201102539 六、發明說明： 【發明所屬之技術領域】 本發明係有關一種變速器控制裝置，尤指一種無段 變速器之控制裝置。 【先前技術】 按’引擎動力的輸出必須透過精確的變速系統始能達成 有效率的傳動。目前市面上可見各式各樣的變速控制裝 置’然而使變速裝置在有效率的動力傳輸前提之下，如何 • 提供無段變速且將損耗動能降至最低，係各家設計之共同 指標。 傳統之變速裝置係透過不同轉速比之齒輪間嚙合的變 化，以達到轉速改變，然而並無法達到無段變速，且構件 的配合以及操作原理相當的複雜。 目前市面上可見的無段變速包括透過油壓變速、 CVT(Continuously Variable Transmission)無段變速系統 之可變皮帶盤半徑的輸入與輸出、以及電氣變頻馬達等 籲等。然而’透過油壓傳動具有動能損耗大及速度慢的限制， 而CVT的皮帶盤傳動時之摩擦力障礙的克服難以消除，且 電氣馬達有能源攜帶的困難。 以懸浮式之契合式齒輪組亦能產生無段變速之功能，例 如以行星系齒輪組或者差速器齒輪組等等。惟，目前立無 法對懸浮式之契合式齒輪組之傳動有效率的控制，雖配合 前述油壓傳動、皮帶盤傳動、或者電氣馬達傳動仍可產生 無段變速的功能’但仍會造成上述此幾種傳動方式之問 201102539 題，因此如何解決此一問題即為本發明之重點所在。 【發明内容】 本發明之主要目的，在於解決上述的問題而提供一種 無段變速器控制裝置，使裝置之傳動構件簡化且堅固，並 使其減速比之範圍更為寬廣。 為達前述之目的，本發明係包括： 一加速齒輪組，其於後端連結至少一傳送變速動力且 輸出之減速齒輪組，此加速齒輪組包括一前環齒輪與一前 太陽輪，前環齒輪具有一環徑大於該前太陽輪之内環齒， 且前太陽輪於該内環齒之相對位置設有外環齒，前環齒輪 與前太陽輪分別伸設於内外獨立轉動之傳動軸至減速齒輪 組，各傳動軸上分別設有一於變速箱内支撐之單向軸承， 且單向軸承分別於各傳動軸上限制該前環齒輪與前太陽輪 僅朝同一方向單向轉動。 至少一行星齒輪，此行星齒輪於相對之兩端分別嚙合 於該内環齒以及該外環齒，此行星齒輪於加速齒輪組外具 有一外套環，此外套環中樞設一與行星齒輪同軸樞轉之内 套環，且内套環之環徑大於該行星齒輪之直徑。 一由外部之動力源提供動力轉動之驅動單元，此驅動 單元並且驅動該行星齒輪而帶動前環齒輪與前太陽輪轉 動，其係樞接於該内套環，且樞接點相對位於該行星齒輪 之直徑範圍外之偏心位置。 該驅動單元以該樞接點帶動内套環於行星齒輪嚙合前 環齒輪及前太陽輪之兩端間弧擺，且樞接點位移之半徑大 201102539 於該行星齒輪半徑，透過樞接點相對於行星齒輪軸心為中 心的距離增減，使行星齒輪驅動前環齒輪與前太陽輪轉動 時，分別對環齒輪與太陽輪間產生向量變化而改變施力力 矩，使環齒輪或太陽輪於單向轉動之限制下產生加速之速 差。 本發明之上述及其他目的與優點，不難從下述所選用 實施例之詳細說明與附圖中，獲得深入了解。 當然，本發明在某些另件上，或另件之安排上容許有 所不同，但所選用之實施例，則於本說明書中，予以詳細 說明，並於附圖中展示其構造。 【實施方式】 請參閱第1圖至第3圖，圖中所示者為本發明所選用 之實施例結構，此僅供說明之用，在專利申請上並不受此 種結構之限制。 本實施例提供一種無段變速器控制裝置，其於本實施 例中係應用於汽車之無段變速系統，且裝設於變速箱内， 包括： 一加速齒輪組1，其於後端連結至少一減速齒輪組 2，藉由加速齒輪組1搭配減速齒輪組2而傳送變速動力 且輸出。此加速齒輪組1包括一前環齒輪1 1與一前太陽 輪1 2，前環齒輪1 1具有一内環齒1 1 1，其環徑大於 該前太陽輪1 2，且前太陽輪1 2於前環齒輪1 1之内環 齒1 1 1之相對位置設有外環齒1 2 1，前環齒輪1 1與 前太陽輪1 2分別伸設於内外獨立轉動之傳動軸3、4至 201102539 減速齒輪組2 ’該傳動軸3係結合於前環齒輪1 1，而傳 動軸4則結合於該前太陽輪丄2，而如圖中所示該傳動軸 3係中空且供該傳動軸4由其中穿設，各傳動軸34上 分別設有一單向軸承31、41以於變速箱内支撐（於圖 中未示），且單向軸承3 1、41分別於各傳動軸3、4上 限制該前環齒輪1 1與前太陽輪i 2僅朝同一方向單向轉 動。 至少一行星齒輪5，此行星齒輪5於相對之兩端分別 嚙合於該内環齒1 1 1以及該外環齒丄2 i，此行星齒輪 5於加速齒輪組1外具有一之外套環5 i，此外套環5工 中樞設一與行星齒輪同軸樞轉之内套環5 2，且内套環5 2之環徑大於該行星齒輪5之直徑。 於本實施例中，該前環齒輪1 1中設有一前支架1 3，此剛支架1 3相對於各該行星齒輪5分別伸設一軸桿 1 3 1，行星齒輪5則樞接於對應之轴桿1 3 1上而定 位。於此係於行星齒輪5内設有軸承（於圖中未示）並套 設於該軸桿131。 一由外部之動力源提供動力轉動之驅動單元6，此驅 動單元6並驅動該行星齒輪5而帶動前環齒輪1i與前太 陽輪1 2轉動，其係與該内套環5 2樞設於一樞接點a 上，此樞接點A相對位於該行星齒輪5直徑外之内套環5 2偏心位置。 本實施例之驅動單元6，其係具有一主軸6 i，此主 轴6 1係由外部之動力源連接且提供動力轉動，於本實施 201102539 例中係連減車引擎线，主轴6丨與汽車引料統之間 可透過離合器（於圖中未示）的設置而控制動力傳送與否 0 主軸6 1上具有朝徑向伸設之支臂6 2，此支臂6 2 係對應該至少一行星齒輪而設，於支臂6 2樞設一擺臂6 3，且以擺臂6 3連動該樞接點弧擺，此擺臂6 3以末端 槐接於該内套環之偏心位置。 如圖中所示，本實施例之前環齒輪1 i與該前太陽輪 1 2之間分別於兩相對側設有一行星齒輪5，而主軸^工 對應各該行星齒輪5伸設一支臂6 2，且本實施例之内套 環5 2與該外套環5 1間設有滚針而可相對樞轉，於内套 %<中具有一内徑大於該行星齒輪5直徑之環凹槽5 2 1， 於此環凹槽5 2 1内具有一與該擺臂6 3末端樞接之定位 部5 2 2，此定位部即設置於該行星齒輪5直徑外之内套 環5 2偏心位置，且擺臂6 3末端朝環凹槽5 2 i中伸設 一樞軸6 3 1，並樞接於該内套環5 2之定位部5 2 2。 主軸6 1上並設有一主傘齒輪6 4，此主傘齒輪6 4 係與該主軸同軸轉動，主傘齒輪6 4連結於一變速馬達6 5，此變速馬達驅動主傘齒輪6 4於主轴轉動時相對 與反轉。 主傘齒輪6 4嚙合至少一副傘齒輪6 6 i，此副傘齒 輪6 6 1係與主傘齒輪6 4相對呈垂直方向轉動，副伞# 輪6 6 1並驅動一滑塊6 6 2相對於主軸6 1呈經向滑移 ，此滑塊6 6 2係與該擺臂6 3於末端樞接内套環5 2之 201102539 另一側結合。 本實施例之副傘齒輪6 6 1與滑塊6 6 2分別設於一 框架6 6中，此框架6 6樞設於該主軸6 1，且連結於擺 臂6 3而隨主軸6 1轉動，該副傘齒輪6 6丄於框架6 6 中連結一螺桿6 6 3，此螺桿6 β 3係相對於主軸6 1之 徑向伸設，且該滑塊6 6 2係螺設於此螺桿6 6 3上，藉 由變速馬達6 5控制主傘齒輪6 4於主軸6 1轉動時正轉 與反轉’以驅動副傘齒輪6 61而帶動螺桿6 6 3轉動， 滑塊6 6 2則隨螺桿6 6 3而向外侧或内側滑移。本實施 例之驅動馬達6 5透過一外部設備輸入控制訊號，且控制 主傘齒輪6 4與主軸6 1間之相對轉速，其於主軸6 1上 設有一電磁離合器6 5 1，於主傘齒輪6 4相對於轉動中 之主軸正轉與反轉時，以此電磁離合器6 5 1控制主傘齒 輪6 4與主軸6 1分離。 本實施例之減速齒輪組2，其係於該前環齒輪1 1之 傳動軸3端部連接固定同軸之後太陽輪21，於前太陽輪 1 2之傳動軸4末端連接固定同軸之後環齒輪2 2，其中 該後太陽輪2 1具有一外環齒2 1 1，而後環齒輪2 2具 有一大於該後太陽輪2 1之外環齒2 1 1直徑之内環齒2 2 1，該前環齒輪1 1與後太陽輪2 1相連之傳動軸3上 拖設一輸出變速動力之輸出齒輪7，此輸出輪7於側向接 合一後支架7 1，並於此後支架7 1設有至少一行星齒輪 7 2嚙合於後環齒輪2 2之内環齒2 2 1與後太陽輪2 1 之外環齒2 1 1間，於本實施例中係於後支架7 1側上設 201102539 有三行星齒輪7 2，藉此使後環齒輪2 2與後太陽輪2 1 轉動時透過行星齒輪7 2帶動輸出輪7輸出變速動力。 本實施例之單向轴承31係設於結合該前環齒輪11 之傳動軸3，且鄰近於前環齒輪1 1。另一單向軸承4 1 則設於該前太陽輪1 2結合之傳動轴4穿出後環齒輪2 2 之端部，並靠抵於該後環齒輪2 2。 本實施例之變速控制裝置作動時，係由汽車之引擎系 統（於圖中未示）傳送動力至該主軸6 1，當主軸6 1接 • 受動力而轉動時，透過支臂6 2將傳動力量透過擺臂6 3 而施力於内套環5 2，並經由外套環5 1牽引行星齒輪5 而帶動前環齒輪11與前太陽輪12轉動。 以槓桿原理而言，該行星齒輪5之軸心為支點B，而 行星齒輪5與該前環齒輪11及該前太陽輪12相對嚙合 之齒部則為相對於支點施力之兩端點，為便於說明，於此 將靠近行星齒輪5與前環齒輪11嚙合方向之其一端點定 義為外施力點C，而靠近行星齒輪5與前太陽輪1 2嚙合 ® 方向之另一端點定義為内施力點D。 如第4圖所示，當驅動馬達6 5之電磁離合器6 5 1 結合於主轴6 1上時，主傘齒輪6 4則隨主轴6 1旋轉， 故此時之主傘齒輪6 4與主軸6 1係同速轉動，此時二副 傘齒輪6 6 1與主傘齒輪6 4間係於主軸轉動中停留於靜 止嚙合的狀態，故框架6 6中之滑塊6 6 2即停留於螺桿 6 6 3之中間位置，而使擺臂6 3與内套環5 2之樞接點 A則位於支點B相同之施力位置。 201102539 如第5圖所示，當框架66中之滑塊6 6 2將該樞接 ，點A移至該内套環5 2於前環齒輪1 1與前太陽輪1 2間 之中間位置時，此時主軸6 1傳動之力量則相對施力於該 行星歯輪5之軸心（即圖示中之支點b )，使行星齒輪兩端 之齒部平均施力於該前環齒輪1 1及該前太陽輪1 2，使 該前環齒輪11及該前太陽輪12承受主軸61各1/2 的施力’如果不計算太陽輪1 2和環齒輪1 1的阻力，這 時整個系統以1:1之轉速比同速轉動。 如第6圖所示，當驅動馬達6 5驅動該主傘齒輪6 4 相對於轉動之主軸正轉，此時主傘齒輪6 4之轉速相對高 於主軸6 1 ’二副傘齒輪6 6 1隨主伞齒輪6 4之轉速而 開始旋轉’使框架6 6中之滑塊6 6 2朝外側移動，使擺 臂6 3與内套環5 2之樞接點A朝前環齒輪1 1方向擺動 〇 如第7圖所示，由於框架6 6中之滑塊6 Θ 2將該樞 接點A移至該外施力點c，故主軸6 i傳動之力量則完全 施力於該行星齒輪5嚙合於前環齒輪1 i之齒部，而該行 星齒輪5嚙合於前太陽輪12之齒部此時之施力消失，行 星齒輪5由於力量完全朝前環齒輪丄i方向施加，且前太 陽輪1 2因裝設單向軸承4 1而無法逆轉，故此時行星齒 輪5則隨前太陽輪1 2之外環齒丄2丄軌跡導引而順時鐘 自轉，而使該前環齒輪1 1達到小加速的效果。 如第8圖所示，當驅動馬達6 5驅動該主傘齒輪6 4 相對於轉動之主軸6 1反轉，此時主傘齒輪6 4之轉速相 201102539 對低於主軸6 1，二副傘齒輪6 6 1隨主傘齒輪6 4之轉 速而開始旋轉，使框架6 6中之滑塊6 6 2朝内側移動， 使擺臂6 3與内套環5 2之樞接點A朝前太陽輪1 2方向 擺動。 如第9圖所示，由於框架6 6中之滑塊6 6 2將該樞 接點A移至該内施力點d，故主軸6 1傳動之力量則完全 施力於該行星齒輪5嚙合於前太陽輪1 2之齒部，而該行 星齒輪5嚙合於前環齒輪1 1之齒部此時之施力消失，行 星齒輪5由於力量完全朝前太陽輪1 2方向施加，且前環 齒輪1 1因裝設單向軸承3 1而無法逆轉，故此時行星齒 輪5則隨前環齒輪1 1之内環齒1 1 1軌跡導引而逆時鐘 自轉，而使該前太陽輪達到大加速的效果。 如第10圖所示，當框架66中之滑塊6 6 2將該樞 接點A移由該支點B向外施力點C逐漸移動時，行星齒輪 5之齒部驅動前環齒輪11之力量由於相量的分散而相對 於驅動前太陽輪1 2之力量遞增，而當樞接點A移由外施 力點C向該支點B逐漸移動時則相對遞減。反之，如第工 1圖所示，當該支點B向内施力點D逐漸移動時，行星齒 輪5之齒部驅動前太陽輪12之力量相對於驅動前環齒輪 11之力量遞增’當樞接點A移由内施力點D向該支點b 逐漸移動時則相對遞減。 值得一提的是，實務上因前環齒輪1 1與前太陽輪丄 2在環境因素的影響下，重力的負荷會隨之改變，故行星 齒輪與前環齒輪及前太陽輪間之傳動會產生誤差，為減少 11 201102539 此環境因素所造成之誤差，故如上所述該驅動馬達6 5透 過外部設備輸入控制訊號，且該主傘齒輪6 4與主軸6 1 間之相對轉速，經計算後對應調整滑塊6 6 2之實際位 移。如第1 2圖所示，本實施例之外部設備係一中央處理 單元6 7，其接收汽車變速時所需之狀態訊號，此狀態訊 號經運算處理後輸出至一輸出控制單元6 8，以控制該變 速馬達6 5作動，而樞接點A於外施力點C及内施力點D 之間可由外部設備的控制而依變速需求任意改變位置，以 達到無段變速的須求。上述之狀態訊號於本實施例中包括 引擎轉速訊號、變速桿位置訊號、油門踏板訊號、變速箱 輸入軸轉速訊號、變速箱輸出軸轉速訊號、時速訊號、以 及力矩變化裝置施力點位置訊號。而該輸出控制單元6 8 包括變速馬達6 5電磁離合器6 5 1開關、變速馬達6 5 之正負轉及開關、以及駕駛艙儀表板之警示燈號。 因此，透過驅動單元6以該樞接點A帶動内套環5 2 於行星齒輪5嚙合前環齒輪11及前太陽輪12之兩端間 弧擺，且樞接點A位移之半徑大於該行星齒輪5半徑，透 過樞接點A相對於行星齒輪5軸心為中心的距離增減，使 行星齒輪5驅動前環齒輪1 1與前太陽輪1 2轉動時，分 別對前環齒輪1 1與前太陽輪1 2間產生向量變化而改變 施力力矩，使前環齒輪1 1或前太陽輪1 2於單向轉動之 限制下產生加速之速差。換言之，驅動單元6透過擺臂6 3於偏心位置驅動内套環5 2 2，而帶動該枢接點A於外 施力點C與内施力點D之範圍内移動，樞接點A向外施力 12 201102539 點C移動而使行星齒輪5產生順時鐘自轉，樞接點A向内 施力點D移動而使行星齒輪5產生逆時鐘自轉，行星齒輪 5透過驅動時之轉向改變，使前環齒輪1 1與前太陽輪1 2之間的轉速產生差異。 由上述之說明不難發現本發明之優點：在於： 1、 本發明利用力矩變化的無段變速器，其構造簡單 堅固、容易操作、體積更小、重量更輕，完全機械式的動 力傳導並齒輪完全契合、變速時無需離合器的暫時切斷、 籲 並且單軸向的動力輸入與輸出。 2、 多項的優點及變速齒輪比寬廣，使其適合使用在 腳踏車、兩輪機動車、汽車、超大型重車等各種需要變速 的機具。 3、 本發明所有的系統皆在一個封閉的動力迴路，因 物質不滅定律，沒有動能損失的疑慮。 4、 本發明之加速齒輪組1與減速齒輪組2的組合， 可任意由一組或多組的組合，齒輪組中任意兩軸輸入一軸 ® 輸出或任意一軸輸入兩轴輸出，視所需要的齒輪比或動力 混合可做出多種的結合變化。 5、 本發明變速的方式，為達到利用價值衍生的自動 控制和精密控制需要，除了機械式亦可增加數位計算之電 子控制、電氣馬達控制或油壓控制，利用該中央處理單元 監控變速控制裝置，並藉此達到引擎系統的管理，亦可加 入混合式動力，可由傳動轴3、4中的任何一軸輸入或輸 出。 13 201102539 以上所述實施例之揭示係用以說明本發明’並非用以吧制本 發明。本發明之精隨係利用槓桿原理之力矩變化達 速’故舉凡數值之蚊轉效元件之置換麵_本發明之 由以上詳細說明，可使熟知 確可達成前述目的，實已符合專 :明瞭本發明的 申請。 卜之規定，爰提出專利 【圖式簡單說明】 第1圖係本發明之立體夕卜觀示意圖 第2圖係本發明之立體分解示意圖 第3圖係本發明之剖示結構示意圖 第4圖係本發明之主伞齒輪相對於 滑塊位置Μ目 纽轉動時之 第5圖係本發明之行星齒輪於支點Β 第6圖係本發明之主傘齒輪相對於不思圖 動時之滑塊外移示意S1 _加速轉 第7圖係本發明之行星齒輪於外施为 之驅動示意圖 .點C順時鐘自轉 第8圖係本發明之主傘齒輪相對於主 動時之滑塊内移示意圖 主轴反轉而減速轉 第9圖係本發明之行星齒輪於内施力點 之驅動示意圖 第10圖係本發明之行星齒輪於外施力 間順時鐘自轉之驅動示意圖 201102539 第1 1圖係本發明之行星齒輪於外施力點D與支點B 間逆時鐘自轉之驅動示意圖 第1 2圖係本發明之外部設備控制變速馬達之示意圖 【主要元件符號說明】 (習用部分） 無201102539 VI. Description of the Invention: [Technical Field] The present invention relates to a transmission control device, and more particularly to a control device for a stepless transmission. [Prior Art] The output of the engine power must be transmitted through a precise shifting system to achieve an efficient transmission. A wide variety of shift control devices are currently available on the market. However, how to provide a stepless shift and minimize kinetic energy loss under the premise of efficient power transmission is a common indicator of each design. The conventional shifting device transmits the change of the meshing between the gears of different speed ratios to achieve the speed change, but the stepless shifting cannot be achieved, and the fitting and operating principle of the components are quite complicated. The stepless shifts currently available on the market include the input and output of variable belt pulley radius through hydraulic shifting, CVT (Continuously Variable Transmission), and electric variable frequency motors. However, through the hydraulic transmission, there is a limitation of large kinetic energy loss and slow speed, and the frictional obstacle of the CVT's belt pulley transmission is difficult to eliminate, and the electric motor has difficulty in carrying energy. The suspension-type gear set can also produce a stepless shifting function, such as a planetary gear set or a differential gear set. However, at present, it is impossible to control the transmission of the suspension-type gear unit in a suspension manner. Although the above-mentioned hydraulic transmission, belt pulley transmission, or electric motor transmission can still produce the function of stepless speed change, it still causes the above. There are several transmission methods for 201102539, so how to solve this problem is the focus of the invention. SUMMARY OF THE INVENTION A primary object of the present invention is to solve the above problems and to provide a stepless transmission control device which makes the transmission member of the device simple and robust, and which has a wider range of reduction ratios. For the foregoing purposes, the present invention comprises: an acceleration gear set coupled to at least one reduction gear train that transmits variable speed power and outputs at the rear end, the acceleration gear set including a front ring gear and a front sun gear, front ring The gear has a ring diameter larger than the inner ring gear of the front sun gear, and the front sun gear is provided with outer ring teeth at a relative position of the inner ring gear, and the front ring gear and the front sun gear respectively extend from the inner and outer independent rotating transmission shafts to the reduction gear Each of the transmission shafts is provided with a one-way bearing supported in the transmission, and the one-way bearing respectively limits the front ring gear and the front sun gear to rotate in one direction only in the same direction on each transmission shaft. At least one planetary gear, the planetary gear meshes with the inner ring tooth and the outer ring tooth respectively at opposite ends, the planetary gear has an outer ring outside the acceleration gear set, and the outer ring of the outer ring is coaxial with the planetary gear The inner ring is turned, and the inner ring has a larger diameter than the diameter of the planetary gear. a driving unit that is powered by an external power source, and the driving unit drives the planetary gear to drive the front ring gear to rotate with the front sun gear, and is pivotally connected to the inner ring, and the pivot point is opposite to the planet The eccentric position outside the diameter of the gear. The driving unit drives the inner collar to engage the inner ring of the planetary gear to engage the arc between the front ring gear and the front sun gear, and the radius of the pivot point displacement is 201102539 at the radius of the planetary gear, and the pivot point is relatively The distance between the center of the planetary gear shaft center increases or decreases, so that when the planetary gear drives the front ring gear and the front sun gear, a vector change occurs between the ring gear and the sun gear to change the applied torque, so that the ring gear or the sun gear The speed difference of acceleration is generated under the limitation of one-way rotation. The above and other objects and advantages of the present invention will be readily understood from Of course, the invention may be varied on certain components, or in the arrangement of the components, but the selected embodiments are described in detail in the specification and their construction is shown in the drawings. [Embodiment] Please refer to Fig. 1 to Fig. 3, which shows the structure of the embodiment selected for the present invention, which is for illustrative purposes only and is not limited by this structure in the patent application. The embodiment provides a stepless transmission control device, which is applied to the stepless transmission system of the automobile in the embodiment, and is installed in the transmission, and includes: an acceleration gear set 1 coupled to at least one end of the rear end The reduction gear set 2 transmits the shifting power by the acceleration gear set 1 in conjunction with the reduction gear set 2 and outputs it. The acceleration gear set 1 includes a front ring gear 1 1 and a front sun gear 1 2 . The front ring gear 11 has an inner ring gear 1 1 1 , the ring diameter is larger than the front sun gear 12, and the front sun gear 1 2 The outer ring gear 1 1 is disposed at a position opposite to the inner ring gear 1 1 1 of the front ring gear 1 1 , and the front ring gear 1 1 and the front sun gear 1 2 are respectively extended on the inner and outer independent rotating drive shafts 3 and 4 To 201102539 reduction gear set 2 'the transmission shaft 3 is coupled to the front ring gear 1 1 and the transmission shaft 4 is coupled to the front sun rim 2, and as shown in the figure, the transmission shaft 3 is hollow and is provided for the transmission The shaft 4 is disposed therein, and each of the transmission shafts 34 is respectively provided with a one-way bearing 31, 41 for supporting in the transmission (not shown), and the one-way bearings 31, 41 are respectively disposed on the respective transmission shafts 3, 4 limits the front ring gear 11 and the front sun gear i 2 to rotate in one direction only in the same direction. At least one planetary gear 5 meshing with the inner ring gear 1 1 1 and the outer ring gear 2 i at opposite ends, the planetary gear 5 having an outer collar 5 outside the acceleration gear set 1 i. The outer ring of the outer ring of the outer ring is provided with an inner ring 52 that is coaxially pivoted with the planetary gear, and the inner ring ring 52 has a larger diameter than the diameter of the planetary gear 5. In the present embodiment, the front ring gear 1 1 is provided with a front bracket 13 , and the rigid bracket 13 defines a shaft 1 3 with respect to each of the planetary gears 5 , and the planetary gear 5 is pivotally connected to the corresponding one. The shaft 1 3 1 is positioned above. Here, a bearing (not shown) is disposed in the planetary gear 5 and is sleeved on the shaft 131. a driving unit 6 that is powered by an external power source, and the driving unit 6 drives the planetary gear 5 to drive the front ring gear 1i and the front sun gear 12 to rotate, and the inner ring 52 is pivoted to the inner ring 52 At a pivot point a, the pivot point A is eccentrically located relative to the inner collar 5 2 outside the diameter of the planet gear 5. The driving unit 6 of the embodiment has a main shaft 6 i which is connected by an external power source and provides power rotation. In the embodiment 201102539, the engine line is reduced, the main shaft 6丨 and the vehicle lead material are used. The power transmission can be controlled by the setting of the clutch (not shown). The main shaft 6 1 has an arm 6 6 extending radially, and the arm 6 2 corresponds to at least one planetary gear. For example, a swing arm 6 3 is pivoted on the arm 6 2 , and the pivot joint swing is connected by the swing arm 63 3 , and the swing arm 6 3 is end-connected to the eccentric position of the inner collar. As shown in the figure, a planetary gear 5 is disposed on the opposite sides of the front ring gear 1 i and the front sun gear 12 respectively, and the main shaft corresponds to each of the planetary gears 5 to extend an arm 6 . 2, and the inner collar 5 2 of the embodiment is provided with a needle roller between the outer sleeve ring 5 1 and can be relatively pivoted, and has a ring groove having an inner diameter larger than the diameter of the planetary gear 5 in the inner sleeve % < 5 2 1 , a positioning portion 52 2 pivotally connected to the end of the swing arm 6 3 is disposed in the groove 5 2 1 , and the positioning portion is disposed at an eccentric position of the inner collar 5 2 outside the diameter of the planetary gear 5 . A pivot 633 is extending from the end of the swing arm 63 to the ring recess 5 2 i and pivoted to the positioning portion 52 2 of the inner collar 5 2 . The main shaft 6 1 is provided with a main bevel gear 64. The main bevel gear 64 is coaxially rotated with the main shaft. The main bevel gear 64 is coupled to a variable speed motor 65. The variable speed motor drives the main bevel gear 64 to the main shaft. Relative and reverse when turning. The main bevel gear 6 4 engages at least one pair of bevel gears 6 6 i. The pair of bevel gears 6 6 1 rotates in a direction perpendicular to the main bevel gears 6 4 , and the auxiliary umbrellas # 6 6 1 drives a slider 6 6 2 The slider 6 6 2 is slid in the warp direction relative to the main shaft 61, and the slider 6 6 is coupled to the other side of the pivoting arm 63 at the end of the end of the inner collar 5 2 of the 102102539. The sub-bevel gear 6 6 1 and the slider 6 6 2 of the embodiment are respectively disposed in a frame 66. The frame 6 6 is pivotally mounted on the main shaft 61 and is coupled to the swing arm 63 to rotate with the main shaft 61. The auxiliary bevel gear 6 6 is coupled to a screw 6 6 3 in the frame 66. The screw 6 β 3 is radially extended with respect to the main shaft 61, and the slider 6 6 2 is screwed to the screw. 6 6 3, the main bevel gear 6 4 is controlled by the variable speed motor 6 5 to rotate forward and reverse when the main shaft 6 1 rotates to drive the auxiliary bevel gear 6 61 to drive the screw 6 6 3 to rotate, and the slider 6 6 2 Sliding outward or inside with screw 636. The driving motor 65 of the embodiment inputs the control signal through an external device, and controls the relative rotational speed between the main bevel gear 64 and the main shaft 61. The main shaft 61 is provided with an electromagnetic clutch 6 5 1 on the main bevel gear. When the main shaft is rotated and reversed with respect to the rotating shaft, the electromagnetic clutch 615 controls the main bevel gear 64 to be separated from the main shaft 6 1 . The reduction gear set 2 of the present embodiment is connected to the end of the transmission shaft 3 of the front ring gear 1 and is fixed to the coaxial sun wheel 21, and is connected to the end of the transmission shaft 4 of the front sun gear 12 to fix the coaxial rear ring gear 2 2, wherein the rear sun gear 2 1 has an outer ring gear 2 1 1 , and the rear ring gear 22 has an inner ring tooth 2 2 1 which is larger than the outer ring gear 2 1 outside the ring tooth 2 1 1 An output gear 7 for outputting variable speed power is dragged onto the transmission shaft 3 of the ring gear 1 1 and the rear sun gear 2 1 . The output wheel 7 is laterally engaged with a rear bracket 7 1 and thereafter the bracket 7 1 is provided with at least A planetary gear 7 2 is engaged between the inner ring gear 2 2 1 of the rear ring gear 2 2 and the outer ring gear 2 1 1 of the rear sun gear 2 1 . In this embodiment, the rear bracket 7 1 side is provided with 201102539. The planetary gears 7 2 thereby drive the output wheels 7 through the planetary gears 7 2 to output the shifting power when the rear ring gear 2 2 and the rear sun gear 2 1 are rotated. The one-way bearing 31 of the present embodiment is disposed on the transmission shaft 3 that is coupled to the front ring gear 11, and is adjacent to the front ring gear 11. The other one-way bearing 4 1 is disposed at the end of the rear ring gear 2 2 and the drive shaft 4 coupled to the front sun gear 12 and abuts against the rear ring gear 2 2 . When the shift control device of the embodiment is actuated, the engine system (not shown) of the automobile transmits power to the main shaft 61, and when the main shaft 61 is connected to be driven by the power, the transmission is transmitted through the arm 6 2 . The force is applied to the inner collar 52 by the swing arm 6 3 and the planetary gear 5 is pulled through the outer ring 5 1 to drive the front ring gear 11 and the front sun gear 12 to rotate. In the principle of leverage, the axis of the planetary gear 5 is the fulcrum B, and the tooth portion of the planetary gear 5 that meshes with the front ring gear 11 and the front sun gear 12 is the end point of the force applied relative to the fulcrum. For convenience of explanation, one end point of the meshing direction of the planetary gear 5 and the front ring gear 11 is defined as an external force point C, and the other end of the meshing direction of the planetary gear 5 and the front sun gear 12 is defined as Apply force point D internally. As shown in Fig. 4, when the electromagnetic clutch 6 5 1 of the drive motor 65 is coupled to the main shaft 61, the main bevel gear 64 rotates with the main shaft 61, so that the main bevel gear 64 and the main shaft 6 1 at this time At the same speed, the two bevel gears 6 6 1 and the main bevel gears 64 are in a state of static engagement during the rotation of the main shaft, so that the slider 6 6 2 in the frame 66 stays at the screw 6 6 In the middle position of 3, the pivot point A of the swing arm 6 3 and the inner collar 5 2 is located at the same applied position of the fulcrum B. 201102539 As shown in Fig. 5, when the slider 6 6 2 in the frame 66 pivots, the point A is moved to the middle position between the front ring gear 1 1 and the front sun gear 12 At this time, the force of the main shaft 61 is relatively applied to the axis of the planetary wheel 5 (ie, the fulcrum b in the figure), so that the teeth at both ends of the planetary gear are equally applied to the front ring gear 1 1 And the front sun gear 12, the front ring gear 11 and the front sun gear 12 are subjected to the urging force of each of the main shafts 61. If the resistance of the sun gear 12 and the ring gear 11 is not calculated, the entire system is The 1:1 speed is faster than the same speed. As shown in Fig. 6, when the driving motor 65 drives the main bevel gear 64 to rotate forward with respect to the rotating main shaft, the rotational speed of the main bevel gear 64 is relatively higher than the main shaft 6 1 'two bevel gears 6 6 1 Starting to rotate with the rotation speed of the main bevel gear 64 4, the slider 6 6 2 in the frame 6 6 is moved outward, so that the pivot point A of the swing arm 6 3 and the inner collar 5 2 is directed toward the front ring gear 1 1 As shown in Fig. 7, since the slider 6 Θ 2 in the frame 66 moves the pivot point A to the external force point c, the force of the main shaft 6 i is completely applied to the planetary gear. 5 is engaged with the tooth portion of the front ring gear 1 i, and the planetary gear 5 is engaged with the tooth portion of the front sun gear 12 at this time, and the force of the planetary gear 5 is completely applied to the front ring gear 丄i direction, and the front The sun gear 1 2 cannot be reversed due to the installation of the one-way bearing 4 1 , so at this time, the planetary gear 5 is guided by the ring gear of the front sun gear 1 2 and rotates clockwise, so that the front ring gear 1 1 achieve a small acceleration effect. As shown in Fig. 8, when the driving motor 65 drives the main bevel gear 64 to reverse with respect to the rotating main shaft 61, at this time, the main bevel gear 64 has a rotational speed phase 201102539 which is lower than the main shaft 6 1, two pairs of umbrellas. The gear 6 6 1 starts to rotate with the rotation speed of the main bevel gear 64, so that the slider 6 6 2 in the frame 6 6 moves inward, so that the pivot point A of the swing arm 6 3 and the inner collar 5 2 faces the front sun. Wheel 1 2 swings. As shown in Fig. 9, since the slider 6 6 2 of the frame 66 moves the pivot point A to the inner applied point d, the force of the main shaft 61 is fully applied to the mesh gear 5 to mesh. At the tooth portion of the front sun gear 12, the planetary gear 5 is engaged with the tooth portion of the front ring gear 11 at this time, and the force of the planetary gear 5 is completely applied toward the front sun gear 12, and the front ring The gear 1 1 cannot be reversed due to the installation of the one-way bearing 31. Therefore, the planetary gear 5 is guided by the inner ring gear 1 1 1 of the front ring gear 1 1 and rotates counterclockwise, so that the front sun gear reaches a large The effect of acceleration. As shown in FIG. 10, when the slider 6 6 in the frame 66 moves the pivot point A from the fulcrum B to the outward force application point C, the tooth portion of the planetary gear 5 drives the front ring gear 11 The force is increased relative to the force of the front sun gear 12 due to the dispersion of the phasors, and is relatively decremented when the pivot point A is gradually moved from the outer applied point C to the fulcrum B. On the contrary, as shown in the first working diagram 1, when the fulcrum B is gradually moved toward the inner application point D, the tooth portion of the planetary gear 5 drives the force of the front sun gear 12 to increase with respect to the force of driving the front ring gear 11. When the contact point A moves gradually from the inner applied point D to the fulcrum b, it is relatively decremented. It is worth mentioning that, in practice, due to environmental factors, the front ring gear 1 1 and the front sun rim 2 will change the load of gravity, so the transmission between the planetary gear and the front ring gear and the front sun gear will The error is generated. In order to reduce the error caused by the environmental factor of 201102539, the drive motor 65 inputs the control signal through the external device as described above, and the relative rotational speed between the main bevel gear 64 and the spindle 61 is calculated. Corresponding to the actual displacement of the slider 6 6 2 . As shown in FIG. 2, the external device of the present embodiment is a central processing unit 167, which receives the status signal required for the vehicle to shift, and the status signal is processed and output to an output control unit 6.8. The variable speed motor 65 is controlled to be actuated, and the pivot point A is arbitrarily changed between the external force point C and the inner force point D by the control of the external device according to the shifting demand, so as to achieve the requirement of the stepless shifting. In the embodiment, the status signal includes an engine speed signal, a shift lever position signal, an accelerator pedal signal, a transmission input shaft speed signal, a transmission output shaft speed signal, a speed signal, and a torque varying device application point position signal. The output control unit 6 8 includes a variable speed motor 65 electromagnetic clutch 6 5 1 switch, a positive and negative rotation of the variable speed motor 65 and a switch, and a warning light of the cockpit dashboard. Therefore, the inner ring 5 is driven by the driving unit 6 to engage the inner ring 5 2 with the planetary gear 5 to engage the arc between the front ring gear 11 and the front sun gear 12, and the pivot point A has a larger radius than the planet. The radius of the gear 5 is increased or decreased by the distance between the pivot point A and the center of the planetary gear 5, so that the planetary gear 5 drives the front ring gear 1 1 and the front sun gear 12 to rotate, respectively, to the front ring gear 1 1 and The front sun gear 1 generates a vector change and changes the applied torque, so that the front ring gear 11 or the front sun gear 12 generates an acceleration speed difference under the limitation of one-way rotation. In other words, the driving unit 6 drives the inner collar 52 2 through the swing arm 63 3 at the eccentric position, and drives the pivot point A to move within the range of the external force point C and the inner force point D, and the pivot point A External force 12 201102539 Point C moves to make the planetary gear 5 rotate clockwise, the pivot point A moves inwardly to the point D to cause the planetary gear 5 to rotate counterclockwise, and the planetary gear 5 changes through the driving direction. A difference in rotational speed between the front ring gear 1 1 and the front sun gear 12 is generated. From the above description, it is not difficult to find the advantages of the present invention: 1. The present invention utilizes a stepless transmission with variable torque, which is simple and sturdy in construction, easy to operate, smaller in size, lighter in weight, and fully mechanically powered and geared. There is no need for a temporary cut-off, a single-axis power input and output of the clutch when fully engaged and shifted. 2, a number of advantages and a wide range of gear ratios make it suitable for use in bicycles, two-wheeled vehicles, automobiles, super heavy vehicles and other gears that require shifting. 3. All of the systems of the present invention are in a closed power circuit, and there is no doubt about kinetic energy loss due to the law of material immortality. 4. The combination of the acceleration gear set 1 and the reduction gear set 2 of the present invention can be arbitrarily combined by one or more groups, and any two axes of the gear set can input one axis® output or any one axis input two-axis output, as needed. Gear ratios or power mixing can make a variety of combinations. 5. The shifting mode of the present invention requires automatic control and precision control derived from the use value, in addition to the mechanical type, electronic control, electric motor control or oil pressure control for digital calculation can be added, and the central processing unit is used to monitor the shift control device. And to achieve the management of the engine system, it is also possible to add hybrid power, which can be input or output by any one of the transmission shafts 3, 4. 13 201102539 The disclosure of the above-described embodiments is intended to illustrate the invention and is not intended to be used in the invention. The precision of the present invention utilizes the torque variation of the lever principle to achieve the speed of replacement. The replacement surface of the mosquito conversion component of the present invention can be achieved by the above detailed description, and the above-mentioned purpose can be achieved well. Application for the present invention. 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 Fig. 5 is a perspective view of the main bevel gear of the present invention when the main bevel gear is rotated relative to the position of the slider. The sixth embodiment of the present invention is the main bevel gear of the present invention, which is opposite to the slider when the figure is not moved. Shifting S1 _Acceleration Turning 7 is a schematic diagram of the driving of the planetary gear of the present invention in the external application. Point C is clockwise rotation. FIG. 8 is the main rotor of the present invention. Turning to the deceleration to turn to the ninth figure is the driving diagram of the planetary gear of the present invention at the internal application point. FIG. 10 is a schematic diagram of driving the planetary gear of the present invention to rotate clockwise between external applied forces. 201102539 Schematic diagram of the driving of the planetary gear in the counterclockwise rotation between the external force point D and the fulcrum B. Fig. 12 is a schematic diagram of the external device control variable speed motor of the present invention [Description of main component symbols] (customized part)
(本發明部分） 加速齒輪組1 内環齒111 外環齒121 軸桿1 3 1 後太陽輪2 1 外環齒2 1 1 傳動軸3 傳動軸4 行星齒輪5 内套環5 2 定位部5 2 2 主軸6 1 擺臂6 3 主傘齒輪6 4 離合器6 5 1 副傘齒輪6 6 1 中央處理單元6 7 前環齒輪11 前太陽輪12 前支架1 3 減速齒輪組2 後環齒輪2 2 内環齒2 2 1 單向軸承3 1 單向軸承41 外套環5 1 環凹槽5 2 1 驅動單元6 支臂6 2 樞軸6 3 1 變速馬達6 5 框架6 6 滑塊6 6 2 輪出控制單元6 8 15 201102539(Invention part) Acceleration gear set 1 Inner ring tooth 111 Outer ring tooth 121 Shaft 1 3 1 Rear sun gear 2 1 Outer ring gear 2 1 1 Drive shaft 3 Drive shaft 4 Planetary gear 5 Inner collar 5 2 Positioning part 5 2 2 Spindle 6 1 Swing arm 6 3 Main bevel gear 6 4 Clutch 6 5 1 Pair bevel gear 6 6 1 Central processing unit 6 7 Front ring gear 11 Front sun gear 12 Front bracket 1 3 Reduction gear set 2 Rear ring gear 2 2 Inner ring gear 2 2 1 One-way bearing 3 1 One-way bearing 41 Outer ring 5 1 Ring groove 5 2 1 Drive unit 6 Arm 6 2 Pivot 6 3 1 Variable speed motor 6 5 Frame 6 6 Slider 6 6 2 Wheel Out control unit 6 8 15 201102539
輸出輪7 行星齒輪7 2 支點B 内施力點D 後支架7 1 樞接點A 外施力點COutput wheel 7 Planetary gear 7 2 Pivot point B Internal force point D Rear bracket 7 1 Pivot point A External force point C