200938752 九、發明說明： 【發明所屬之技術領域】 ' 本發明係關於一種可獨立控制傳動機構，特別μ於利用二行星 . #齡及二傳動組進行可默_能錄从能量輸出之可獨立 控制傳動機構。 【先前技術】 習用傳動機構，如中華民國專利公告第以勘號之車輛用之變 〇 速祕造’其揭示—錄上設置有—滑塊，姆塊之_設有-前進 用錄及-加賴齒輪，於-連動軸上設置有—反向滑塊，位於該反 向滑塊之-侧之該連動軸上設置有一倒退用傘形齒輪及一前進用伞形 齒輪，且於該倒退用傘形齒輪及前進用傘形齒輪之間設置有_最終軸 ，该最終軸係由軸傳動，藉由該最終軸位於該倒退用傘形齒輪及前進 用傘形齒輪之間，以及該加力用齒輪及前進用齒輪亦位於該倒退用傘 形齒輪及前進用傘形齒輪之間，而可使該變速箱之寬度方向變小，並 且利用該連動軸之倒退用傘形齒輪及前進用傘形齒輪嚙合該最終軸之 φ 一傳動傘形齒輪，而可使該變速箱達到小型化之目的。惟，該變速箱 構造設置有該滑塊，且該滑塊必然會產生相互摩擦滑動，因而相對降 低其功率的傳輸效率。 另一傳動機構’如美國專利第6387004號之Continuously Variable Transmission〃，其揭示一連續可變傳動組。該連續可變傳動組 包含一第一行星齒輪組及一第二行星齒輪組，其用以將一第—馬達及 一第二馬達之動力傳輸至一傳動軸。然而，該連續可變傳動組僅將該 第一馬達及第二馬達之動力固定經由該第一行星齒輪組及第二行星齒 輪組傳輸至該傳動軸。換言之，該連續可變傳動組僅將該第—馬達及 5 200938752 達設定為蚊_個動力輸人端，縣稱動概定為固定的 賴-V、力輪出H之’在傳輪動力上其仍有必要進—步選擇提供 2式控魏量輸人及能量輪出之傳動機構，以符合不同的動力整合 得輸需求。 ❹ 有鐘於此’本發明為了改良上述缺點或符合上述需求，其提供一 I獨立控制傳動祕，該傳動機構利用二行星齒輪組及二傳動連接 、，=可變她議爾伽，_繼#—控制端及 =傳輸端’該控制端用以控制該自由傳輸端，如此該自由傳輸端 提古」換做為里輸人端或能量輪_，以達成可獨立控制傳動及 =；：讀輸效率之目的。科，該傳動機構未顧任何摩擦滑動元 【發明内rrslidmgmember〕’以達成提高能量傳輸效率之目的。 本發批主要_、提供—射獨立謂_構其利用二行 觸雜魄行可l倾錄入及綠輸出，該傳 量ΓΓ咖—自由雜物嫌痛量輸入端或能 輪出％’本綱達成·立控轉動及提高能量傳輸辭之目的。 本發明之另—目的係提供_種可獨立控娜動機構，其利用二行 動機構未利用任何摩擦滑動元件，其達成提高能量傳輸效率之^傳 為了達成上述目的，本發g月可獨立控制傳動機構包含 姓亥第-仃《輪组具有—能量輸出端，該第二行星 制=第-傳動連接組具有—能量輸入端，該第二傳動連二 -自由傳輸端。物喻繼自_端，以㈣換該自由= 6 200938752 端做為能量輸人端或能量輸出端。 一珩一硬轉幸由 考明較佳實施例之該第一行星齒輪組： 一疑轉軸及一第三旋轉軸。 本發明較佳實細H行星祕組之第—旋_為該可獨 立控制傳動機構之能量輸出端。 本發明較佳實補之鄉—行㈣輪組之第二_軸連接至今 第一傳動連接組。 Λ200938752 IX. Description of the invention: [Technical field to which the invention pertains] The present invention relates to an independently controllable transmission mechanism, in particular to the use of two planets. Control the transmission mechanism. [Prior Art] Conventional transmission mechanism, such as the Republic of China Patent Announcement, the use of the vehicle for the survey of the speed of the idling secrets of its own disclosure - the record is set with - slider, the block of the block - set - forward record and - a slanting gear, a reverse slider is disposed on the linkage shaft, and a reverse bevel gear and a forward mushroom gear are disposed on the linkage shaft on the side of the reverse slider, and the reverse gear is reversed A final shaft is disposed between the bevel gear and the forward bevel gear, and the final shaft is driven by the shaft, wherein the final shaft is located between the reverse bevel gear and the forward bevel gear, and the plus The force gear and the forward gear are also located between the reverse bevel gear and the forward bevel gear, and the width direction of the gearbox can be made small, and the bevel gear and the forward gear for reversing the interlocking shaft can be used. The bevel gear meshes with the φ-transmission bevel gear of the final shaft, so that the gearbox can be miniaturized. However, the gearbox structure is provided with the slider, and the slider inevitably produces frictional sliding with each other, thereby relatively reducing the transmission efficiency of its power. Another transmission mechanism, such as the Continuous Variable Transmission of U.S. Patent No. 6,387,004, discloses a continuously variable transmission. The continuously variable transmission set includes a first planetary gear set and a second planetary gear set for transmitting power of a first motor and a second motor to a drive shaft. However, the continuously variable transmission group transmits only the power of the first motor and the second motor to the transmission shaft via the first planetary gear set and the second planetary gear set. In other words, the continuously variable transmission group only sets the first motor and 5 200938752 to be a mosquito-powered input terminal, and the county weighing is defined as a fixed Lai-V, and a force-in-H is in the transmission power. It is still necessary to further choose to provide a 2-type control of the transmission and energy transmission mechanism to meet the different power integration needs. In order to improve the above disadvantages or meet the above requirements, the present invention provides an I independent control transmission, the transmission mechanism utilizes two planetary gear sets and two transmission connections, = variable her ergo, _ #—Control end and = transmission end 'The control end is used to control the free transmission end, so that the free transmission end is changed to the inner input or the energy wheel _ to achieve independent control of the transmission and =; Read the purpose of transmission efficiency. The transmission mechanism does not care about any friction sliding element [invention invention rrslidmgmember]' to achieve the purpose of improving energy transmission efficiency. The main batch of this batch is _, providing - shooting independent _ constituting its use of two lines of touch, can be entered and green output, the volume of ΓΓ — 自由 自由 自由 自由 自由 — — — — — — — — — — — — — — — — — The goal is to achieve the purpose of turning and improving the energy transmission. Another object of the present invention is to provide an independently controllable mechanism that utilizes two friction mechanisms without utilizing any frictional sliding elements to achieve improved energy transmission efficiency. In order to achieve the above objectives, the present invention can be independently controlled. The transmission mechanism includes a surname, "the wheel set has an energy output, the second planetary system = the first transmission connection group has an energy input end, and the second transmission has a two-free transmission end. The material is subordinated to the _ end, and (4) is replaced by the free = 6 200938752 end as the energy input end or energy output end. The first planetary gear set of the preferred embodiment is ascertained by a hard drive: a suspected shaft and a third axis of rotation. Preferably, the first embodiment of the present invention is an energy output of the independently controllable transmission mechanism. The second shaft of the home-row (four) wheel set of the preferred embodiment of the present invention is connected to the first transmission connection group. Λ
本發明較佳實細之㈣_行星雜組之第三旋_連接至該 第二傳動連接組。 〜 本發明較佳實施例之該第一行星齒輪組為正比值驅動式行星齒 輪組。 本發明較佳實施例之該第二行星齒輪組具有一第一旋轉輛、一第 一旋轉軸及一第三旋轉轴。 本發明較佳實施例之該第二行星齒輪組之第一旋轉軸為該可獨 立控制傳動機構之控制端。 本發明較佳實施例之該第二行星齒輪組之第二旋轉轴連接至咳 第一傳動連接組。 本發明較佳實施例之該第二行星齒輪組之第三旋轉軸連接至該 第二傳動連接組。 本發明較佳實施例之該第二行星齒輪組為負比值驅動式行星齒 輪組。 【實施方式】 為了充分瞭解本發明，於下文將例舉較佳實施例並配合所附圖式 作詳細說明，且其並非用以限定本發明。 7 200938752 本發明較佳實施例之可獨立控制傳動機構可應用於各種 速傳動相關技術領域’例如：海洋發電機、風力發電機或複去 =1=速箱等，但其並非用以限縣發明之可獨立控_動機構 第i圖_本發·佳實_之可社控麟軸構 ;第2關林發曝佳實_之可獨立控轉域構之内部架^ ❹ ❿ 。請參照第丨及2圖所示，本發明較佳實施例之可獨立動1 包含-第-繼敝丨、-第：行星輸2 ^機構 及-第二鑛連胁4。 傳動連接組3 請參照第2圖所示 :-第二旋轉輛終第三旋轉轴•該第—行星齒輪，二 疑轉軸QP _可獨立_傳動機構之能量輪㈣；該第 組1之第二旋轉轴連接至該第—傳動連接組域第-行星:輪 i之第三旋轉軸AE連接至該第二傳動連接組4。相對的齒輪組 齒輪組2具有-第-旋轉轴CR、—第二旋轉軸BD及—二二行星 郎。該第二行星齒輪組2之第—旋轉軸CR為該可獨立控轉2 之控制端，該第一订星齒輪組2之第二旋轉轴肋連接至— 連接組3 ;該第二行星齒輪組2之第三旋轉軸be連接至 傳動 接組4。此外，該第―傳動連接組3具有一能量輸入端S:動: 動連接組4具有一自由傳輸端SE。 A弟一傳 請再參照第i及2圖所示，本發明可獨立控制傳 二行星錄組2之控制端〔第-旋轉軸CR〕控齡第二值t用料 之自由傳輸端SE，以自由切換該自由傳輸物《崎ft! 里輸出端。當職第二傳動_組4之自φ 8 200938752 入端時，該第二傳動連接組4之自由傳輸端SE與該第-傳動逄接组3 之能量輸人端SD共同輸人缝。反之，#將該第二傳動連接組*之 自由傳輸端SE切換做為能量輸出端時，該第二傳動連接乡且*之自由傳 輸端SE與該第-行星齒輪組丨之第—旋轉軸〇ρ〔能量輸出端〕共同 輸出能量。 〃 第3A至3C圖揭示本發明較佳實施例之可獨立控制傳動機構採Preferably, the third sub-rotation of the (four)-planetary group of the present invention is connected to the second transmission connection group. ~ The first planetary gear set of the preferred embodiment of the present invention is a proportional drive planetary gear set. In the preferred embodiment of the present invention, the second planetary gear set has a first rotating vehicle, a first rotating shaft and a third rotating shaft. The first rotating shaft of the second planetary gear set of the preferred embodiment of the present invention is the control end of the independently controllable transmission mechanism. In a preferred embodiment of the invention, the second rotary shaft of the second planetary gear set is coupled to the cough first drive connection set. The third rotating shaft of the second planetary gear set of the preferred embodiment of the present invention is coupled to the second transmission connection set. The second planetary gear set of the preferred embodiment of the present invention is a negative ratio driven planetary gear set. The present invention will be described in detail below with reference to the accompanying drawings, and is not intended to limit the invention. 7 200938752 The independently controllable transmission mechanism of the preferred embodiment of the present invention can be applied to various speed transmission related technical fields, for example: marine generator, wind power generator or reset ===speed box, etc., but it is not used to limit the county The invention can be independently controlled _ moving mechanism i- _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ _ Referring to Figures 2 and 2, the independently movable 1 of the preferred embodiment of the present invention comprises a -th-thoracic, -th: planetary transmission 2^ mechanism and -second ore threat 4 . Transmission connection group 3 Please refer to Fig. 2: - the second rotating shaft of the second rotating unit • the first planetary gear, the second rotating shaft QP _ can be independent _ transmission energy wheel (four); the first group of the first The second rotary shaft AE is connected to the second transmission connection group 4 by the second rotary shaft AE of the first transmission shaft. The opposite gear set gear set 2 has a -first-rotation axis CR, a second rotation axis BD, and a second-two planet. The first rotating shaft CR of the second planetary gear set 2 is the control end of the independently controllable rotation 2, and the second rotating shaft rib of the first planetary gear set 2 is connected to the connection group 3; the second planetary gear The third rotary shaft be of the group 2 is connected to the drive set 4. Furthermore, the first transmission connection group 3 has an energy input S: the dynamic connection group 4 has a free transmission end SE. A younger brother, please refer to the figures i and 2 again, the present invention can independently control the control terminal (the first rotating shaft CR) of the second planetary record group 2, the second transmission value of the second value t material, the free transmission end SE, To freely switch the output of the freely transmitted object "Saki ft!". When the second transmission_group 4 is from the φ 8 200938752 inlet, the free transmission end SE of the second transmission connection group 4 and the energy input end SD of the first transmission connection group 3 are jointly input. On the other hand, when the free transmission end SE of the second transmission connection group* is switched as the energy output end, the second transmission connects the free transmission end SE of the town and the first rotation axis of the first planetary gear set 〇ρ [energy output] outputs energy together. 〃 3A to 3C are diagrams showing the independently controllable transmission mechanism of the preferred embodiment of the present invention
用行星嵩輪組之内部結構圖，其包含三種行星齒輪組之内部、结構，但 其並非用以限定本發明。 請參照第3A圖所示，該行星齒輪組包含一太陽齒輪psl、一太 陽齒輪旋轉軸pssl、一中央齒輪ps2、一中央齒輪旋轉軸pss2、一第一 订星齒輪PP卜一第二行星齒輪PP2及一行星臂旋轉軸pa。該一第一 行星齒輪ppl及第二行星齒輪pp2嚅合該太陽齒輪psl及中央齒輪ps2 。亥太陽齒輪旋轉轴pssl及行星臂旋轉轴pa為共軸。當該行星臂旋轉 細Pa固定不動時，該太陽齒輪旋轉轴pssi及中央齒輪旋轉軸pss2之 知轉方向為相同方向’且其轉速比值為正。該行星齒輪組係屬正比值 動式行星齒輪組。 請再參照第2及3A圖所示，該太陽齒輪旋轉軸pssl、中央齒輪 旋轉軸pss2及行星臂旋轉軸pa可做為該第一行星齒輪組1之第一旋轉 軸0P、第二旋轉軸AD及第三旋轉軸AE。或者，該太陽齒輪旋轉軸 Pssl、中央齒輪旋轉轴pSS2及行星臂旋轉軸pa可做為該第二行星齒輪 魬2之第一旋轉軸CR、第二旋轉軸BD及第三旋轉軸bE。. &青參照第3B及3C圖所示，該行星齒輪組包含一太陽齒輪ns、 —太陽齒輪旋轉軸nss、一環齒輪nr、一環齒輪旋轉轴、至少一行 星齒輪叩及一行星臂旋轉軸na。該二行星齒輪組係屬兩種不同型式的 200938752 負比值驅動式行星齒輪組。 «月再參照第3B圖所不，該太陽齒輪旋轉轴聊及行星臂焚轉輪 ⑽為共軸。當該行星臂旋轉軸na固定不動時，該太陽齒輪旋轉轴吻 及環齒輪旋轉軸⑽之旋财⑽減方向，且其轉雜值為負。 、請再參照第3C圖所示，該環齒輪旋轉轴⑽及行星臂旋轉轴如 為八軸S該仃星臂旋轉轴na固定不動時，該太陽齒輪旋轉轴吻及 環齒輪旋轉細8之旋轉方向為相反方向，且其轉速比值為負。 請再參照第2、3B及3C _示，該太陽齒輪旋轉軸nss、壤齒 輪旋轉轴nrs及行星臂旋轉細&可做為該第一行星齒輪組】之第= 轉軸OP、第二旋轉軸AD及第三旋轉軸处；或者，該太陽齒輪旋轉 軸脱、環齒輪旋轉軸nrs及行星臂旋熱na可做為該第二行星歯輪級 2之第一旋轉轴CR、第二旋轉軸BD及第三旋轉轴BE。 第4A至4F圖揭示本發明較佳實施例之可獨立控制傳動機構採 用傳動連減之_結_，其包含六種傳動連接組之内部結構^ 其並非用以限定本發明。— 請參照第4A至4F圖所示，該傳動連接組包含一第一齒輪 、一旋轉軸cms、一第二齒輪cmg2及一第三齒輪。該第一齒^ cmgl唱合該第二齒輪cmg2及第三齒輪啊3，且該第二齒輪吻说及 第二齒輪cmg3可選自單一轉軸、共軸之外軸及共軸之内軸。 請再參照第4A圖所示，該第二齒輪cmg2及第三齒輪咖幻皆 為單-轉轴。請再參照第4B圖所示，該第二齒輪啦拉為共轴之外二 ，而該第三齒輪cmg3為單一轉軸。請再參照第4C圖所示，該第二齒 輪cmg2為單一轉軸’而該第三齒輪cmg3為共軸之内軸。請再參照第 4D圖所示，該第一齒輪cmg2及第三齒輪cmg3皆為共軸之外轴。請 200938752 再參照第4E圖所示，該第二齒輪0111§2為共軸之外軸，而該第三齒輪 cmg3為共軸之内軸。請再參照第4F圖所示，該第二齒輪及第 三齒輪cmg3皆為共轴之内軸。 請再參照第2及4A至4F圖所示，該傳動連接纟㈣ 選擇做為該第-傳動連接組3之能量輸入端SD或該第二傳動連接組4 之自由傳輸端SE。該第二齒輪cmg2及第三齒輪咖幻用以同時連接 該第一行星齒輪組1之第二旋轉軸AD及該第二行星齒輪組2之第二 旋轉軸BD。該第二齒輪cmg2及第三齒輪cmg3用以同時連接該第一 行星齒輪組1之第三旋轉軸AE及該第二行星齒輪組2之第三旋轉轴 BE。 請再參照第2圖所示，本發明之可獨立控制傳動機構 星齒輪組i之第二旋轉軸AD之轉速與該第二行星齒輪組2 ^第二旋 轉軸BD之轉速設定為關係式為：nBD=anA〇 —疋 其中nBD及nAD分別為該第二行星齒輪组2之第二旋轉轴助之 轉速及該第-行星齒輪組1之第二旋轉軸奶之轉速。 ❹ 肖時’本發明之可獨立控制傳動機構將該第-行星齒輪組！ -旋轉軸OP〔能量輸出端〕之轉速與該第二行星齒輪組2之第— 軸CR〔控制端〕之轉速設定為關係式為：ncR=pn〇p 疋 其中吻及nOP分別為該第二行星齒輪組2之第一旋轉轴邙 制端〕之轉速及該第-行星齒輪組i之第一旋轉轴〇p〔能量輪出端〕工 之轉速。 同時，本發明之可獨立控制傳動機構將該第一行星齒輪組ι之第 三旋轉軸AE之轉速麟第二㈣贿組2 ^三旋_ be之轉迷設 定為關係式為.nAE^BE ' 200938752 其中nAE及nBE分别為該第一行星 轉速及該第二行星齒輪組2之第三旋轉軸BE之轉速了疋^之 ㈣二㈣佳細 —仃星齒輪組及二傳動連接組之組合示意圖 ’其包含二十三鑛合之健實施例，但其並非用以岐本卿The internal structure diagram of the planetary wheel set includes the interior and structure of the three planetary gear sets, but it is not intended to limit the present invention. Referring to FIG. 3A, the planetary gear set includes a sun gear ps1, a sun gear rotating shaft pssl, a central gear ps2, a central gear rotating shaft pss2, a first positioning gear PP, and a second planetary gear. PP2 and a planetary arm rotation axis pa. The first planetary gear ppl and the second planetary gear pp2 are coupled to the sun gear ps1 and the central gear ps2. The sun gear rotation axis pssl and the planetary arm rotation axis pa are coaxial. When the planetary arm rotation fine Pa is fixed, the sun gear rotation axis pssi and the central gear rotation axis pss2 have the same direction of rotation and the rotation speed ratio is positive. The planetary gear set is a proportional planetary gear set. Referring to FIGS. 2 and 3A again, the sun gear rotating shaft pssl, the central gear rotating shaft pss2, and the planetary arm rotating axis pa can be used as the first rotating shaft OP and the second rotating shaft of the first planetary gear set 1. AD and third axis of rotation AE. Alternatively, the sun gear rotating shaft Pss1, the center gear rotating shaft pSS2, and the planetary arm rotating shaft pa may be the first rotating shaft CR, the second rotating shaft BD, and the third rotating shaft bE of the second planetary gear 魬2. As shown in Figures 3B and 3C, the planetary gear set includes a sun gear ns, a sun gear rotation axis nss, a ring gear nr, a ring gear rotation axis, at least one planet gear 叩, and a planet arm rotation axis. Na. The two planetary gear sets are of two different types of 200938752 negative ratio driven planetary gear sets. «The month is again referred to in Figure 3B. The sun gear rotation axis and the planetary arm combustion wheel (10) are coaxial. When the rotation axis na of the planetary arm is fixed, the rotation of the sun gear and the rotation of the ring gear (10) are reduced (10), and the turning noise is negative. Referring to FIG. 3C again, when the ring gear rotating shaft (10) and the planetary arm rotating shaft are eight axes S, the comet arm rotating shaft na is fixed, the sun gear rotating shaft kiss and the ring gear rotating fine 8 The direction of rotation is in the opposite direction and its speed ratio is negative. Referring to FIGS. 2, 3B and 3C, the sun gear rotation axis nss, the soil gear rotation axis nrs, and the planetary arm rotation fineness & can be used as the first planetary gear set] the second rotation axis OP, the second rotation The axis AD and the third rotating shaft; or the sun gear rotating shaft off, the ring gear rotating shaft nrs and the planetary arm rotating heat na can be used as the first rotating shaft CR of the second planetary wheel stage 2, the second rotation The shaft BD and the third rotating shaft BE. 4A through 4F illustrate an embodiment of the present invention which is capable of independently controlling the transmission mechanism using a transmission reduction, which includes the internal structure of the six transmission connection groups, which is not intended to limit the present invention. — Referring to Figures 4A to 4F, the transmission connection set includes a first gear, a rotating shaft cms, a second gear cmg2, and a third gear. The first tooth ^cmgl sings the second gear cmg2 and the third gear 3, and the second gear and the second gear cmg3 are selected from a single shaft, a coaxial outer shaft and a coaxial inner shaft. Referring to Figure 4A again, the second gear cmg2 and the third gear are all single-rotating. Referring to FIG. 4B again, the second gear is pulled out of the coaxial axis, and the third gear cmg3 is a single rotating shaft. Referring again to Fig. 4C, the second gear cmg2 is a single rotating shaft ' and the third gear cmg3 is a coaxial inner shaft. Referring to Fig. 4D again, the first gear cmg2 and the third gear cmg3 are coaxial axes. Please refer to FIG. 4E again. The second gear 0111 § 2 is a coaxial outer shaft, and the third gear cmg3 is a coaxial inner shaft. Referring to Fig. 4F again, the second gear and the third gear cmg3 are coaxial inner shafts. Referring to Figures 2 and 4A to 4F again, the transmission port (4) is selected as the energy input terminal SD of the first transmission connection group 3 or the free transmission end SE of the second transmission connection group 4. The second gear cmg2 and the third gear are used to simultaneously connect the second rotation axis AD of the first planetary gear set 1 and the second rotation axis BD of the second planetary gear set 2. The second gear cmg2 and the third gear cmg3 are used to simultaneously connect the third rotation axis AE of the first planetary gear set 1 and the third rotation axis BE of the second planetary gear set 2. Referring to FIG. 2 again, the rotational speed of the second rotating shaft AD of the star gear set i of the independently controllable transmission mechanism of the present invention and the rotational speed of the second rotating shaft BD of the second planetary gear set 2 are set to be : nBD=anA〇—疋 nBD and nAD are respectively the second rotating shaft assisting speed of the second planetary gear set 2 and the second rotating shaft milk rotating speed of the first planetary gear set 1. ❹ Xiao Shi 'The invention can independently control the transmission mechanism to the first planetary gear set! - the rotational speed of the rotating shaft OP (energy output end) and the rotational speed of the first-axis CR [control end] of the second planetary gear set 2 are set as follows: ncR = pn 〇 p 疋 where kiss and nOP are respectively The rotation speed of the first rotating shaft clamping end of the second planetary gear set 2 and the first rotating shaft 〇p [energy wheel output end] of the first planetary gear set i. At the same time, the independently controllable transmission mechanism of the present invention sets the rotation speed of the third rotation axis AE of the first planetary gear set ι to the second (four) bribe group 2^三旋_be to the relationship of .nAE^BE ' 200938752 wherein nAE and nBE are respectively the rotation speed of the first planetary rotation speed and the third rotation axis BE of the second planetary gear set 2, and the combination of the four (four) two (four) fine-winter gear group and the second transmission connection group Schematic 'which contains the twenty-three mines, but it is not used to
。請參照第5至27圖所示，本發明第一較佳實施例.之可獨立控制傳動 機構包含二行星齒輪組〔圓形虛線框，對照第3A至3c圖所示〕及二 傳動連接組〔長方型虛線框，對照第4A至4F圖所示〕，其詳細内部 結構已揭示於第3A至3C圖及第4八至仲圖，於此不予贊述。 請再參照第2及5圖所示，本發明第一較佳實施例中該二行星齒 輪組對應於該第-行星齒輪組丨及第二行星齒輪組2，且為兩個正比 值驅動式行星齒輪組，該二傳動連接組對應於該第—傳動連接組3及 第二傳動連接組4。該二行星齒輪組之二行星臂旋轉軸paA及paB及 二中央齒輪旋轉軸Pss2A及Pss2B連接至該二傳動連接組。該二行1 齒輪組之二太陽齒輪旋轉轴Pssl可任意形成該第一行星齒輪組〗之能 量輸出端〔第一旋轉軸0P〕及第二行星齒輪組2之控制端〔第一旋轉 軸CR〕；該二傳動連接組之二旋轉軸cms可任意形成該第一傳動連接 組3之能量輸入端SD及該第二傳動連接組4之自由傳輸端SE。 請再參照第2及6圖所示，本發明第二較佳實施例中該二行星齒 輪組對應於該第一行星齒輪組1及第二行星齒輪組2，且為一個正比 值驅動式行星齒輪組及一個負比值驅動式行星齒輪組，該二傳動連接 組對應於該第一傳動連接組3及第二傳動連接組4。該二行星齒輪組 之二行星臂旋轉軸Pa及na、中央齒輪旋轉軸pss2及環齒輪旋轉軸ns 連接至該二傳動連接組。該二行星齒輪組之二太陽齒輪旋轉軸pssl及 12 200938752 nss可任意形成該帛一行星齒輪虹i之能量輪出端〔第一旋轉軸〇p〕 及第二行星齒輪組2之控制端〔第一旋轉軸CR〕；該二傳動連接組之 一旋轉軸cms可任意形成該第一傳動連接組3之能量輸入端SD及該 第一傳動連接組4之自由傳輸端SE。 π再參照第2及7圖所示’本發明第三較佳實施例中該二行星齒 輪組對應於#第—行星齒輪組i及第二行星齒輪組2，且為—個正比 值驅動式行星#輪組及―個負比值驅動式行星齒輪組，該二傳動連接 0 2對應於該第—傳動連接組3及第二傳純接組4。該二行星齒輪組 之一订星臂旋轉軸坪及na、太陽齒輪旋轉軸pssl及nss連接至該二傳 動連接組。該二行星齒輪組之中央齒輪旋轉軸pss2及環齒輪旋轉軸nrs 可任意形成該第一行星齒輪組1之能量輸出端〔第一旋轉軸OP〕及第 —仃星齒輪組2之控制端〔第一旋轉軸CR〕；該二傳動連接組之二旋 轉軸cms可任意形成該第一傳動連接組3之能量輸入端SD及該第二 傳動連接組4之自由傳輸端SE。 。月再參照第2及8圖所示，本發明第四較佳實施例中該二行星齒 〇 輪組對應於該第—行星齒輪組1及第二行星齒輪組2，且為相同型式 的兩個負比值驅動式行星齒輪組，該二傳動連接組對應於該第一傳動 連接組3及第二傳動連接組4。該二行星齒輪组之二行星臂旋轉軸naA 及naB、環齒輪旋轉軸nrsA及nrsB連接至該二傳動連接組。該二行星 齒輪組之二太陽齒輪旋轉軸nss可任意形成該第一行星齒輪組丨之能 置輸出端〔第一旋轉軸0P〕及第二行星齒輪組2之控制端〔第一旋轉 軸CR〕；該二傳動連接組之二旋轉軸cms可任意形成該第一傳動連接 '、且3之志量輸入端SD及該第二傳動連接組4之自由傳輸端SE。 請再參照第2及9圖所示’本發明第五較佳實施例中該二行星齒 13 200938752 輪組對應於該第一行星齒輪組1及第二行星齒輪組2，且為相同型式 的兩個負比值驅動式彳亍星齒輪組’該二傳動連接組對應於該第一傳動 連接組3及第二傳動連接組4。該二行星齒輪組之二行星臂旋轉抽 及naB、太陽齒輪旋轉軸nssA及nssB連接至該二傳動連接組。該二 行星齒輪組之二環齒輪旋轉軸nrs可任意形成該第—行星齒輪組丨之能 量輸出端〔第一旋轉軸OP〕及第二行星齒輪組2之控制端〔第一旋轉 軸CR〕；該二傳動連接組之二旋轉軸cms可任意形成該第一傳動連接 組3之能量輸入端SD及該第二傳動連接組4之自由傳輸端SE。 明再參照第2及10圖所示，本發明第六較佳實施例中該二行星 齒輪組對應於該第一行星齒輪組1及第二行星齒輪組2，且為兩種不 同型式的兩個負比值驅動式行星齒輪組，該二傳動連接組對應於該第 一傳動連接組3及第二傳動連接組4。該二行星齒輪組之二行星臂旋 轉轴naA及naB、環齒輪旋轉軸及太陽齒輪旋轉軸nssB連接至 譴一傳動連接組。該二行星齒輪組之太陽齒輪旋轉軸nssA及環齒輪旋 轉軸nrsB可任意形辆行星錄組丨之能量輸㈣〔第—旋轉轴 ❾ OP〕及第二行星齒輪組2之控制端〔第一旋轉軸cr〕；該二傳動連 接紙之二旋轉轴Cms可任意形成該第一傳動連接組3之能量輸入端SD 及該第二傳動連接组4之自由傳輸端SE。 請再參照第2及n圖所示，本發明第七較佳實施例巾該二行星 齒輪組對應於料―行録輪組1及第二行星齒輪組2，且為兩個正 比值驅動式行星齒輪組，該二傳動連接組對應於該第一傳動連接組3 及第二傳動連接組4。該二行星齒輪組之行星臂旋雜paA及太陽齒 輪方疋轉軸psslB及—中央齒輪旋轉軸pSS2A及pss2B連接至該二傳動 連接組。該二行星齒輪組之太陽齒輪旋轉軸巧^及行星臂旋轉軸ρΒ 14 200938752 可任意形成該第-行星齒輪之能量輸出端〔第—旋轉轴〇p〕及第 二行星齒輪組2之控繼〔第—旋熟⑶〕；該二伽連触之二旋 轉軸⑽可任意形成該第一傳動連接組$之能量輸入端奶及該第二 傳動連接組4之自由傳輸端SE。 凊再參照第2及12圖所示，本發明第人較佳實施例中該二行星 齒輪組對應_第-行星錄組丨及第二行餘触2，且為兩個正 比值驅動式付錄組，該二傳動連接崎應機第―傳動連接組3 及第二傳動連接組4。該二行星齒輪組之行星轉軸_及太陽齒 輪捷轉軸_B、中央齒輪旋轉軸pss2A及行星臂旋熱_連接至 該二傳動連触。該二行録輪組之太_輪旋絲_Α及中央齒 輪旋轉軸PSS2B可任意形成該第—行1錄組丨之輸出端〔第一 旋轉軸OP〕及第二行星錄組2之控制端〔第—旋轉軸CR〕；該二 傳動連接組之二旋轉軸簡可任意形成該第一傳動連接組3之能量輸 入多而SD及該弟一傳動連接組4之自由傳輸端§e。 凊再參照第2及13圖所示，本發明第九較佳實施例中該二行星 齒輪組對應於該第一行星齒輪組1及第二行星齒輪組2，且為一個正 比值驅動式行星齒輪組及一個負比值驅動式行星齒輪組，該二傳動連 接組對應於該第一傳動連接組3及第二傳動連接組4。該二行星齒輪 組之行星臂旋轉軸pa、太陽齒輪旋轉軸nss、中央齒輪旋轉軸pss2及 環齒輪旋轉軸nrs連接至該二傳動連接組。該二行星齒輪組之太陽齒輪 旋轉軸pssl及行星臂旋轉軸na可任意形成該第一行星齒輪組！之能量 輸出端〔第一旋轉軸OP〕及第二行星齒輪組2之控制端〔第一旋轉軸 CR〕；該二傳動連接組之二旋轉軸cms可任意形成該第一傳動連接組 3之能量輸入端SD及該第二傳動連接組4之自由傳輸端SE。 15 200938752 請再參照第2及Μ _示，本發㈣十較佳實施射該二行星 齒輪組對應於該第—行星齒輪組1及第二行星錄組2，且為-個正 比值驅動式彳了星齒触及—個訊值驅動式行星餘組，該二傳動連 接組對應於該第-傳鱗触3及第二觸連接組4 。該二行星齒輪 組之行星臂;^轉軸pa、環齒輪旋轉軸⑽、巾央齒輪旋轉軸pss〕及太 陽齒輪說轉軸nss連接至該二傳動連接組。該二行星齒輪組之太陽齒 輪旋轉軸PSS1及行星倾轉細&可任意形成該第—行錢輪組i之能 ΐ輸出端〔第-旋轉軸0p〕及第二行星齒輪組2之控制端〔第一旋轉 軸CR〕；該二傳動連接組之二旋轉轴娜可任意形成該第一傳動連接 組3之能量輸入端SD及該第二傳動連接組4之自由傳輸端SE。 明再參照第2及15圖所示，本發明第_一較佳實施例中該二行 星齒輪組對應於該第一行星齒輪組丨及第二行星齒輪組2，且為一個 正比值驅動式行星齒輪組及一個負比值驅動式行星齒輪組，該二傳動 連接組對應於該第一傳動連接組3及第二傳動連接組4。該二;f亍星齒 輪組之太陽齒輪旋轉軸pssl、行星臂旋轉軸na、中央齒輪旋轉軸pss2 及環齒輪旋轉軸nrs連接至該二傳動連接組。該二行星齒輪組之行星臂 旋轉軸Pa及太陽齒輪旋轉軸nss可任意形成該第一行星齒輪組1之能 量輸出端〔第一旋轉軸OP〕及第二行星齒輪組2之控制端〔第一旋轉 軸CR〕；該二傳動連接組之二旋轉軸cms可任意形成該第一傳動連接 組3之能量輸入端SD及該第二傳動連接組4之自由傳輸端SE。 請再參照第2及16圖所示，本發明第十二較佳實施例中該二行 星齒輪組對應於該第一行星齒輪組1及第二行星齒輪組2，且為一個 正比值驅動式行星齒輪組及一個負比值驅動式行星齒輪組’該二傳動 連接組對應於該第一傳動連接纽3及第二傳動連接組4。該二行星齒 16 200938752 輪組之太陽齒輪旋轉軸Pss卜行星臂旋轉軸na、中央齒輪旋轉轴pss2 及太陽齒輪旋轉軸nss連接至該二傳動連接組。該二行星齒輪紐之行 星臂旋轉轴pa及環齒輪旋轉轴nrs可任意形成該第一行星齒輪紐丨之 能量輪出端〔第一旋轉軸OP〕及第二行星齒輪組2之控制端〔第—旋 轉軸CR〕；該二傳動連接组之二旋轉軸cms可任意形成該第—傳動連 接組3之能量輸入端SD及該第二傳動連接組4之自由傳輸端SE。 請再參照第2及17圖所示，本發明第十三較佳實施例中該二行 星齒輪組對應於該第一行星齒輪組1及第二行星齒輪組2，且為—個 正比值驅動式行星齒輪組及一個負比值驅動式行星齒輪組，該二傳動 連接組對應於該第一傳動連接組3及第二傳動連接組4。該二行星齒 輪組之行星臂旋轉軸pa、環齒輪旋轉軸nrs、中央齒輪旋轉軸pss2及 行星臂旋轉軸na連接至該二傳動連接組。該二行星齒輪組之二太陽齒 輪旋轉軸pssl及nss可任意形成該第一行星齒輪組1之能量輪出端〔 第—旋轉軸OP〕及第二行星齒輪組2之控制端〔第一旋轉軸CR〕； 該二傳動連接組之二旋轉軸cms可任意形成該第一傳動連接組3之能 量輪入端SD及該第二傳動連接組4之自由傳輸端SE。 請再參照第2及18圖所示，本發明第十四較佳實施例中該二行 星齒輪組對應於該第一行星齒輪組1及第二行星齒輪組2，且為一個 正比值驅動式行星齒輪組及一個負比值驅動式行星齒輪組，該二傳動 連接組對應於該第一傳動連接組3及第二傳動連接組4。該二行星齒 輪組之行星臂旋轉軸pa、太陽齒輪旋轉軸nss、中央齒輪旋轉軸pss2 及行星臂旋轉軸na連接至該二傳動連接組。該二行星齒輪組之太陽齒 輪旋轉軸pssl及環齒輪旋轉轴nrs可任意形成該第一行星齒輪組1之 能量輸出端〔第一旋轉軸OP〕及第二行星齒輪組2之控制端〔第一旋 17 200938752 轉軸CR〕；該二傳動連接組之二旋轉轴cms可任意形成該第一傳動連 接組3之能量輸入端SD及該第二傳動連接組4之自由傳輸端se。 請再參照第2及19圖所示’本發明第十五較佳實施例中該二行 星齒輪組對應於該第一行星齒輪組1及第二行星齒輪組2，且為相同 型式的兩個負比值驅動式行星齒輪組，該二傳動連接組對應於該第— 傳動連接組3及第二傳動連接組4。該二行星齒輪組之行星臂旋轉軸 naA、太陽齒輪旋轉軸nssB、二環齒輪旋轉軸nrsA及加迅連接至該二 傳動連接組。該二行星齒輪組之太陽齒輪旋轉軸nssA及行星臂旋轉軸 naB可任意形成該第一行星彘輪組！之能量輸出端〔第一旋轉軸〇p〕 及第二行星齒輪組2之控制端〔第一旋轉轴CR〕；該二傳動連接組之 二旋轉軸cms可任意形成該第一傳動連接組3之能量輸入端SD及該 第二傳動連接組4之自由傳輸端SE。 5月再參照第2及20圖所示，本發明第十六較佳實施例中該二行 星齒輪組對應於該第一行星齒輪組丨及第二行星齒輪組2，且為相同 型式的兩個I比值驅動式行星齒輪組，該二傳動連接组對應於該第一 傳動連接組3及第二傳動連接組4。該二行星齒輪組之行星臂旋轉軸 naA、二環齒輪旋轉軸msA及瓜迅及太陽齒輪旋轉軸仍迅連接至該 二傳動連接組。該二行星齒輪組之太陽齒輪旋轉軸nssA及行星臂旋轉 軸naB可任意形成該第一行星齒輪組1之能量輪出端〔第一旋轉軸〇p 〕及第一仃星齒輪組2之控制端〔第一旋轉轴cr〕；該二傳動連接組 之=旋轉轴_可任意形成該第一傳動連接組3之能量輸入端阳及 該第二傳動連接組4之自由傳輪端se。 月U 2及2i ®所示，本發明第十七較佳實施例中該二行 星齒輪組對應於該第—行星餘組1及第二行星齒輪組2，且為相同 18 200938752 型式的兩個負比值驅動式行星齒輪組，該三傳動連接組對應於該第一 傳動連接組3及第二傳動連接组4。該二行星齒輪組之二行星臂旋轉 軸naA及naB、二環齒輪旋轉軸及沉迅連接至該二傳動連接組 。该一行星齒輪組之二太陽齒輪旋轉軸nssA及nssB可任意形成該第 一行星齒輪組1之能量輸出端〔第一旋轉軸〇P〕及第二行星齒輪組2 之控制端〔第-旋轉轴CR〕；該二傳動連接組之二旋轉轴_可任意 形成該第-傳動連接組3之能量輸入端SD及該第二傳動連接纽4之 自由傳輸端SE。 請再參照第2及22圖所示，本發明第十八較佳實施例中該二行 星齒輪組對應於該第-行星齒輪組丨及第二行星齒輪組2，且為相同 型式的兩個貞比娜賦行麵輪組，該二傳鱗接崎應於該第一 傳動連接組3及第二傳動連接組4。該二行星齒輪組之二行星臂旋轉 軸naA及naB、一太陽齒輪旋轉轴脱八及nssB連接至該二傳動連接 組。該二行星錄組之二環齒猶_ ^及她可任意形成該第 -行星齒輪組1之能量輸出端〔第一旋轉軸〇p〕及第二行星齒輪組2 之控制端〔第-旋轉軸CR〕；該二傳動連接組之二旋轉軸_可任意 形成該第-傳動連接組3之能量輸入端SD及該第二傳動連接組^ 自由傳輪端SE。 請再參照第2及23圖所示，本發明第十九較佳實施例中♦亥二行 星齒輪組對應於該第-行星錢組丨及第二行星錄組2，且為兩種 不同型式的兩個負比值驅動切星齒輪組，該二傳動連接組對應於該 第-傳動連接組3及第二傳動連接組〇該二行星齒輪組之二行星臂 旋轉軸naA及naB、環齒輪旋轉轴—及太陽齒輪旋轉轴祕連接 至遠_傳動連接組。該二行麵輪組之太陽齒輪旋雜⑽A及環齒輪 19 200938752 旋轉軸nrsB可任意形成該第一行星齒輪組〗之能量輸出端〔第一旋轉 •軸OP〕及第二行星齒輪組2之控制端〔第一旋轉軸CR〕；該二傳動 連接組之二旋轉軸cms可任意形成該第一傳動連接組3之能量輪入蠕 SD及該第二傳動連接組4之自由傳輸端SE。 請再參照第2及24圖所示，本發明第二十較佳實施例中該二行 星齒輪組對應於該第-行輪組丨及第二行星絲組2，且為兩個 正比值驅動式行星錄組，該二傳動連接㈣應於鮮—傳動達接組 3及第二傳動連接組4。該二行星齒輪組之二太陽齒輪旋轉軸psslA及 psslB、一中央齒輪旋轉軸pss2A及pss2B連接至該二傳動連接組。該 -盯星齒輪組之二行星臂旋娜paA及paB可任意形成鮮—行星齒 輪組1之能量輸出端〔第一旋熱OP〕及第二行星齒輪組2之控制端 〔第-旋轉轴CR〕；該二傳動連接组之二旋轉軸_可任意形成該第 -傳動連接組3之能量輸人端SD及該第二傳動連接組4之自由傳輸 端SE。 請再參照第2及25圖所示，本發明第二十一較佳實施例中該二 Φ 打星齒輪組對應於該第一行星齒輪組1及第二行星齒輪組2，且為一 個正比值驅動式行星齒輪組及一個負比值驅動式行星齒輪組該二傳 動連接組對應於該第一傳動連接組3及第二傳動連接組4。該二行星 齒輪組之二太陽齒輪旋轉軸pssl及nss、中央齒輪旋轉軸pss2及環齒 輪旋轉軸nrs連接至該二傳動連接組。該二行星齒輪組之二行星臂旋轉 軸pa及na可任意形成該第一行星齒輪組丨之能量輸出端〔第一旋轉 轴OP〕及第二行星齒輪組2之控制端〔第一旋轉軸CR〕；該二傳動 連接組之二旋轉軸cms可任意形成該第一傳動連接組3之能量輸入端 SD及該第二傳動連接組4之自由傳輸端SE。 20 200938752 清再參照第2及26圖所示，本發明第二十二較佳實施例中該二 行星齒輪組對應於該第一行星齒輪組】及第二行星齒輪組2，且為相 - ㈣式的兩個負比值驅動式行星齒輪組，該二傳動連接組對應於該第 —傳動連接組3及第二傳動連接纽4。該二行星錄組之二太陽#輪 旋轉軸nssA及nssB 齒輪旋轉軸及otsb連接至該二傳動連 接..且β亥一行星齒輪組之二行星臂旋轉軸滋及祕可任意形成該第 -行星齒輪組1之能量輪出端〔第—旋轉軸〇p〕及第二行星齒輪組2 之控綱〔第-旋轉軸CR〕；該二傳動連接組之二旋轉轴_可任意 形成該第-傳動連接組3之能量輸入端SD及該第二傳動連接組4之 自由傳輸端SE。 請再參照第2及27圖所示，本發明第二十三較佳實施例中該二 订星齒輪組對應於該第-行星齒輪組i及第二行星齒輪組2,且為相 同型式的兩個負比值驅動式行星齒輪組，該二傳動連接組對應於該第 -傳動連接組3及第二傳動連接組4。該二行星齒輪組之二太陽齒輪 旋轉軸nssA丨nssB、二環齒輪旋轉軸鹏A &恤連接至該二傳動連 〇 接組。該二行星錄組之二行星臂旋轉軸naA及naB可任意形成該第 -行星齒輪組1之能量輸出端〔第一旋轉軸〇p〕及第二行星齒輪組2 之控制端〔第-旋轉軸CR〕；該二傳動連接組之二旋轉轴cms可任意 形成該第-傳動連接組3之能量輸入端SD及該第二傳動連接組*之 自由傳輸端SE。 前述較佳實施例僅舉例說明本發明及其技術特徵，該實施例之技 術仍可適當進行各種實質等效修飾及/或#換方奸以實施；因此本 發明之權利範圍須視後附申請專利範圍所界定之範圍為準。 21 200938752 【圖式簡單說明】 第1圖：本發明較佳實施例之可獨立控制傳動機構之亍意^ 。第2 w:树佳實關之可獨結轉_構❹部架構圖 ,第3A至3C圖：本發明較佳實施例之可獨立控制傳動機構採用 行星齒輪組之内部結構圖。 第4A至4F圖：本發明較佳實施例之可獨立控制傳動機構採用 傳動連接組之内部結構圖。 第5至27圖：本發明第一較佳實施例至第二十三較佳實施例之 可獨立控制傳動機構由二行星齒輪組及二傳動連接組之組合示意圖。 【主要元件符號說明】 1 第一行星齒輪組 2 第二行星齒輪組 3 第一傳動連接組 4 第二傳動連接組 OP 第一旋轉轴 AD 第二旋轉軸 AE 第三旋轉軸 CR 第一旋轉軸 BD 第二旋轉軸 BE 第三旋轉軸 SD 能量輸入端 SE 自由傳輸端 psl 太陽齒輪 pssl 太陽齒輪旋轉軸 ps2 中央齒輪 pss2 中央齒輪旋轉轴 ppl 第一行星齒輪 PP2 第二行星齒輪pa 行星臂旋轉軸 ns 太陽齒輪 nss 太陽齒輪旋轉軸 nr 環齒輪 nrs 環齒輪旋轉軸 np 行星齒輪 na 行星臂旋轉軸 cmgl第一齒輪 cmg2 第二齒輪 cmg3第三齒輪 cms 旋轉軸 22. Referring to Figures 5 to 27, the independently controllable transmission mechanism of the first preferred embodiment of the present invention comprises two planetary gear sets (circular dotted frame, as shown in Figures 3A to 3c) and two transmission connection groups. [Rectangular dotted frame, as shown in Figures 4A to 4F], the detailed internal structure of which has been disclosed in Figures 3A to 3C and 4th to 8th, and is not mentioned here. Referring to FIGS. 2 and 5 again, in the first preferred embodiment of the present invention, the two planetary gear sets correspond to the first planetary gear set 丨 and the second planetary gear set 2, and are two proportional drive types. The planetary gear set, the two transmission connection group corresponds to the first transmission connection group 3 and the second transmission connection group 4. The two planetary arm rotating shafts paA and paB and the two central gear rotating shafts Pss2A and Pss2B of the two planetary gear sets are coupled to the two transmission connection groups. The two sun gear rotating shafts Pss1 of the two rows and one gear sets can arbitrarily form the energy output end of the first planetary gear set (the first rotating shaft OP) and the control end of the second planetary gear set 2 (the first rotating shaft CR) The two rotating shafts cms of the two transmission connection groups can arbitrarily form the energy input end SD of the first transmission connection group 3 and the free transmission end SE of the second transmission connection group 4. Referring to FIGS. 2 and 6, in the second preferred embodiment of the present invention, the two planetary gear sets correspond to the first planetary gear set 1 and the second planetary gear set 2, and are a proportional drive planetary. The gear set and a negative ratio driven planetary gear set corresponding to the first transmission connection group 3 and the second transmission connection group 4. The two planetary gear rotating shafts Pa and na, the central gear rotating shaft pss2, and the ring gear rotating shaft ns of the two planetary gear sets are connected to the two transmission connection groups. The two sun gear rotating shafts pssl and 12 200938752 nss of the two planetary gear sets can arbitrarily form the energy wheel output end of the first planetary gear rainbow i (the first rotating shaft 〇p) and the control end of the second planetary gear set 2 The first rotating shaft CR]; the rotating shaft cms of the two transmission connecting groups can arbitrarily form the energy input end SD of the first transmission connection group 3 and the free transmission end SE of the first transmission connection group 4. π Referring to FIGS. 2 and 7 in the third preferred embodiment of the present invention, the two planetary gear sets correspond to the #-th planetary gear set i and the second planetary gear set 2, and are proportional-driven The planetary #wheel and the "negative ratio drive planetary gear set", the two transmission connection 0 2 corresponds to the first transmission connection group 3 and the second transmission pure connection group 4. One of the two planetary gear sets, the star arm rotating shaft and the na, the sun gear rotating shafts pssl and nss are connected to the two-way connecting group. The central gear rotating shaft pss2 and the ring gear rotating shaft nrs of the two planetary gear sets can arbitrarily form the energy output end (first rotating shaft OP) of the first planetary gear set 1 and the control end of the first comet gear set 2 The first rotating shaft CR]; the two rotating shafts cms of the two transmission connecting groups can arbitrarily form the energy input end SD of the first transmission connection group 3 and the free transmission end SE of the second transmission connection group 4. . Referring to FIGS. 2 and 8 again, in the fourth preferred embodiment of the present invention, the two planetary gear sets correspond to the first planetary gear set 1 and the second planetary gear set 2, and are the same type of two. A negative ratio driven planetary gear set corresponding to the first transmission connection group 3 and the second transmission connection group 4 . The two planetary arm rotating shafts naA and naB and the ring gear rotating shafts nrsA and nrsB of the two planetary gear sets are connected to the two transmission connection groups. The two sun gear rotating shafts nss of the two planetary gear sets can arbitrarily form the first output end of the first planetary gear set (the first rotating shaft OP) and the control end of the second planetary gear set 2 (the first rotating shaft CR) The two rotation axes cms of the two transmission connection groups can arbitrarily form the first transmission connection ', and the 3 input terminals SD and the free transmission end SE of the second transmission connection group 4. Referring to FIGS. 2 and 9 respectively, in the fifth preferred embodiment of the present invention, the two planetary teeth 13 200938752 wheel sets correspond to the first planetary gear set 1 and the second planetary gear set 2, and are of the same type. Two negative ratio driven comet gear sets 'the two transmission connection groups correspond to the first transmission connection group 3 and the second transmission connection group 4. The two planetary gears of the two planetary gear sets are rotated and naB, and the sun gear rotating shafts nssA and nssB are connected to the two transmission connection groups. The two-ring gear rotating shaft nrs of the two planetary gear sets can arbitrarily form the energy output end of the first planetary gear set 第一 [first rotating shaft OP] and the control end of the second planetary gear set 2 [first rotating shaft CR] The two rotating shafts cms of the two transmission connection groups can arbitrarily form the energy input end SD of the first transmission connection group 3 and the free transmission end SE of the second transmission connection group 4. Referring to FIGS. 2 and 10, in the sixth preferred embodiment of the present invention, the two planetary gear sets correspond to the first planetary gear set 1 and the second planetary gear set 2, and are two different types of two. A negative ratio driven planetary gear set corresponding to the first transmission connection group 3 and the second transmission connection group 4 . The two planetary gear rotating shafts naA and naB, the ring gear rotating shaft and the sun gear rotating shaft nssB of the two planetary gear sets are connected to the singular transmission connection group. The sun gear rotating shaft nssA and the ring gear rotating shaft nrsB of the two planetary gear sets can be arbitrarily shaped as the energy input of the planetary recording group (four) [the first rotating shaft ❾ OP] and the control end of the second planetary gear set 2 (first The rotating shaft cr]; the two rotating shafts Cms of the two transmission connecting papers can arbitrarily form the energy input end SD of the first transmission connection group 3 and the free transmission end SE of the second transmission connection group 4. Referring to FIGS. 2 and n, the second planetary gear set of the seventh preferred embodiment of the present invention corresponds to the material-recording wheel set 1 and the second planetary gear set 2, and is driven by two proportional values. The planetary gear set, the two transmission connection group corresponds to the first transmission connection group 3 and the second transmission connection group 4. The planetary arm misalignment paA of the two planetary gear sets and the sun gear rotating shaft psslB and the central gear rotating shafts pSS2A and pss2B are connected to the two transmission connection groups. The sun gear rotating shaft of the two planetary gear sets and the planetary arm rotating shaft ρΒ 14 200938752 can form the energy output end of the first planetary gear (the first rotating shaft 〇p) and the control of the second planetary gear set 2 [First-spinning (3)]; the two-gauge two-axis rotating shaft (10) can arbitrarily form the energy input end milk of the first transmission connection group $ and the free transmission end SE of the second transmission connection group 4. Referring to Figures 2 and 12 again, in the preferred embodiment of the present invention, the two planetary gear sets correspond to the _th-planetary group and the second line of the second touch 2, and are two proportional drive-type In the recording group, the two transmissions are connected to the first transmission connection group 3 and the second transmission connection group 4. The planetary shaft _ of the two planetary gear sets _ and the sun gear rotating shaft _B, the central gear rotating shaft pss2A and the planetary arm rotating heat _ are connected to the two transmissions. The two rows of the record wheel set _ wheel wire _ Α and the central gear rotation axis PSS2B can arbitrarily form the output of the first line 1 group 丨 output [first rotation axis OP] and the second planetary record group 2 The end (the first rotating shaft CR); the two rotating shafts of the two transmission connection groups can arbitrarily form the energy input of the first transmission connection group 3 and the free transmission end §e of the SD and the transmission connection group 4. Referring to Figures 2 and 13, in the ninth preferred embodiment of the present invention, the two planetary gear sets correspond to the first planetary gear set 1 and the second planetary gear set 2, and are a proportional drive planetary. The gear set and a negative ratio driven planetary gear set corresponding to the first transmission connection group 3 and the second transmission connection group 4. The planetary arm rotation axis pa, the sun gear rotation axis nss, the center gear rotation axis pss2, and the ring gear rotation axis nrs of the two planetary gear sets are connected to the two transmission connection groups. The sun gear rotating shaft pssl and the planetary arm rotating axis na of the two planetary gear sets can arbitrarily form the first planetary gear set! The energy output end (the first rotating shaft OP) and the control end of the second planetary gear set 2 (the first rotating shaft CR); the two rotating shafts cms of the two transmission connecting groups can arbitrarily form the first transmission connecting group 3 The energy input terminal SD and the free transmission end SE of the second transmission connection group 4. 15 200938752 Please refer to the second and fourth _, the preferred embodiment of the present invention is directed to the two planetary gear sets corresponding to the first planetary gear set 1 and the second planetary record set 2, and is a proportional drive type The star-shaped tooth touches a signal-driven planetary residual group, and the two transmission connection groups correspond to the first-pass scale contact 3 and the second contact connection group 4. The planetary arm of the two planetary gear sets; the shaft shaft pa, the ring gear rotating shaft (10), the towel center gear rotating shaft pss, and the sun gear shaft nss are connected to the two transmission link groups. The sun gear rotating shaft PSS1 and the planetary tilting fines of the two planetary gear sets can arbitrarily form the energy output end of the first money wheel set i (the first rotating shaft 0p) and the control of the second planetary gear set 2 The second rotating shaft CR of the second transmission connection group arbitrarily forms the energy input end SD of the first transmission connection group 3 and the free transmission end SE of the second transmission connection group 4. Referring to FIGS. 2 and 15, in the first preferred embodiment of the present invention, the two planetary gear sets correspond to the first planetary gear set 第二 and the second planetary gear set 2, and are a proportional drive type. The planetary gear set and a negative ratio driven planetary gear set corresponding to the first transmission connection group 3 and the second transmission connection group 4. The sun gear rotation axis pssl, the planetary arm rotation axis na, the central gear rotation axis pss2, and the ring gear rotation axis nrs of the f-star gear set are connected to the two transmission connection groups. The planetary arm rotation axis Pa and the sun gear rotation axis nss of the two planetary gear sets can arbitrarily form the energy output end (first rotation axis OP) of the first planetary gear set 1 and the control end of the second planetary gear set 2 A rotating shaft CR]; the two rotating shafts cms of the two transmission connecting groups can arbitrarily form the energy input end SD of the first transmission connection group 3 and the free transmission end SE of the second transmission connection group 4. Referring to FIGS. 2 and 16, in the twelfth preferred embodiment of the present invention, the two planetary gear sets correspond to the first planetary gear set 1 and the second planetary gear set 2, and are a proportional drive type. The planetary gear set and a negative ratio driven planetary gear set 'the two transmission connection sets correspond to the first transmission connection 3 and the second transmission connection set 4. The two planetary teeth 16 200938752 The sun gear rotating shaft Pss of the wheel set, the planetary arm rotating shaft na, the central gear rotating shaft pss2 and the sun gear rotating shaft nss are connected to the two transmission connection groups. The planetary arm rotation axis pa and the ring gear rotation axis nrs of the two planetary gears can arbitrarily form the energy wheel output end (first rotation axis OP) of the first planetary gear button and the control end of the second planetary gear set 2 The first rotating shaft CR2; the two rotating shafts cms of the two transmission connecting groups can arbitrarily form the energy input end SD of the first transmission connection group 3 and the free transmission end SE of the second transmission connection group 4. Referring to FIGS. 2 and 17, in the thirteenth preferred embodiment of the present invention, the two planetary gear sets correspond to the first planetary gear set 1 and the second planetary gear set 2, and are driven by a proportional ratio. The planetary gear set and a negative ratio driven planetary gear set corresponding to the first transmission connection group 3 and the second transmission connection group 4. The planetary arm rotation axis pa, the ring gear rotation axis nrs, the center gear rotation axis pss2, and the planetary arm rotation axis na of the two planetary gear sets are connected to the two transmission connection groups. The two sun gear rotating shafts pssl and nss of the two planetary gear sets can arbitrarily form the energy wheel output end of the first planetary gear set 1 (the first rotating shaft OP) and the control end of the second planetary gear set 2 (first rotation) The shaft CR]; the two rotating shafts cms of the two transmission connection groups can arbitrarily form the energy wheel end SD of the first transmission connection group 3 and the free transmission end SE of the second transmission connection group 4. Referring to FIGS. 2 and 18, in the fourteenth preferred embodiment of the present invention, the two planetary gear sets correspond to the first planetary gear set 1 and the second planetary gear set 2, and are a proportional drive type. The planetary gear set and a negative ratio driven planetary gear set corresponding to the first transmission connection group 3 and the second transmission connection group 4. The planetary arm rotation axis pa, the sun gear rotation axis nss, the center gear rotation axis pss2, and the planetary arm rotation axis na of the two planetary gear sets are connected to the two transmission connection groups. The sun gear rotating shaft pssl and the ring gear rotating shaft nrs of the two planetary gear sets can arbitrarily form the energy output end (the first rotating shaft OP) of the first planetary gear set 1 and the control end of the second planetary gear set 2 One rotation 17 200938752 shaft CR]; the two rotation axes cms of the two transmission connection groups can arbitrarily form the energy input end SD of the first transmission connection group 3 and the free transmission end se of the second transmission connection group 4. Referring to FIGS. 2 and 19, in the fifteenth preferred embodiment of the present invention, the two planetary gear sets correspond to the first planetary gear set 1 and the second planetary gear set 2, and are two of the same type. A negative ratio driven planetary gear set corresponding to the first transmission connection group 3 and the second transmission connection group 4. The planetary arm rotation axis naA of the two planetary gear sets, the sun gear rotation axis nssB, the two-ring gear rotation axis nrsA, and the acceleration are connected to the two transmission connection groups. The sun gear rotating shaft nssA of the two planetary gear sets and the planetary arm rotating axis naB can arbitrarily form the first planetary wheel set! The energy output end (the first rotation axis 〇p) and the control end of the second planetary gear set 2 (the first rotation axis CR); the two rotation axes cms of the two transmission connection groups can arbitrarily form the first transmission connection group 3 The energy input terminal SD and the free transmission end SE of the second transmission connection group 4. Referring to FIGS. 2 and 20 again, in the sixteenth preferred embodiment of the present invention, the two planetary gear sets correspond to the first planetary gear set 第二 and the second planetary gear set 2, and are the same type of two The first ratio drive planetary gear set corresponds to the first transmission connection group 3 and the second transmission connection group 4. The planetary arm rotating shaft naA of the two planetary gear sets, the two-ring gear rotating shaft msA, and the Gua Xun and the sun gear rotating shaft are still connected to the two transmission connection groups. The sun gear rotating shaft nssA and the planetary arm rotating axis naB of the two planetary gear sets can arbitrarily form the energy wheel output end of the first planetary gear set 1 (the first rotating shaft 〇p) and the control of the first comet gear set 2 The end [first rotating shaft cr]; the two rotating connecting groups = the rotating shaft _ can arbitrarily form the energy input end of the first transmission connection group 3 and the free transmission end se of the second transmission connection group 4. According to the U2 and 2i®, in the seventeenth preferred embodiment of the present invention, the two planetary gear sets correspond to the first planetary subgroup 1 and the second planetary gear set 2, and are the same 18 of the same 18 200938752 type. A negative ratio driven planetary gear set corresponding to the first transmission connection group 3 and the second transmission connection group 4 . The two planetary gear rotating shafts naA and naB of the two planetary gear sets, the two-ring gear rotating shaft and the sun-stop are connected to the two transmission connection groups. The two sun gear rotating shafts nssA and nssB of the one planetary gear set can arbitrarily form the energy output end of the first planetary gear set 1 (the first rotating shaft 〇P) and the control end of the second planetary gear set 2 (the first rotating The shaft CR]; the two rotating shafts of the two transmission connection groups arbitrarily form the energy input terminal SD of the first transmission connection group 3 and the free transmission end SE of the second transmission connection button 4. Referring to FIGS. 2 and 22, in the eighteenth preferred embodiment of the present invention, the two planetary gear sets correspond to the first planetary gear set 丨 and the second planetary gear set 2, and are two of the same type. The 贞bina is assigned to the face wheel set, and the second squad is connected to the first transmission connection group 3 and the second transmission connection group 4. The two planetary gear rotating shafts naA and naB of the two planetary gear sets, a sun gear rotating shaft, and the nssB are connected to the two transmission connecting groups. The second ring gear of the two planetary recording group _ ^ and she can arbitrarily form the energy output end of the first planetary gear set 1 (the first rotating shaft 〇p) and the control end of the second planetary gear set 2 (the first rotation The shaft CR]; the two rotating shafts of the two transmission connection groups arbitrarily form the energy input end SD of the first transmission connection group 3 and the second transmission connection group ^ free transmission end SE. Referring to FIGS. 2 and 23 again, in the nineteenth preferred embodiment of the present invention, the ♦ 二 2 planetary gear set corresponds to the first planetary planet group 第二 and the second planetary record group 2, and is of two different types. The two negative ratios drive the cutting star gear set, and the two transmission connection groups correspond to the first transmission connection group 3 and the second transmission connection group, the two planetary gear rotation axes naA and naB of the two planetary gear sets, and the ring gear rotation The shaft-and-sun gear rotating shaft is connected to the far-drive connection group. The sun gear winding (10) A and the ring gear 19 of the two-row face wheel set 200938752 The rotating shaft nrsB can arbitrarily form the energy output end of the first planetary gear set [first rotation axis OP] and the second planetary gear set 2 The control end [first rotating shaft CR]; the two rotating shafts cms of the two transmission connecting groups can arbitrarily form the energy wheel input creep SD of the first transmission connection group 3 and the free transmission end SE of the second transmission connection group 4. Referring to FIGS. 2 and 24, in the twentieth preferred embodiment of the present invention, the two planetary gear sets correspond to the first-wheel set 第二 and the second planetary set 2, and are driven by two proportional values. For the planetary recording group, the two transmission connections (4) should be in the fresh-drive transmission group 3 and the second transmission connection group 4. The two planetary gear rotating shafts psslA and psslB and one central gear rotating shaft pss2A and pss2B of the two planetary gear sets are connected to the two transmission connection groups. The two planetary arms of the star-steering gear set, the spinners paA and paB, can arbitrarily form the energy output end of the planetary gear set 1 (the first hot air OP) and the control end of the second planetary gear set 2 (the first rotating shaft) CR]; the two rotating shafts of the two transmission connection groups can arbitrarily form the energy input end SD of the first transmission connection group 3 and the free transmission end SE of the second transmission connection group 4. Referring to FIGS. 2 and 25, in the twenty-first preferred embodiment of the present invention, the two Φ star gear set corresponds to the first planetary gear set 1 and the second planetary gear set 2, and is a positive The ratio drive planetary gear set and a negative ratio drive planetary gear set correspond to the first transmission connection group 3 and the second transmission connection group 4. The two planetary gear rotating shafts pssl and nss, the central gear rotating shaft pss2, and the ring gear rotating shaft nrs of the two planetary gear sets are coupled to the two transmission connection groups. The two planetary arm rotating shafts pa and na of the two planetary gear sets can arbitrarily form the energy output end of the first planetary gear set 第一 [the first rotating shaft OP] and the control end of the second planetary gear set 2 (the first rotating shaft) CR]; the two rotating shafts cms of the two transmission connection groups can arbitrarily form the energy input end SD of the first transmission connection group 3 and the free transmission end SE of the second transmission connection group 4. 20 200938752 As further shown in FIGS. 2 and 26, in the twenty-second preferred embodiment of the present invention, the two planetary gear sets correspond to the first planetary gear set and the second planetary gear set 2, and are phase- Two negative ratio driven planetary gear sets of the type (4), the two transmission connection groups corresponding to the first transmission connection group 3 and the second transmission connection 4 . The two planets record group two sun # wheel rotation axis nssA and nssB gear rotation axis and otsb are connected to the two transmission connection.. and the second planetary gear rotation group of the β Haiyi planetary gear set can be arbitrarily formed. The energy wheel output end of the planetary gear set 1 (the first rotating shaft 〇p) and the control unit of the second planetary gear set 2 (the first rotating shaft CR); the two rotating shafts of the two transmission connecting groups can be arbitrarily formed The energy input SD of the transmission connection group 3 and the free transmission end SE of the second transmission connection group 4. Referring to FIGS. 2 and 27, in the twenty-third preferred embodiment of the present invention, the two-spindle gear set corresponds to the first-planetary gear set i and the second planetary gear set 2, and is of the same type. Two negative ratio driven planetary gear sets, the two transmission connection groups corresponding to the first transmission connection group 3 and the second transmission connection group 4. The two planetary gear sets of the two sun gear rotating shaft nssA 丨 nssB, the two-ring gear rotating shaft A & are connected to the two transmission splicing group. The two planetary arm rotation axes naA and naB of the second planetary record group can arbitrarily form the energy output end of the first planetary gear set 1 (first rotation axis 〇p) and the control end of the second planetary gear set 2 (first rotation) The shaft CR]; the two rotating shafts cms of the two transmission connection groups can arbitrarily form the energy input end SD of the first transmission connection group 3 and the free transmission end SE of the second transmission connection group*. The foregoing preferred embodiments are merely illustrative of the present invention and its technical features, and the techniques of the embodiments can be appropriately implemented by various substantial equivalent modifications and/or substitutions; therefore, the scope of the present invention is subject to the appended claims. The scope defined by the scope of patents shall prevail. 21 200938752 [Simple description of the drawings] Fig. 1 is a view of the preferred embodiment of the present invention for independently controlling the transmission mechanism. The second w: the tree can be achieved. The structure of the structure is shown in Figs. 3A to 3C. The independently controllable transmission mechanism of the preferred embodiment of the present invention adopts the internal structure diagram of the planetary gear set. 4A to 4F are drawings showing the internal structure of the drive connection group for the independently controllable transmission mechanism of the preferred embodiment of the present invention. Figures 5 to 27 are schematic diagrams showing the combination of the two planetary gear sets and the two transmission connection groups of the independently controllable transmission mechanism of the first preferred embodiment to the twenty-third preferred embodiment of the present invention. [Main component symbol description] 1 First planetary gear set 2 Second planetary gear set 3 First transmission connection group 4 Second transmission connection group OP First rotation axis AD Second rotation axis AE Third rotation axis CR First rotation axis BD second rotary axis BE third rotary axis SD energy input terminal SE free transmission end psl sun gear pssl sun gear rotation axis ps2 central gear pss2 central gear rotation axis ppl first planetary gear PP2 second planetary gear pa planetary arm rotation axis ns Sun gear nss sun gear rotating shaft nr ring gear nrs ring gear rotating shaft np planetary gear na planetary arm rotating shaft cmgl first gear cmg2 second gear cmg3 third gear cms rotating shaft 22