TWI329173B

TWI329173B - Independently controllable transmission mechanism

Info

Publication number: TWI329173B
Application number: TW97107270A
Authority: TW
Inventors: Guan Shyong Hwang; Der Min Tsay
Original assignee: Univ Nat Sun Yat Sen
Priority date: 2008-03-03
Filing date: 2008-03-03
Publication date: 2010-08-21
Also published as: TW200938752A

Description

1329173 九、發明說明：【發明所屬之技術領域】本發明係關於-種可齡控轉誠構’制是關於蝴二行星齒輪組及二傳動連接組進行可變式控繼量輸人及能量· 控制傳動機構。【先前技術】1329173 IX. Description of the invention: [Technical field to which the invention pertains] The present invention relates to a variable-controlled input and output of a butterfly-type planetary gear set and a second transmission connection group. · Control the transmission mechanism. [Prior Art]

習用傳動機構，如中華民國專利公告第㈣切號之車輪用之變速箱構造，其揭示-主軸上設置有—滑塊，該滑塊之_設有一前進用齒輪及-加力用齒輪，於—連動軸上設置有—反向滑塊，位於該反向滑塊之-側之該連動軸上設置有_靖財職輪及—前進用伞形齒輪’且於該倒顧傘形齒輪及前進財形齒輪之間設置有_最終轴，該最終_由⑽動，藉由該最終軸位於該倒傘形齒輪及前進用傘形齒輪之間，以及該加力赌輪及前賴齒輪亦位於該倒退用伞形齒輪及前進神形錄之間，而可錢魏箱之寬度方向變小，並且利用該連_之倒轉絲及前進用轉錄献該最終轴之一傳動傘軸輪’而可使該變速箱_小型化之目的。惟，該變速箱構造設置有該滑塊’且騎塊必齡產生相互縣義，因而相對降低其功率的傳輸效率。另—傳動機構，如美國專利第6387〇〇4號之、C〇nti_usly Vanable 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，其用以將一第一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JL轉絲。财之，鱗續可變傳触僅將該帛-馬達及 5 1329173 第二馬達設定為固定的兩個動力輸入端，泛單-動力輸出端。簡言之，在傳輸動力上其輕設定為固定的有必要進一步選擇提供可變式㈣《輸人及能餘出之傳動機構，崎合不_ 人傳輸需求。有鑑於此，本發明為了改良上述缺點或符合上述需长，種可獨立控制傳動機構，該傳動機構利用二行星歯輪組及二傳動連接組進行可物讎⑽嶋㈣__♦控制端及 2由祕做魏量輸人端或·輪出端，以達成可獨立控制傳動及二能量傳:效率之目的。另外’該傳動機構未利用任何摩擦滑動元 member〕，以達成提高能量傳輸效率之目的。本發明之主要目的係提供—種可獨立控制傳動機構其利用二行動二傳動連餘進行可默控魏量輸人及能量輸出，該傳 -控制端控制一自由傳輸端自由切換做為能量輸入姆兩鳊本發明達成可獨立控制傳動及提高能量傳輸效率之目的。本㈣之另-目的倾供-财取控辦賴構，細用二行軸接崎L繼輸人繼輸出，該傳利用任何摩擦滑動元件，其達成提高能量傳輸效率之目的。為了達成上述目的，本發明可獨立控制傳動機構包含_第—行星。^二"第—仃星齒輪組、—第—傳動連接組及—第二傳動連接組制姓\ r星齒輪組具有—能量輪出端，該第二行星齒輪_有一控一自由傳亥^傳^!接㈣有一能量輪入端，該第二傳動連接組具有别^上制端控制該自由傳輸端，以自由切換該自由傳輪 6 蠕做為能錢入H能量輸㈣。 …本發明触實關之該第_行星錄組具有―第—旋轉轴、一第一夂轉軸及一第三旋轉軸。务月車又佳貫施例之該第—行星齒輪組之第一旋轉軸為該可獨控制傳動機構之能量輸出端。 I月較佳貫施例之該第一行星齒輪組之第二旋轉軸連接至該第一傳動連接組。本發月較佳貫施例之該第一行星齒輪組之第三旋轉軸連接至該第二傳動連接組。本匙月較佳貫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鶴二行星錄組具H旋轉軸、一第二旋轉軸及一第三旋轉軸。本發明較佳實關之該第二行錢輪敗第―_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軸連接至該第一傳動連接組。本發明較佳實施例之該第二行星齒輪组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组為負比值驅動式行星遙輪組。【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。The conventional transmission mechanism, such as the gearbox structure for the wheel of the fourth section of the Republic of China Patent Announcement, discloses that the main shaft is provided with a slider, and the slider is provided with a forward gear and an afterburning gear. - a reverse slider is provided on the linkage shaft, and the linkage shaft on the side of the reverse slider is provided with a _ Jingcai professional wheel and a forward-shaped bevel gear, and the inverted bevel gear and A forward shaft is disposed between the forward shape gears, and the final_ is moved by (10), wherein the final shaft is located between the inverted bevel gear and the forward bevel gear, and the afterburner and the front gear are also located. Between the inverted bevel gear and the forward character record, the width direction of the money box can be made smaller, and the reverse wire and the forward transcription can be used to transmit one of the final shafts to transmit the umbrella shaft wheel. Make the gearbox _ miniaturized. However, the gearbox structure is provided with the slider' and the riding blocks are mutually dependent, thereby reducing the transmission efficiency of their power. In addition, the transmission mechanism, such as U.S. Patent No. 6,387, 4, C〇nti_usly Vanable Transmission, 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 set only transmits the power of the first motor and the second motor via the first planetary gear set and the second planetary gear set to transmit the JL rotary wire. Fortunately, the variable-size transmission only sets the 帛-motor and 5 1329173 second motors as fixed two power inputs, a single-power output. In short, the light setting of the transmission power is fixed. It is necessary to further choose to provide the variable (4) "transmission and the remaining transmission mechanism, and the convergence is not _ human transmission demand. In view of the above, the present invention can independently control the transmission mechanism in order to improve the above disadvantages or meet the above requirements, and the transmission mechanism utilizes two planetary gear sets and two transmission connection groups to perform the object (10) 嶋 (4) __ ♦ control end and 2 The secret is to reduce the input end or the round end to achieve the purpose of independent control of the transmission and the second energy transmission: efficiency. In addition, the transmission mechanism does not utilize any friction sliding member to achieve the purpose of improving energy transmission efficiency. The main object of the present invention is to provide an independently controllable transmission mechanism that utilizes a second action second transmission balance to perform a measurable variable input and energy output, and the transmission-control terminal controls a free transmission end to freely switch as an energy input. The invention achieves the purpose of independently controlling the transmission and improving the energy transmission efficiency. The other purpose of this (four) is to provide the purpose of improving energy transmission efficiency. In order to achieve the above object, the present invention can independently control the transmission mechanism to include a - planet. ^二"The first comet gear set, the first-drive connection group and the second drive connection group last name\r star gear set has - energy wheel output, the second planetary gear _ has a control one free pass ^传^! (4) has an energy wheel-in end, the second transmission connection group has a different terminal to control the free transmission end, to freely switch the free-wheeling 6 to make money into the H energy input (four). The _ planet record set of the present invention has a "first" rotation axis, a first 夂 rotation axis and a third rotation axis. The first rotating shaft of the first planetary gear set is the energy output end of the independently controllable transmission mechanism. Preferably, the second rotating shaft of the first planetary gear set of the preferred embodiment of the first month is coupled to the first transmission connection set. The third rotating shaft of the first planetary gear set of the preferred embodiment of the present month is coupled to the second transmission connection set. The first planetary gear set of the present preferred embodiment is a proportional drive planetary gear set. The crane second planetary recording set of the preferred embodiment of the present invention has an H rotating shaft, a second rotating shaft and a third rotating shaft. Preferably, the second row of money is defeated by the second line of the invention, and the _axis is the control end of the independently controllable transmission mechanism. The second rotating shaft of the second planetary gear set of the preferred embodiment of the present invention is coupled to the first transmission 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 planetary gear set. The present invention will be described in detail below with reference to the accompanying drawings,

本發明較佳實施例之可獨立控卿動機構可朗於各速傳動相關技術領域’例如：料發電機、風力發 I =速箱——一控^ 〃第1圖揭不本發明較佳實施例之可獨立控制傳動機構之示意圖，第2 本發明較佳實施例之·立控㈣麟構之内部架The independent control mechanism of the preferred embodiment of the present invention can be used in the technical fields related to each speed transmission, for example, the material generator, the wind power I = the speed box, and the first control unit. A schematic diagram of an independently controllable transmission mechanism of an embodiment, a second embodiment of the preferred embodiment of the present invention

勺ir笛第1及2圖所不’本發明較佳實施例之可獨立控制傳動機構以一第一行星齒輪組i、一第二行星齒輪組2、一第—傳動連接电3 及一第二傳動連接組4。請參照第2圖所示’該第—行星齒輪組1具有-第-旋轉轴0P 、-第二旋轉軸AD及-第三旋轉轴处。該第一行星齒輪組i之第一旋轉軸OP為該可獨墟爾動機構之能量輪出端；—行星齒輪The scoop ir flutes 1 and 2 are not the preferred embodiment of the present invention. The independently controllable transmission mechanism is a first planetary gear set i, a second planetary gear set 2, a first transmission connection 3 and a first Two transmission connection group 4. Referring to Fig. 2, the first planetary gear set 1 has a -first rotational axis OP, a second rotational axis AD, and a third rotational axis. The first rotating shaft OP of the first planetary gear set i is the energy wheel output end of the movable mechanism; the planetary gear

組1^第二旋轉軸AD連接至該第-傳動連接組3;該第-行星齒輪組 1之弟二_軸AE連接至該第二傳動連胁4。相對的，該第二行星齒輪組^具有-第-旋熟CR、—第二旋轉軸犯及—第三旋轉轴。亥第一灯星ω輪、、且2之第—旋轉軸CR為該可獨立控制傳動機之控制端；該第二行星齒輪組2之第二旋轉轴BD連接至該第-傳動連接組3，該第二彳由輪組2之第三旋轉細連接至該第二傳動連接組4。此外，該第一傳動連接組3具有一能量輸入端SD，該第二傳動連接組4具有一自由傳輪蠕SE。 „月再參’’?、第1及2圖所不’本發明可獨立控制傳動機構利用該第二行星齒輪組2之控制端〔第1_CR〕控繼第二傳動連接組4 之自由傳輸k SE ’以自由切換該自由傳輸端se做為能量輸入端或能量輸出端。當將該第二傳動連接組4之自由傳輪端犯切換做為能量輸 8 132.9173 入端時，鱗二傳動連接組4之自由傳輸端SE與該第—傳動連捿组3 之能量輸入端SD共同輸入能量。反之，當將該第二傳動連接紐4 自由傳輸端SE切換做為能量輸出端時，該第二傳動連接組* 輸端SE與該第一行星齒輪組1之第一旋轉轴〇p〔能量輪出端〕共同輸出能量。弟3A至3C圖揭示本發明較佳實施例之可獨立控制傳動機構p 用行星齒輪組之内部結構圖’其包含三種行星齒輪組之内部結 1:1 9 但其並非用以限定本發明。The group 1^ second rotation axis AD is connected to the first-drive connection group 3; the second-axis AE of the first-planetary gear set 1 is connected to the second transmission link 4. In contrast, the second planetary gear set has a - first-rotating CR, a second rotating shaft, and a third rotating shaft. The first light star ω wheel, and the second one - the rotating shaft CR is the control end of the independently controllable transmission; the second rotating shaft BD of the second planetary gear set 2 is connected to the first transmission connection group 3 The second turn is connected to the second drive connection group 4 by a third rotation of the wheel set 2. Furthermore, the first transmission connection 3 has an energy input SD, and the second transmission connection 4 has a freewheeling SE. „月再参''?, Figures 1 and 2 do not 'the invention can independently control the transmission mechanism using the control end of the second planetary gear set 2 (1_CR) to control the free transmission of the second transmission connection group 4 SE 'freely switches the free transmission end se as an energy input or an energy output. When the free transmission end of the second transmission connection group 4 is switched as an energy input 8 132.9173, the scale 2 transmission connection The free transmission terminal SE of the group 4 inputs energy together with the energy input terminal SD of the first transmission linkage group 3. Conversely, when the second transmission connection button 4 free transmission terminal SE is switched as the energy output terminal, the first The second transmission connection group * the output end SE and the first rotation axis 〇p [energy wheel output end] of the first planetary gear set 1 output energy together. The brothers 3A to 3C show the independently controllable transmission of the preferred embodiment of the present invention. The internal structure of the planetary gear set of the mechanism p 'which contains the internal knots of the three planetary gear sets 1:1 9 is not intended to limit the invention.

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、_第_ 行星齒輪pp卜一第二行星齒輪pp2及一行星臂旋轉軸pa。該—第_ 行星齒輪ρρΐ及第二行星齒輪pp2嚅合該太陽齒輪psl及中央齒輪ps2 。該太陽齒輪旋轉軸pssl及行星臂旋轉轴pa為共軸。當該行星臂旋轉軸pa固定不動時，該太陽齒輪旋轉軸pssl及中央齒輪旋轉軸pss2之旋轉方向為相同方向，且其轉速比值為正。該行星齒輪組係屬正比值驅動式行星齒輪組。Referring to FIG. 3A, the planetary gear set includes a sun gear ps1, a sun gear rotation axis pssl, a center gear ps2, a central gear rotation axis pss2, a _ planet gear pp, and a second planet gear pp2. And a planetary arm rotation axis pa. The -the _ planet gear ρρ ΐ and the second planet gear pp2 converge the sun gear ps1 and the center gear ps2. The sun gear rotation axis pssl and the planetary arm rotation axis pa are coaxial. When the planetary arm rotation axis pa is stationary, the rotation directions of the sun gear rotation axis pssl and the center gear rotation axis pss2 are the same direction, and the rotation speed ratio is positive. The planetary gear set is a proportional drive planetary gear set.

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OP、第二旋轉轴AD及第三旋轉轴处。或者’該太陽齒輪旋轉軸 pssl、中央齒輪旋轉軸pss2及行星臂方疋轉軸Pa可做為5亥弟二行星齒輪組2之第一旋轉軸CR、第二旋轉軸BD及第三旋轉軸BE。請參照第3B及3C圖所示，該行星齒輪組包含一太陽齒輪ns、一太陽齒輪旋轉軸nss、一環齒輸肛、一環齒輪旋轉軸nrs、至少一行星齒輪np及一行星臂旋轉柏na。該二行星齒輪組係屬兩種不同型式的 9 1329173 負比值驅動式行星齒輪組。凊再參照第3B圖所不，该太陽齒輪旋轉轴nss及行星臂旋轉軸 na為共軸。當該行星臂旋轉軸na固定不動時，該太陽齒輪旋轉袖脱及環齒輪旋_nrs之旋轉方向為相反額，料轉速比值為負。請再參照第3C圖所示’該環齒輪旋轉軸邮及行星臂旋轉轴旭為共軸。當該行星臂旋轉軸na固定不動時，該太陽齒輪旋轉抽脱及環齒輪旋轉軸nrs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圖所示，該太陽齒輪旋轉轴、環齒輪旋轉軸nrs及行星臂旋轉軸na可做為該第一行星齒輪組丨之第一旋轉轴OP、第二旋轉軸AD及第三旋轉軸ae ;或者，該太陽齒輪旋轉軸nSS、環齒輪旋轉軸nrs及行星臂旋轉軸na可做為該第二行星齒輪組 2之第一旋轉軸CR、第二旋轉軸BD及第三旋轉軸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接組之内部結構圖，其包含六種傳動連接組之内部結構，但其並非用以限定本發明。請參照第4A至4F圖所示，該傳動連接组包含一第一齒輪cmgl 、一旋轉軸cms、一第二齒輪(；„^2及一第三齒輪cmg3。該第—齒輪 cmg 1嚅合該第二齒輪cmg2及第三齒輪cmg3 ’且該第二齒輪咖故及第二齒輪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cmg3皆為單一轉軸。請再參照第4B圖所示，該第二齒輪cmg2為共軸之外軸，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，該第二齒輪cmg2及第三齒輪cmg3皆為共軸之外轴。請 10 132.9173 再參照第4E圖所示，該第二齒輪cmg2為共輛之外軸，而該第二齒輪 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皆為共軸之内轴。請再參照第2及4A至4F圖所示，該傳動連接紐夕#姑虹疋轉轴cmsReferring to FIGS. 2 and 3A again, the sun gear rotating shaft Pss1, 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 rotating shaft. Alternatively, the sun gear rotation axis pssl, the central gear rotation axis pss2, and the planetary arm rotation axis Pa can be used as the first rotation axis CR, the second rotation axis BD, and the third rotation axis BE of the 5th Heidi 2 planetary gear set 2. . Referring to Figures 3B and 3C, the planetary gear set includes a sun gear ns, a sun gear rotation axis nss, a ring gear anal, a ring gear rotation axis nrs, at least one planet gear np, and a planet arm rotation cyna . The two planetary gear sets are of two different types of 9 1329173 negative ratio driven planetary gear sets. Referring again to Fig. 3B, the sun gear rotation axis nss and the planetary arm rotation axis na are coaxial. When the rotation axis na of the planetary arm is fixed, the rotation direction of the sun gear rotating sleeve and the ring gear rotation _nrs are opposite, and the material rotation speed ratio is negative. Please refer to the figure 3C for the ring gear rotation axis and the planetary arm rotation axis as the common axis. When the rotation axis na of the planetary arm is fixed, the rotation direction of the sun gear is released and the rotation direction of the ring gear rotation axis nrs is opposite, and the rotation speed ratio is negative. Referring to FIGS. 2, 3B and 3C again, the sun gear rotating shaft, the ring gear rotating shaft nrs and the planetary arm rotating axis na can be used as the first rotating shaft OP and the second rotation of the first planetary gear set 丨The axis AD and the third rotation axis ae; or the sun gear rotation axis nSS, the ring gear rotation axis nrs, and the planetary arm rotation axis na can be used as the first rotation axis CR and the second rotation axis of the second planetary gear set 2 BD and third rotating shaft BE. 4A through 4F are diagrams showing the internal structure of a driveable connection set for an independently controllable transmission mechanism in accordance with a preferred embodiment of the present invention, which includes the internal structure of the six drive connection sets, but is not intended to limit the present invention. Referring to Figures 4A to 4F, the transmission connection group includes a first gear cmgl, a rotation axis cms, a second gear (; „^2 and a third gear cmg3. The first gear cmg 1 is combined The second gear cmg2 and the third gear cmg3′ and the second gear tooth and the second gear cmg3 may be selected from a single shaft, a coaxial outer shaft and a coaxial inner shaft. Referring to FIG. 4A, The second gear cmg2 and the third gear cmg3 are each a single rotating shaft. Referring to FIG. 4B again, the second gear cmg2 is a coaxial outer shaft, and the third gear cmg3 is a single rotating shaft. As shown in 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 second gear cmg2 and the third gear cmg3 are coaxial. External axis. Please refer to Figure 4E. The second gear cmg2 is the external shaft of the common vehicle, and the second gear cmg3 is the coaxial inner shaft. Please refer to the figure 4F again. The second gear and the third gear cmg3 are both coaxial inner shafts. Please refer to Figures 2 and 4A to 4F again, the transmission is connected to New Zealand #姑Cloth shaft cms

選擇做為該第一傳動連接組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cmg3用以同护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 旋轉軸BD。該第二齒輪cmg2及第三齒輪咖妇用以同時連接該第一行星窗輪組1之第三旋轉軸AE及該第二行星齒輪組2之第三^触請再參照第2圖所示，本發明之可獨立控制傳動機構將— 星齒輪組1之第二旋轉軸AD之轉速與該第二行星齒 "仃轉軸BD之轉速設定為關係式為：ηΒϋ=αηΑ〇、第-旋其中nBD及nAD分別為該第二行星齒輪組2之第轉速及該第-行星齒輪组丨之第二旋轉轴奶之轉速。 BD之The energy input SD of the first transmission connection group 3 or the free transmission end SE of the second transmission connection group 4 is selected. The second gear cmg2 and the third gear cmg3 are used to connect the second rotation axis AD of the first planetary gear set 1 and the second planetary gear set 2 rotation axis BD. The second gear cmg2 and the third gears are used to simultaneously connect the third rotating shaft AE of the first planetary wheel set 1 and the third contact of the second planetary gear set 2, and refer to FIG. 2 again. The independently controllable transmission mechanism of the present invention sets the rotational speed of the second rotational axis AD of the star gear set 1 to the rotational speed of the second planetary gear "the rotational axis BD as: ηΒϋ=αηΑ〇, first-rotation Wherein nBD and nAD are the rotational speed of the second planetary gear set 2 and the rotational speed of the second rotating shaft of the first planetary gear set. BD

同時，本發敗可彳_娜賴婦鶴—行星 -旋轉軸QP〔《輸出端〕之轉速與鄕二行星錄，第= 軸CR [控制端〕之轉速設定為關係式為：ncn 弟-喊其中吻及¥分別為該第二行星齒輪組2之第一旋轉㈣制端〕之轉速及邊第一行星齒輪二之轉速。 t且1之第-旋轉軸op〔能量輸出端〕同時，本發.可獨立控爾動機構縣第—行三旋轉軸AE之轉速與該第二卜铷、'且1之弟定為關係式為：ηΑΕ=ηΒΕ ω、，且2之第三旋轉細之轉速設 1329173At the same time, the defeat of the 彳娜娜娜娜娜娜娜娜娜娜娜娜娜娜娜娜娜娜娜娜娜娜娜娜娜娜娜娜娜娜娜娜娜娜娜娜娜娜娜娜娜娜娜娜娜娜娜娜The middle of the rotation of the first planetary gear set 2 and the rotational speed of the first planetary gear 2 are respectively indicated by the kiss and the ¥ respectively. t and the first-rotation axis op [energy output terminal] At the same time, the rotational speed of the first-row three-rotation axis AE of the independent controllable mechanism is determined by the second dice, and the brother of the 1st The formula is: ηΑΕ=ηΒΕ ω, and the third rotation fine rotation speed of 2 is set to 1319173

’、中ηΑε及nBE分別為該第—行星齒輪組工之第三旋轉軸处轉速及該第二行星齒輪組2之第三旋轉軸Μ之轉速。弟5至27圖揭示本發明第—較佳實施例至第二十三較佳實施例之^^控轉動機構由二行星齒輪減二傳動連接組之組合示意圖 ’ΐ包!？十三種傳動纽合之較佳實施例，但·其並非用以限定本發明叫參知、第5至π騎示’本發明第—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Μ至仲圖所示〕，其詳細内部結構已揭示於第3A至3C圖及第4A至4F圖，於此不予費述。凊再參照第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一行星齒輪組及第二行星齒輪組2，且為兩個正比值驅動式行録輪組，該二傳動連接_應於該第—傳輯接組3及第-傳動連接組4。該二行星齒輪組之二行星臂旋轉轴Μ及_及 -中央齒鱗雜pss2A及pss2B連接至該二傳树接組。該二行星齒輪組之二太陽齒輪旋轉軸pssl可任意形成該第—行星齒輪組丄之能And η Α ε and n BE are the rotational speeds of the third rotational axis of the first planetary gear set and the third rotational rotational speed of the second planetary gear set 2, respectively. Figures 5 to 27 show a combination of the two planetary gear reduction transmission connection groups of the second to third preferred embodiments of the present invention. A preferred embodiment of the thirteen transmissions, but it is not intended to limit the invention, and the fifth to π ride shows that the independently controllable transmission mechanism of the first preferred embodiment of the present invention comprises two planetary gears. Group [circular dotted frame, as shown in Figures 3A to 3c] and two transmission connection groups [rectangled dotted frame, as shown in the second to the middle), the detailed internal structure of which is disclosed in Figures 3A to 3C And Figures 4A to 4F, which are not mentioned here. Referring to FIGS. 2 and 5, in the first 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 two proportional drive rows. The recording wheel set, the two transmission connections _ should be in the first-to-transmission group 3 and the first-drive connection group 4. The two planetary arm rotating shafts _ and _ and - the central tooth scales pss2A and pss2B of the two planetary gear sets are connected to the second tree. The two sun gear rotating shafts pssl of the two planetary gear sets can arbitrarily form the energy of the first planetary gear set

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_可任意形成該第—傳動連接 ’’且3之迠量輸入端§d及該第二傳動連接組4之自由傳輪端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[行星齒輪組丨及第二行星錄組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。該二行星齒輪組之二行星臂旋轉軸pa及na、中央齒輪旋轉軸pss2及環齒輪旋轉轴仍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pa〗及 12 1329173 nss可任意形成該第-行星齒輪组！之能量輪出端〔第—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-傳動連接組3之能量輸入端如及該第二傳動連接組4之自由傳輸端SE。請再參照第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鱗-行星齒輪組i及第二行星齒輪组2，I為—個正比值驅動式行錢胁及-個貞味驅喊似絲組，該三傳動連接組對應於該第-傳紐触3及第二傳鱗触4。該二行星齒輪組之二行星臂旋轉軸pa及na、太陽齒輪旋轉軸_及脱連接至該二傳動連接組。該二行星雜結難_ _及環雜雜轴肥可任意形成該第-行星齒輪組丨之能量輸出端〔第—旋轉軸〇p〕及第二行星齒輪組2之控_〔第—旋轉軸CR〕；該二傳動連接組之二旋轉軸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8 ®所示，本發明第啸佳實施例巾該二行星齒輪組對應於料-行雜魅丨及第二行星錄組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。該二行星齒輪組之二行星臂旋轉軸祕及naB、環錄轉轴耐及她連接_二傳滅触。該二行星，輪組之二太陽齒輪旋轉軸nss可任意形成該第—行星齒輪組^之能 1輸出端〔第-旋轉軸OP〕及第二行星齒輪組2之控制端〔第一旋轉軸CR〕’ 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I輸入端SD及該第二傳動連接組*之自由傳輸端犯。月再〜、第2及9圖所示’本發明第五較佳實施例中該二行星齒 13 132,9173 輪組對應於該第一行星齒輪組1及第二行星齒輪组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。該二行星齒輪組之二行星臂旋轉轴加八及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可任意形成該第一行星齒輪組丨之能 ϊ輸出端〔第一旋轉軸0P〕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丨及第二行星齒輪組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軸naA及naB、環齒輪旋轉軸加认及太陽齒輪旋轉軸肥出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及環齒輪旋轉軸nrsB可任意形成該第一行星齒輪—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—旋轉轴CR〕；該二傳動連接組之二旋轉軸cms可任意形銳第一傳動連接組3之能量輸入端沁及該第二傳動連接組4之自由傳輸端SE。请再參照第2及11麟示，本發明第七較佳實施例巾該二行星齒輪組對應_第-行錢輪組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-傳動連触4。該二行星#輪組之行星倾轉軸一及太陽齒輪方疋轉軸psslB及二中央齒輪旋轉軸pss2A及pss2B連接至該二傳動連接組。該二行星齒輪組之太陽齒輪旋_ _及行星臂旋轉轴_ 14 1329173 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〔第一旋轉軸CR〕；該二傳動連接级之二旋轉軸ems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12圖所示’本發明第八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轉軸paA及太陽齒輪旋轉軸psslB、中央齒輪旋轉軸pss2A及行星臂旋轉軸paB連接至 δ亥一傳動連接組。該二行星齒輪組之太陽齒輪旋轉軸pSSiA及中央齒輪旋轉軸pss2B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。請再參照第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、'且之行星臂旋轉軸pa '太陽齒輪旋轉軸nss、中央齒輪旋轉軸pss2及 %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1之能量輪出端〔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袖 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 1329173 請再參照第2及14圖所示’本發明第十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、環齒輪旋轉軸nrs、中央齒輪旋轉軸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1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15圖所示’本發明第十一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组。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。请再參照第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s亥第一傳動連接組3及第二傳動連接組4。該二行星齒 16 丄輪組之太陽齒輪旋轉軸㈣、行星臂旋轉軸na、中央齒輪旋轉轴_ -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 _ ^旋轉軸邱及環食輪旋轉轴nrs可任意形成該第一行星齒輪组】之 - 知輸出端〔第―旋難〇Ρ〕及第讀星組2之控綱〔第一旋轉，CR〕；該二傳動連接組之二旋轉軸⑽可任意形成該第—傳動連 I塁輸入端SD及该第二傳動連接組4之自由傳輸端se。睛再參照第2及17圖所示，本發明第十三較佳實施例中該二行 φ 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錄域—個組健賦行星錄組，該二傳動連接细對應於該第—傳動連接組3及第二傳動連接組*。該二行星齒輪^之仃星仏雜pa、環錄旋轉軸⑽、巾央齒輪旋雜pss2及订生〇疋轉軸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轴㈣及nss可㈣形成該第—行星齒輪組丨之能量輸出端〔第-旋轉軸0P〕及第二行星齒輪組2之控制端〔第一旋轉轴⑻；該二傳動連接組之二旋轉軸ems可任意形成該第—傳動連接組3之能 φ 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18 _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-行星錄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-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、太陽齒輪旋轉軸啦、中央齒輪旋轉轴_ 及行星臂旋轉轴na連接至該二傳動連接組。該二行·輪組之太陽齒輪旋轉軸PSS1及環齒輪旋轉軸邮可任意形成該第一行星齒輪組】之能量輸出端〔第-旋轉軸OP〕及第二行星齒輪組2之控制端〔第一旋 17 132.9173 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§£。凊再參照第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nrsB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及行星臂旋轉轴 naB可任意形成該第一行星齒輪組1之能量輸出端〔第一旋轉幸由〇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 •一叙轉轴cms可任意形成s亥第一傳動連接組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及第一傳動連接組4。该二行星齒輪組之行星臂旋轉轴 naA、二環齒輪旋轉軸nrsA及nrsB及太陽齒輪旋轉軸nssB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21圖所示’本發明第十七較佳實施例中該二行星齒輪組對應於該第一行星齒輪組1及第二行星齒輪組2，且為相同 18 132.9173 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軸naA及naB、二環齒輪旋轉軸nrsA及nrSB連接至該二傳動連接組。邊一行星齒輪組之二太陽齒輪旋轉轴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P，?、弟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s亥第一行星齒輪組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、二太陽齒輪旋轉軸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及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23圖所示，本發明第十九較佳實施例中該二行星齒輪組對應於該第-行星齒輪組！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-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、環齒輪旋轉轴nrsA及太陽齒輪旋轉軸nssB連接至泫二傳動連接組。該二行星齒輪組之太陽齒輪旋轉軸nssA及環齒輪 19 132.9173 旋轉軸nrsB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OP〕及第二行星齒輪組2之控制端〔第一旋轉軸CRJ ;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一行星齒輪組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及第一傳動連接組4。該二行星齒輪組之二太陽齒輪旋轉抽psslA及 psslB、二中央齒輪旋轉軸pSS2A及pss2B連接至該二傳動連接组。該二行星齒輪組之二行星臂旋轉軸paA及paB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OP〕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。 '•月再參照第2及25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-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_輪旋轉軸pssl及⑽、中央齒輪_軸_及環齒輪旋轉軸nrs連接傳動連接纟且。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—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〔第一旋轉抽⑶〕：該二傳動連接組之二旋轉軸ems可任意形成該第一傳動連接組3之能量輸入端 SD及该第一傳動連接組4之自由傳輸端。 20 132.9173 '•月再參照第2及26圖所示，本發明第二十二較佳實施例中該二仃星齒輪崎應於該第—行星絲組丨及第二行星齒触2，且為相同型式的兩個負比值驅動式行1齒輪組，該二傳動連接輯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疋轉轴nssA及nssB、一環齒輪旋轉轴j^sA及沉必連接至該二傳動連妾'、且。亥一行星齒輪組之二行星臂旋轉軸naA及naB可任意形成該第 -仃星齒輪組1之能量輸出端〔第—旋絲〇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。清再參照第2及27圖所示，本發明第二十三較佳實施例中該二仃星齒輪崎應於該第-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方疋轉軸nssA及nssB、二環齒輪旋轉軸j^sa及沉出連接至該二傳動連接、·且j一行星齒輪組^—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。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/或替換方式予以實施；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。 21 132.9173 【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示▲ 第2圖：本發明較佳實補之可獨立控轉動機構之内部=圖第3A至3C圖：本發明較佳實施例之可獨立控制傳動機行星齒輪組之内部結構圖。木用第4A至#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。 *a measuring wheel output end (the first rotating shaft OP) and a control end of the second planetary gear set 2 (the first rotating shaft CR), and the two rotating shafts of the two transmission connecting groups can arbitrarily form the first transmission connection '' 3 is the input terminal §d and the free transmission end SE of the second transmission connection group 4. Referring to FIGS. 2 and 6 respectively, in the second preferred embodiment of the present invention, the two planetary gear sets correspond to the [planetary gear set 第二 and the second planetary record 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 of the two planetary gear sets are still connected to the two transmission connecting groups ◎ the two planetary gear sets of the two sun gear rotating shafts pa and 12 1329173 Nss can form this first planetary gear set arbitrarily! The energy wheel 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 connection axes of the two transmission connection groups can arbitrarily form the first transmission connection group The energy input of the 3 is the free transmission end SE of the second transmission connection group 4. Referring to FIGS. 2 and 7, in the third preferred embodiment of the present invention, the two planetary gear sets correspond to the scale-planetary gear set i and the second planetary gear set 2, and I is a proportional drive type. Qian Weihe - a scented screaming group, the three transmission connection group corresponds to the first - pass button 3 and the second pass button 4. The two planetary gear rotating shafts pa and na, the sun gear rotating shaft _, and the two planetary gear sets are disconnected to the two-way transmission group. The two planetary miscellaneous _ _ and the ring heterozygous fertilizer can arbitrarily form the energy output end of the first planetary gear set 第 [the first rotating shaft 〇 p] and the control of the second planetary gear set 2 _ [the 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 4. Referring to Figures 2 and 8 again, the second planetary gear set of the present invention corresponds to the material-line and the second planetary record group 2, and is driven by two negative ratios of the same type. The planetary gear set, the two transmission connection groups correspond to the first transmission connection group 3 and the second transmission connection group 4. The two planetary gear sets of the two planetary arm rotation axis secret naB, the ring recording shaft resistance to her connection _ two pass the touch. The two planets, the second sun gear rotating shaft nss of the wheel set can arbitrarily form the 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 (the first rotating shaft) CR] 'The two rotating shafts of the transmission connection group _ can arbitrarily form the free transmission end of the energy input I terminal SD of the first transmission connection group 3 and the second transmission connection group*. In the fifth preferred embodiment of the present invention, the two planetary teeth 13 132, 9173 wheel sets correspond to the first planetary gear set 1 and the second planetary gear set 2, and are The two negative ratio driven planetary gear sets of the same type correspond to the first transmission connection group 3 and the second transmission connection group 4. The two planetary gear rotating shafts of the two planetary gear sets add eight 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 (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 10, in the sixth 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 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 of the two planetary gear sets, the ring gear rotating shaft and the sun gear rotating shaft are connected to the two transmission connecting groups. The sun gear rotating shaft nssA and the ring gear rotating shaft nrsB of the two planetary gear sets can arbitrarily form the energy output end of the first planetary gear (the first rotating shaft OP) and the control end of the second planetary gear set 2 (the first) The rotating shaft CR]; the two rotating shafts cms of the two transmission connecting groups can arbitrarily sharpen the energy input end 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 11 respectively, in the seventh preferred embodiment of the present invention, the two planetary gear sets correspond to the first-front wheel set 1 and the second planetary gear set 2, and are two proportional-driven planets. The gear set, the two transmission connection group corresponds to the first transmission connection group 3 and the first transmission contact 4 . The planetary tilting shaft 1 of the two planetary # wheel sets and the sun gear rotating shaft psslB and the two central gear rotating shafts pss2A and pss2B are connected to the two transmission connecting groups. The sun gear rotation __ and the planetary arm rotation axis _ 14 1329173 of the two planetary gear sets can arbitrarily form the energy output end of the first planetary gear set 1 (the first rotation axis 〇p) and the control of the second planetary gear set 2 The first rotating shaft ems of the two transmission connection stages 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 12, in the eighth 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 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 planetary arm rotation axis paA and the sun gear rotation axis psslB, the central gear rotation axis pss2A, and the planetary arm rotation axis paB of the two planetary gear sets are connected to the δHai transmission connection group. The sun gear rotating shaft pSSiA and the central gear rotating shaft pss2B of the two planetary gear sets can arbitrarily form the energy output end (the first rotating shaft OP) of the first planetary gear set] 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 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 two planetary gears, 'and the planetary arm rotation axis pa', the sun gear rotation axis nss, the central gear rotation axis pss2, and the % gear rotation axis nrs 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 energy wheel output end (first rotating shaft OP) of the first planetary gear set 1 and the control end of the second planetary gear set 2 The first rotating shaft CR], the two rotating sleeves 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. 15 1329173 Referring again to FIGS. 2 and 14 in the tenth 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 sun gear rotation axis nss 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 energy output end (first rotating shaft 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 the second and preferred embodiments 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 sun gear rotation axis pssl, the planetary arm rotation axis na, 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 planetary arm rotating shaft pa and the sun gear rotating shaft nss 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 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 correspond to the first transmission connection group 3 and the second transmission connection group 4. The sun gear rotating shaft (four) of the two planetary teeth 16 轮 wheel set, the planetary arm rotating shaft na, the central gear rotating shaft _ - and the sun gear rotating shaft nSS are connected to the two transmission connecting groups. The two planetary gears _ ^ Rotary axis Qiu and the hovering wheel rotation axis nrs can arbitrarily form the first planetary gear set] - the output terminal (the first rotation difficult) and the reading of the star group 2 The first rotating shaft (10) of the two transmission connection groups can arbitrarily form the first transmission input terminal SD 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-row 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-driven planetary recording field is a group of the hard-moving planetary recording group, and the two transmission connections are finely corresponding to the first transmission connection group 3 and the second transmission connection group*. The two planetary gears, the comet doping pa, the circular recording rotating shaft (10), the towel center gear pss2, and the customized rotating shaft na are connected to the two transmission connection groups. The two sun gear rotating shafts (four) and nss (four) of the two planetary gear sets form an energy output end of the first planetary gear set (the first rotating shaft OP) and a control end of the second planetary gear set 2 (the first rotating shaft) (8); The two rotating shafts ems of the two transmission connection groups can 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 group 4. Referring to FIGS. 2 and 18 again, in the fourteenth preferred embodiment of the present invention, the two planetary gear sets correspond to the first planetary record set 第二 and the second planetary gear set 2, and are a proportional drive planetary. The gear set and a negative ratio driven planetary gear set correspond 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, the central gear rotation axis _, and the planetary arm rotation axis na of the two planetary gear sets are coupled to the two transmission connection groups. The sun gear rotating shaft PSS1 and the ring gear rotating shaft of the two rows and wheels can arbitrarily form the energy output end (the first rotating shaft OP) of the first planetary gear set and the control end of the second planetary gear set 2 The first rotation 17 132.9173 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 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. The negative ratio driven planetary gear set 'the two transmission connection groups correspond 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 axes nrSA and nrsB are 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 output end of the first planetary gear set 1 (the first rotation is 〇p) and the control end of the second planetary gear set 2 [First rotating shaft CR]; the first 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 second transmission connection group 4. Referring to FIGS. 2 and 20, in the sixteenth 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. The negative ratio driven planetary gear set corresponds to the first transmission connection group 3 and the first transmission connection group 4. The planetary arm rotation axis naA of the two planetary gear sets, the two-ring gear rotation axes nrsA and nrsB, and the sun gear rotation axis nssB are 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 output end (the first rotating shaft 〇p) of the first planetary gear set 1 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 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 the second and second preferred embodiments 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 18 132.9173 type. Two negative ratio driven planetary 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 arm rotating shafts naA and naB and the two-ring gear rotating shafts nrsA and nrSB of the two planetary gear sets are coupled 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 (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 4. . In the eighteenth 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 Two negative ratio driven planetary gear sets of the same type, the two transmission connection groups corresponding to the first transmission connection group 3 and the second transmission connection group 4. The two planetary gear rotating shafts naA and naB and the two sun gear rotating shafts nssA and nssB of the two planetary gear sets are coupled to the two transmission connection groups. a two-ring gear rotating shaft of the two planetary gear sets and an energy wheel output end (first rotating shaft 〇p) of the first planetary gear set 1 and a 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 again to Figures 2 and 23, in the nineteenth preferred embodiment of the present invention, the two planetary gear set corresponds to the first planetary gear set! And the second planetary gear set 2, and two different types of 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 rotating shafts naA and naB, the ring gear rotating shaft nrsA and the sun gear rotating shaft nssB of the two planetary gear sets are connected to the second transmission connecting group. The sun gear rotating shaft nssA and the ring gear 19 132.9173 rotating shaft nrsB 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 of the second planetary gear set 2 The first rotating shaft CRJ; the two rotating shafts cms of the two transmission connecting groups can arbitrarily form the energy bearing 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 24, in the twentieth 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 two proportional values. The planetary gear set, the two transmission connection group corresponds to the first transmission connection group 3 and the first transmission connection group 4. The two planetary gear sets, the two sun gear rotary pumps psslA and psslB, and the two central gear rotating shafts pSS2A and pss2B are connected to the two transmission connection groups. The two planetary arm rotation axes paA and paB of the two planetary gear sets can arbitrarily form the energy wheel output end of the first planetary gear set 1 (the first rotation axis 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 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 Figures 2 and 25, in the second 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 value. The driven planetary gear set and a negative ratio driven planetary gear set correspond to the first transmission connection group 3 and the second transmission connection group 4. The two planetary gear sets have two _ wheel rotation axes pssl and (10), a central gear_shaft _, and a ring gear rotation axis nrs connected to the transmission connection. 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 (first rotating pumping) (3)]: The two rotating shafts ems 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 of the first transmission connection group 4. 20 132.9173 '• month and referring to Figures 2 and 26, in the twenty-second preferred embodiment of the present invention, the two comet gears are in contact with the first planetary wire set and the second planetary tooth 2, and The two types of negative ratio drive type 1 gear sets of the same type are combined with the first transmission connection group 3 and the second transmission connection group 4. The two planetary gear sets of the two sun gears, the rotating shafts nssA and nssB, the one-ring gear rotating shaft j^sA and the sinking must be connected to the two transmissions 、'. The two planetary arm rotation axes naA and naB of the Haiyi planetary gear set can arbitrarily form the energy output end of the first comet gear set 1 (the first wire 〇p) and the control end of the second planetary gear set 2 (the first) The 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 Figures 2 and 27, in the twenty-third preferred embodiment of the present invention, the two satellite gears are applied to the first planetary gear set and the second planetary gear set 2, and are 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 have two sun gears, the rotating shafts nssA and nssB, the two-ring gear rotating shaft j^sa and the sinking connection to the two transmission connections, and the j-planetary gear set ^-the planetary arm rotating axes naA and naB The energy output end of the first planetary gear set 1 (first rotating shaft 〇p) and the control end of the second planetary gear set 2 (the first rotating shaft CR) can be arbitrarily formed; the two rotating shafts of the two transmission connecting groups are cms The energy input terminal SD of the first transmission connection group 3 and the free transmission end SE of the second transmission connection group 4 can be arbitrarily formed. The foregoing preferred embodiments are merely illustrative of the invention and its technical features, and the techniques of the embodiments may be practiced in various equivalents and/or alternatives. The scope defined shall prevail. 21 132.9173 BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a diagram showing an independently controllable transmission mechanism of a preferred embodiment of the present invention. FIG. 2 is a view showing the interior of the independently controllable rotating mechanism of the present invention. FIG. 3C is a diagram showing the internal structure of the planetary gear set of the independently controllable transmission of the preferred embodiment of the present invention. Wood 4A to #: The internal structure of the drive connection group can be independently controlled by the drive mechanism of the preferred embodiment of the present invention. *

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音圖。【主要元件符號說明】 ^ 1 第一行星齒輪組 2 第二行星齒輪組Figures 5 to 27 are 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 第一傳動連接組 4 第二傳動連接組 0P 第一旋轉車由 AD 第二旋轉袖 AE 第三旋轉車由 CR 第一旋轉轴 BD 第二旋轉軸 BE 第三旋轉轴 SD 能量輪入端 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 ppi 第—行星齒輪 pp2 第二行星齒輪Pa 行星臂旋轉軸 ns 太％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 cmg1第一齒輪 cms旋轉軸 cmg2 第二齒輪 cmg3第三齒輪 223 First drive connection group 4 Second drive connection group 0P First rotary car by AD Second rotary sleeve AE Third rotary car by CR First rotary axis BD Second rotary axis BE Third rotary axis SD Energy wheel-in terminal SE Free transmission end psl sun gear pssl sun gear rotation axis ps2 central gear pss2 central gear rotation axis ppi first - planetary gear pp2 second planetary gear Pa planetary arm rotation axis ns too% gear nss sun gear rotation axis nr ring gear nrs ring gear rotation Axis np planetary gear na planetary arm rotating shaft cmg1 first gear cms rotating shaft cmg2 second gear cmg3 third gear 22

Claims

132.9173 申請專利範圍： 1、一種可獨立控制傳動機構，其包含：一第一行星齒輪組，其具有一能量輸出端；一第二行星齒輪組，其具有一控制端；一第一傳動連接組’其連接於該第一行星齒輪組及第二行星齒輪組，該第一傳動連接組具有一能量輸入端；及 -第二傳動連接組’其連接於該第__行星錄組及第二行星歯輪組，該第二傳動連接組具有一自由傳輸端；其中该控制端控制該自由傳輸端，以自由切換該自由傳輸端做為能量輸入端及能量輸出端之一。 2、依申請專利範圍第i項所述之可獨立控制傳動機構，其中該第一行星齒輪組及第二行星錄組為兩個正比值驅動式行星齒輪組。 3、依申請專利範圍第i項所述之可獨立控制傳動機構，其中該第一行星齒輪組為-正比值驅動式行星齒輪組，該第二行㈣輪組為一負比值再區動式行星齒輪組。 4、依申請專利範圍第丨項所述之可獨立控制傳動機構，其中該第—行星齒輪組為-負比值驅動式行星齒輪組，該第二行星齒輪組為— 正比值驅動式行星齒輪組。 5 '依申物娜1柄述之可獨立控_機構，綱星齒主輪組及第二行星錄組為兩個負比值驅動式行星齒輪組。、:^利範圍第5項所述之可獨立控制傳動機構，其中該第畜輪組。序目门型式的兩個負比值驅動式行星、依申物彳細5猶㈣^立__，射該第—行 23 6 1329173 星齒輪組及帛二行星絲㈣兩行星齒輪組。门i式的兩個負比值鵰動式 8、依申請專利範圍第卜2、3、，其中該第-行星歯輪組具有:第:所述之可獨立控制傳動機構第三旋轉軸；該第-行星齒輪組之第^轉輪、一第二旋轉無及-J機構之能量輪出端;該第—行星二為該：立技制傳第一傳動連接組；对-行結輪組: 接至該傳動連接組β 一疋轉轴連接至該第二 9、依申請專利範圍第】、2、3、4或5項所述之，其中该第二行星齒輪組具有-第-旋轉輪、〜_傳動機構第三旋轉軸；該第二行星齒輪組之第_旋轉輪^二旋轉車由及— 動機構之控制端；該第二行星齒輪組可獨立控制傳傳動連接組；該第二行星齒輪轉轴連接至該第— 連接組。 —讀㈣接轉第二傳動 10 一種可獨立控制傳動機構，其包含： -第-行星齒輪組，其具有—控制端； -第二行星齒輪組，其具有—能量輸出端；一第一傳動連接組’其連接於該第—行星齒輪級組，該第一傳動連接組具有一能量輸入端；及行星齒輪一第二義連触，麵接於該第—行星料組’該第二傳動連接組具有一自由傳輸端； $二行星齒輪其令該控制端控制該自由傳輸端，以自由切換能量輸入端及能量輪出端之一。由傳輪端做為 1卜依申請專利範圍第1G項所述之可獨立_傳攝，其中該第— 24 1329173 行星齒輪、、且及第一行星齒輪組為兩個正比值驅動式行星齒輪組。 12、依申請專利範圍第10項所述之可獨立控制傳動麟，其中該第一行星齒輪組為-正比值驅動式行錄輪組，該第二行星齒輪組為一負比值驅動式行星齒輪組。 13、依申請翻制第1G項所述之可獨立控制傳誠構，其中該第一行星齒輪組為-負比值驅動式行星齒輪組，該第二行星齒輪組為一正比值驅動式行星齒輪組。132.9173 Patent application scope: 1. An independently controllable transmission mechanism, comprising: a first planetary gear set having an energy output end; a second planetary gear set having a control end; a first transmission connection group 'connected to the first planetary gear set and the second planetary gear set, the first transmission connection group has an energy input end; and - the second transmission connection group 'connected to the first __ planet record group and the second The planetary transmission wheel set has a free transmission end; wherein the control end controls the free transmission end to freely switch the free transmission end as one of an energy input end and an energy output end. 2. The independently controllable transmission mechanism according to item i of the patent application scope, wherein the first planetary gear set and the second planetary record group are two proportional drive planetary gear sets. 3. The independently controllable transmission mechanism according to item i of the patent application scope, wherein the first planetary gear set is a proportional-driven planetary gear set, and the second (four) wheel set is a negative ratio re-zoned Planetary gear set. 4. The independently controllable transmission mechanism according to the scope of the patent application scope, wherein the first planetary gear set is a negative ratio driven planetary gear set, and the second planetary gear set is a proportional drive planetary gear set . 5 ' According to the Shen Shi Na 1 handle can be independently controlled _ mechanism, the main tooth main wheel set and the second planetary record group are two negative ratio driven planetary gear sets. ,: The independently controllable transmission mechanism described in item 5 of the profit range, wherein the first livestock wheel set. The two negative ratio driven planets of the order gate type, according to the application of the fine 5 (four) ^ __, shoot the first line 23 6 1329173 star gear set and 帛 second planet wire (four) two planetary gear set. The two negative ratio oscillating type of the door i type, according to the patent scopes 2, 3, wherein the first planetary wheel set has: the: the third rotation axis of the transmission mechanism can be independently controlled; The first wheel of the first-planetary gear set, the second wheel of the second rotation and the energy wheel of the -J mechanism; the first-planet two is: the first transmission connection group of the vertical technology transmission; the pair-line connection wheel set : connected to the transmission connection group β, a rotation shaft is connected to the second 9. According to the scope of the patent application, the second planetary gear set has a -th-rotary wheel a third rotating shaft of the transmission mechanism; a third rotating shaft of the second planetary gear set; and a control end of the rotating mechanism; the second planetary gear set can independently control the transmission connection group; A second planetary gear shaft is coupled to the first connection group. - reading (four) connecting the second transmission 10 an independently controllable transmission mechanism comprising: - a first planetary gear set having a - control end; - a second planetary gear set having - an energy output; a first transmission a connection group 'connected to the first planetary gear stage, the first transmission connection group has an energy input end; and a second sense of the planetary gear, connected to the first planetary carrier 'the second transmission The connection group has a free transmission end; the two planetary gears enable the control terminal to control the free transmission end to freely switch one of the energy input end and the energy wheel output end. The independent transmission_transmission is described by the transmission wheel end as a patent application scope 1G, wherein the first - 24 1329173 planetary gear, and the first planetary gear set are two proportional drive planetary gears group. 12. The independently controllable drive train according to claim 10, wherein the first planetary gear set is a proportional drive driven record wheel set, and the second planetary gear set is a negative ratio driven planetary gear group. 13. The independently controllable transmission mechanism described in Item 1G is applied, wherein the first planetary gear set is a negative ratio driven planetary gear set, and the second planetary gear set is a positive ratio driven planetary gear. group.

Η、依申請專利範圍第1Q項所述之可獨立控制傳動機構，其中該第一行星齒輪組及第二行星齒輪組為兩個負比值驅動式行星齒輪植。 15、依申請專利範圍第14項所述之可獨立控制傳動機構其中該第一 1=缺^議⑽兩餘_動式行 !6、依帽翻顧第M賴述之立㈣觸機構，巧 ^星齒輪缺以于纖_兩_峨負伽式行星齒輪組。胃可, independently controllable transmission mechanism according to claim 1Q of the patent application scope, wherein the first planetary gear set and the second planetary gear set are two negative ratio driven planetary gears. 15. According to the 14th item of the patent application scope, the independently controllable transmission mechanism, wherein the first 1 = lack of discussion (10) two more _ move type! 6, according to the cap of the M Lai said (four) touch mechanism, Qiao ^ star gear is missing in the fiber _ two _ 峨 negative gamma planetary gear set. stomach

17 '依申請專利範圍第1G、u、12、u 機構，其_—行纖組具有H轉制^ 及一第三旋轉軸；該第-行星齒輪組之第一旋轉輪為节制傳動機構之控制端；該第-行星齒輪組之第二旋_連= 第-傳動連接組；該第-行星齒輪組連接至该傳動連接組。第—旋料連接至該第二 18、依申請專利範圍第10、11、12、13或14項所述之可猫機構，其中該第二行星齒敎控制傳動及-一該第二行星齒輪㈣二::::: 25 1329173 制傳動機構之能量輸its端；該第二行星錄組之第二旋轉勒連接至§亥第-傳動連接組；該第二行星齒輪組之第三_軸連接至該第二傳動連接組。 19、一種可獨立控制傳動機構，其包含：二行星齒輪組’該二行星齒輪組之其中—組具有―能量輸出端，該二行星齒輪組之另一組具有一控制端；及二傳動連接組’每個該二傳動連接組連接於該二行星齒輪组之間17 ' According to the patent application scope 1G, u, 12, u mechanism, the _-line fiber group has H conversion system and a third rotation axis; the first rotation wheel of the first planetary gear set is controlled by the control transmission mechanism a second rotation of the first planetary gear set = a first transmission connection group; the first planetary gear set is coupled to the transmission connection group. The second spinning device is connected to the cat body according to claim 10, wherein the second planetary gear control transmission and the second planetary gear (d) two::::: 25 1329173 The transmission of the energy of the transmission mechanism is the same end; the second rotation of the second planetary record group is connected to the §Hai-transmission connection group; the third _axis of the second planetary gear set Connected to the second transmission connection set. 19. An independently controllable transmission mechanism comprising: two planetary gear sets 'where the two planetary gear sets have an energy output, the other of the two planetary gear sets has a control end; and two transmission connections Group 'each of the two transmission connection groups is connected between the two planetary gear sets

，該二傳動連接組之其中—組具有—能量輸人端該二傳動連接組之另一組具有一自由傳輸端；其中該控制端控制該自由傳輸端，以自由切換該自由傳輸端做為能量輸入端及能量輸出端之一。機構，其中該二行 2〇、依申請專利範圍第19項所述之可獨立控制傳動星齒輪組為兩個正比值驅動式行星齒輪組。 2卜依中請專利制第19項所述之可獨立控娜動機構，料該二行The other of the two transmission connection groups has an energy input terminal, and the other of the two transmission connection groups has a free transmission end; wherein the control terminal controls the free transmission end to freely switch the free transmission end as One of the energy input and the energy output. The mechanism, wherein the two rows, the independently controllable transmission gear set according to claim 19 of the patent application scope, are two proportional drive planetary gear sets. 2 Bu Yizhong invites the independently controllable movement mechanism mentioned in Item 19 of the patent system.

星齒輪組之其中-組為—正比值驅動式行星齒輪組，該二行星: 輪組之另一組為一負比值驅動式行星齒輪組。 W 22、依申請專利範圍第19項所述之可獨立控制傳動機構，射該4 星齒輪組為兩個負比值驅動式行星齒輪組。、依❻專利範圍第22項所述之可獨立控制傳動機構，其中兮二〜星齒輪組為相同型式的兩個負比值驅動式行星齒幹組 V—仃 24、依中請專利顧第22項所述之可獨立控制傳動機星齒輪组為兩種不同型式的兩個負比值驅動式去、〜仃 25、依中請專利範圍第19、2G、21或2 ^輪組。峒W遮之可獨立控 ’其中該二行星齒輪組之一組具有—第—旋轉軸一機構弟一旋轉轴 26 1329173 及第二方疋轉轴；該第—旋轉軸為該可獨立控制傳動機構之能量輸出端；該第二旋轉从第三旋轉軸分別連接至該二傳動達接組 26、依申請專利範圍第19 n行22項所述之可獨立控制傳動機構及-第三旋轉軸tr第一旋轉軸第二·軸，錢~_減該可社控娜域構之控制 27 知，邊第二轉轴及第三旋轉軸分別連接至該依申請專纖®第20或2 — _連接、，且。弋U項所述之呼獨立控制傳動機構，立中贫正3=式行星齒輪組包含—太陽齒輪、—太陽齒輪旋二 =央齒輪、—中央齒輪旋轉軸、一第—行星齒輪齒輪及一行星臂旋轉輛丁生該太陽齒輪及中央錢/帛輪及第二行星齒輪舊合 21❹娜物敏謂域構，其中該組包含，齒輪、-太陽齒輪旋轉軸、。、—輪_轴、至少-行星齒輪及-行星臂旋轉轴 29、依巾料纖圍第28項齒輪旋轉轴及行星臂旋轉轴為立^傳動麟，其中該太陽且其轉速比值為負。輪旋轉轴之旋轉方向為相反方向， 3〇、依申請專利範圍第28項所述輪旋轉軸及行星做轉軸為、敎控制傳動麟，其巾該環齒 ’該太陽齒輪旋轉軸及環齒輪=當該行星臂旋轉轴固定不動時其轉速比值為負。鳴車由之旋轉方向為相反方向，且 27One of the star gear sets is a proportional drive planetary gear set, and the other two sets of wheels are a negative ratio driven planetary gear set. W 22. The independently controllable transmission mechanism according to claim 19 of the patent application scope, the four-star gear set is two negative ratio driven planetary gear sets. According to the 22nd patent scope, the independently controllable transmission mechanism, wherein the second to the star gear set are the same type of two negative ratio driven planetary gear sets V-仃24, according to the patent Gu 22 The independently controllable transmission star gear set can be two different types of two negative ratio drive type, ~ 仃 25, according to the scope of the patent range 19, 2G, 21 or 2 ^ wheel set.峒W can be independently controlled, wherein one of the two planetary gear sets has a first rotating shaft, a rotating shaft 26 1329173 and a second rotating shaft; the first rotating shaft is the independently controllable transmission An energy output end of the mechanism; the second rotation is respectively connected from the third rotating shaft to the two transmission connecting group 26, the independently controllable transmission mechanism and the third rotating shaft according to the 19th line and the 22nd line of the patent application scope Tr first rotation axis second axis, money ~ _ minus the control of the social control Na domain structure 27 know, the second rotation axis and the third rotation axis are respectively connected to the application fiber® 20 or 2 — _Connect, and.呼U said the independent control transmission mechanism, the center-poor 3= planetary gear set includes - the sun gear, the sun gear rotation two = the central gear, the central gear rotating shaft, a first - planetary gear and one The planetary arm rotates the Dingsheng sun gear and the central money/clip wheel and the second planetary gear. The 21-inna-sensitive material domain structure, wherein the group contains the gear, the sun gear rotating shaft, and the sun gear. , - wheel _ axis, at least - planetary gear and - planetary arm rotation axis 29, according to the towel material circumference 28th gear rotation axis and the planetary arm rotation axis is the vertical drive transmission, where the sun and its speed ratio is negative. The rotation direction of the rotating shaft of the wheel is the opposite direction, 3〇, according to the scope of the patent application, the rotating shaft of the wheel and the rotating shaft of the planet are the 传动 control transmission lining, the towel of the ring tooth 'the sun gear rotating shaft and the ring gear = When the planetary arm rotation axis is fixed, its speed ratio is negative. The sounding direction of the car is reversed, and 27