Boss 412 Flange 413 Clearance 414 Flange 20 200923197 415 Annular groove 42 Drive shaft 44 Boss bearing 5 Flywheel 6 Connecting rod 9 p teeth Joint point a, b, c Execution trace t Trajectory section x2 Transmission part x4 Force point pi ~ p3 point 416 Flange 43 Wheel-out shaft 45 Axis gear 51 Forced shaft 7a~7f Piston 01, 02, 03 Force line S inertia stroke section xl piston x3 crankshaft d 1~d 4 trajectory line 21