201109232 六、發明說明 【發明所屬之技術領域】 本發明是關於自行車，詳言之是關於一種具備踏板踩 踏型驅動力傳遞機構之自行車。 【先前技術】 關於具備踏板踩踏型驅動力傳遞機構之自行車，已有 爲了減輕踩踏力、或增強傳遞力的各種提案。例如，專利 文獻1揭示一種自行車’係與自行車踏板之曲軸同心狀地 固設內齒齒輪，在曲軸可旋轉自如地軸支的太陽齒輪，將 與該太陽齒輪相同直徑且嚙合在太陽齒輪及內齒齒輪的行 星齒輪，在從自行車踏板之曲柄臂沿著該曲柄臂之延長線 延伸的延長臂部可旋轉自如地予以軸支，且將前輪側鏈輪 同軸地固定在前述太陽齒輪。 根據該專利文獻1所揭示的自行車，由於太陽齒輪與 行星齒輪的直徑相同，因此使踏板旋轉一次時，太陽齒輪 會旋轉四次，齒輪比會形成四比一，比起以往可加快速 度。然而，該專利文獻1所揭示的自行車，由於在內齒齒 輪與太陽齒輪之間介設可傳遞踩踏力的行星齒輪，因此使 後輪旋轉的作用點是靠近曲軸側，以致將施加在踏板的踩 踏力傳遞至太陽齒輪的力臂的長度變短’除此之外’在內 齒齒輪與太陽齒輪之間的摩擦阻力會變大，因而有需要較 大踩踏力的缺點。 又，專利文獻2提案一種自行車’在曲柄臂前端設置 -5- 201109232 內齒輪，且設置與該內齒輪嚙合而旋轉的外齒 齒輪與外齒輪的齒輪比設定成二比一，並且在 端從形成曲柄臂之旋轉中心的曲軸朝向前方， 輪嚙合在前述內齒輪之從曲軸離開之側的齒 下，以踏板的踩踏面向上形成大致水平姿勢的 固定在外齒輪，俾以較少的踩踏力獲得較大 力。 然而，該專利文獻2所揭示的自行車，由 板的軸比設在曲柄臂前端的內齒輪之外周面 側，因此從力的作用點到旋轉軸的力臂長度變 時會有無法以較少的踩踏力獲得較大的旋轉 況。 通常，在自行車，要將踏板的踩踏力高效 轉驅動力時，安裝有踏板的曲柄臂之長度所產 作用」有很大的影響，但是曲柄臂的長度受到 之距離的限制，無法自由的加長。因此，以往 際上還無法以減輕踩踏力的狀態高效率地傳 力。 [先前技術文獻] [專利文獻] [專利文獻1 ]曰本特開平6- 1 7 1 5 74號 [專利文獻2 ]日本特開平9 _ 3 〇丨2 5 7號 【發明內容】 輪，將該內 曲柄臂的前 且前述外齒 輪部的狀態 方式將踏板 的旋轉驅動 於安裝有踏 更靠近曲軸 短，因而有 驅動力的情 率地變成旋 生的「槓桿 曲軸與地面 的自行車實 遞旋轉驅動 公報 公報 -6- 201109232 [所欲解決之技術課題] 本發明是爲了解決上述的先前技術的缺 的，其課題在於··提供一種能以減輕踩踏力 地傳遞旋轉驅動力的具備踏板踩踏型驅動力 行車。 [解決問題之技術手段] 爲了解決上述課題，本發明人著眼於旋 用的相位齒輪機構，根據經由曲柄臂使相當 之轉子的構件旋轉，並經由偏心輪將該旋轉 的旋轉軸的構想，反覆進行嘗試錯誤的結果 固定外齒齒輪相對於自行車車體予以固定， 使與該固定外齒齒輪嚙合的轉子內齒齒輪旋 心輪旋轉，並將踩踏力傳遞至鏈輪等的驅動 踩踏力的狀態高效率地傳遞旋轉驅動力，因 明。 亦即，爲了解決上述課題，本發明提供 踩踏型驅動力傳遞機構之自行車，係具有： 體可旋轉自如地支承的旋轉軸；相對於前述 呈偏心，且可繞前述旋轉軸的軸心旋轉的偏 旋轉軸同心，且隨著前述偏心輪的旋轉可繞 軸心旋轉的驅動輪；與前述旋轉軸的軸心同 自行車之車體呈固定的固定外齒齒輪；在沿 之軸方向的一側具有與前述固定外齒齒輪 點而開發完成 的狀態高效率 傳遞機構之自 轉式引擎所採 於旋轉式引擎 傳遞至自行車 發現，藉由將 並經由曲柄臂 轉，藉此使偏 輪，能以減輕 而完成了本發 一種具備踏板 被自行車之車 旋轉軸的軸心 心輪；與前述 前述旋轉軸的 心，且相對於 著前述旋轉軸 嚙合的內齒齒 201109232 輪，在另一側具有將前述偏心輪可滑動旋轉自如地予以支 承的軸承部，且相對於前述固定外齒齒輪的中心呈偏心的 轉子；以及使前述轉子旋轉的曲軸。 本發明之具備踏板踩踏型驅動力傳遞機構之自行車， 藉由踩踏踏板並非直接使旋轉軸旋轉，而是先使轉子旋 轉，並藉由該旋轉經由偏心輪使旋轉軸旋轉，因此可利用 以從偏心輪的偏心軸到轉子所產生的旋轉力之作用點的距 離作爲力臂長度的力矩。因此，比起利用曲柄臂直接使旋 轉軸旋轉的情況，可利用較輕的踩踏力使旋轉軸及驅動輪 旋轉。 本發明之具備踏板踩踏型驅動力傳遞機構之自行車， 在其較佳的一個樣態，前述偏心輪安裝在前述旋轉軸，前 述固定外齒齒輪在中心部具有貫穿前述旋轉軸之軸方向的 貫通孔，而且前述曲軸是貫穿前述固定外齒齒輪的前述貫 通孔而安裝在前述轉子的中心。以這種方式構成驅動力傳 遞機構的情況，經由曲柄臂使曲軸旋轉，轉子可一邊使其 內齒齒輪與固定外齒齒輪嚙合，一邊繞固定外齒齒輪的周 圍旋轉，同時，被轉子的軸承部可滑動旋轉自如地支承的 偏心輪可繞旋轉軸的軸心旋轉，而使驅動輪旋轉。 將本發明之具備踏板踩踏型驅動力傳遞機構之自行車 以上述方式構成的情況，在與上述驅動輪存在側的相反側 也可以設置與上述大致相同的驅動力傳遞機構，以將左右 雙方踏板之踩踏力利用在鏈輪等之驅動輪的旋轉。亦即， 本發明之具備踏板踩踏型驅動力傳遞機構之自行車，在其 -8 - 201109232 較佳的一個 傳遞機構， 於前述旋轉 心輪；在比 車之車體呈 旋轉軸貫穿 定外齒齒輪 滑動旋轉自 定外齒齒輪 2轉子之中 前述偏心輪 又，本 車，在其較 車體呈固定 心部具有貫 是貫穿前述 與前述轉子 驅動力傳遞 其內齒齒輪 周圍旋轉， 的偏心輪會 遞機構相同 轉子，因此 軸也不會使 樣態，在驅 同時，在與 軸的軸心呈 第2偏心輪 固定，與旋 之貫通孔的 嚙合的內齒 如地予以支 的中心呈偏 心的曲軸； 的偏心方向 發明之具備 佳的其他樣 的構件可旋 穿前述旋轉 貫通孔而與 是藉由歐丹 機構的情況 與固定外齒 同時，被轉 旋轉而使驅 ，但是曲軸 即使轉子繞 其軸心移動 動輪存在側 驅動輪存在 偏心地安裝 更靠近車體 轉軸的軸心 第2固定外 齒輪，且具 承的軸承部 心的第2轉 前述第2偏 相差1 8 0度 踏板踩踏型 態，前述偏 轉地支承， 軸之軸方向 前述旋轉軸 連結機構而 ，藉由使曲 齒輪嚙合， 子的軸承部 動輪旋轉， 的旋轉是藉 固定外齒齒 。因此，可 具備如上所 側的相反側 在前述旋轉 內側的位置 同心且在中 齒齒輪；具 有將前述第 ，且相對於 子；以及安 心輪的偏心 相位。 驅動力傳遞 心輪被相對 前述固定外 的貫通孔， 同軸地連結 連結。以這 軸旋轉，轉 一邊繞固定 可滑動旋轉 這點與前述 由歐丹連結 輪的周圍旋 使曲軸與旋 述的驅動力 具有：相對 軸的第2偏 相對於自行 心部具有供 有與第2固 2偏心輪可 前述第2固 裝在前述第 方向相對於 機構之自行 於自行車之 齒齒輪在中 且前述曲軸 ，前述曲軸 種方式構成 子會一邊使 外齒齒輪的 自如地支承 的驅動力傳 機構傳遞至 轉移動，曲 轉軸同軸地 -9 - 201109232 連結，而構成簡單的驅動力傳遞機構。 本發明之具備踏板踩踏型驅動力傳遞機構之自行車， 固定外齒齒輪與轉子所具備的內齒齒輪的齒輪比最好是 2 : 3。外齒齒輪與內齒齒輪的齒輪比爲2 : 3的情況，當轉 子旋轉一次，被轉子的軸承可滑動旋轉自如地支承的偏心 輪就會旋轉三次，因此可加快曲柄臂所進行的旋轉而傳遞 至旋轉軸及驅動輪，因此可將旋轉驅動力高效率地傳遞至 驅動輪。 [發明之功效] 根據本發明之具備踏板踩踏型驅動力傳遞機構之自行 車，由於能以減輕踩踏力的狀態加快曲軸的旋轉而傳遞至 驅動輪，可高效率地傳遞旋轉驅動力，因此可獲得即使是 腳力較弱的使用者也容易利用自行車的優點。 【實施方式】 以下’利用圖面來詳細說明本發明，但是本發明當然 不限於圖面所示者。 第1圖是本發明之具備踏板踩踏型驅動力傳遞機構之 自行車之一例的側視圖。第1圖中，符號丨是本發明之具 備踏板踩踏型驅動力傳遞機構之自行車，符號2是鏈輪或 滑輪等的驅動輪’符號3是將驅動輪2的旋轉力傳遞至後 輪的鏈條或皮帶等的傳動帶。符號4是踏板，符號5是曲 柄臂’符號6是固定外齒齒輪，藉由固定構件7a、7b固 -10- 201109232 定於自行車1之車體8。符號9是具有與固定外齒齒輪6 嚙合的內齒齒輪的轉子。 第2圖是將第丨圖的驅動力傳遞機構之主要部位放大 而顯示的部分截面俯視圖，對於與第1圖相同的構件賦予 相同的符號。第2圖中，符號1〇是旋轉軸，符號u是底 部托架’符號1 2是軸承’藉由軸承1 2，旋轉軸1 〇是可 旋轉自如地支承在底部托架11內。首先，針對第2圖中 車體8的右側’也就是面向自行車1行進方向之右側的驅 動力傳遞機構加以說明，在旋轉軸1 〇的右側延長部，相 對於旋轉軸1 0之軸心呈偏心地安裝有偏心輪} 3。 鏈輪等的驅動輪2也是被固定在旋轉軸10的右側延 長部’隨著旋轉軸10的旋轉，驅動輪2也會旋轉。驅動 輪2亦可不固定在旋轉軸1 〇 ’而是固定在偏心輪1 3，或 是亦可固定在旋轉軸1 0及偏心輪1 3雙方。 轉子9是在靠近車體8側具有經由軸承丨2將偏心輪 1 3可滑動旋轉自如地予以支承的軸承部，在遠離車體8 側具有與固定外齒齒輪6之外齒齒輪嚙合的內齒齒輪 9g。符號6g表示固定外齒齒輪6的外齒齒輪，第2圖所 示的狀態是自行車1之行進方向前方部分的內齒齒輪9g 與外齒齒輪6 g嚙合的狀態，在行進方向後方部分，兩者 是處於分開的狀態。此外，轉子9的中心是相對於固定外 齒齒輪6的中心呈偏心。 符號8 a、8 b是將固定構件7 a ' 7b相對於車體8予以 支承的支承柱。固定外齒齒輪6是在旋轉軸1 〇之軸方向 -11 - 201109232 的延長線上的位置，經由固定構件7a、7b及支承柱8a、 8b相對於車體8呈固定。固定外齒齒輪6的中心與旋轉 軸10的軸心一致，旋轉軸10與固定外齒齒輪6同心。符 號6a是沿旋轉軸10的軸方向貫穿固定外齒齒輪6之中心 部的貫通孔。 符號14是曲軸，曲軸14是貫穿固定外齒齒輪6的貫 通孔6 a，其一端是與轉子9同心地被固定在轉子9的中 心，另一端是被固定在曲柄臂5的基端部。當然，在曲柄 臂5的前端部安裝有或是可安裝踏板4。 第2圖中，車體8的左側，也就是面向自行車1行進 方向之左側的驅動力傳遞機構，基本上與右側的機構相 同，但是不需要設置驅動輪2，因此構造較爲簡單。亦 即，在旋轉軸1 0之左側的延長部，首先，第2固定外齒 齒輪6 2是經由固定構件1 5相對於車體2的底部托架1 1 呈固定。第2固定外齒齒輪62的中心與旋轉軸1 0的軸心 一致’兩者爲同心。在第2固定外齒齒輪62是與右側的 固定外齒齒輪6 —樣在中心部設有貫通孔62a，旋轉軸1 0 會貫穿該貫通孔62a然後更進一步朝左側延伸。符號62g 是第2固定外齒齒輪62的外齒齒輪。 在旋轉軸1 0之比第2固定外齒齒輪62更靠左側的延 長部，相對於旋轉軸1 0之軸心偏心地安裝有第2偏心輪 1 32。符號92是第2轉子。第2轉子92與右側的轉子9 一 樣是相對於第2固定外齒齒輪62的中心呈偏心，且在左 側具有經由軸承1 2將第2偏心輪1 3 2可滑動旋轉自如地 -12- 201109232 予以支承的軸承部，在右側具有與第2固定外齒齒輪62 嚙合的內齒齒輪92g。此外，如第2圖所示，第2偏心輪 1 3 2的偏心方向是與右側偏心輪1 3之偏心方向相差1 8 0度 相位，第2圖之左側所示的狀態是與右側相反，處於自行 車1之行進方向後方部分的內齒齒輪92g與外齒齒輪62g 嚙合的狀態，在行進方向前方部分，兩者是處於分開的狀 態。 符號142是第2曲軸，第2曲軸142，其一端是與第 2轉子92同心地固定在第2轉子92的中心，另一端是被 固定在第2曲柄臂52的基端部。當然，在第2曲柄臂52 的前端部安裝有或是可安裝踏板4。 第3圖是第2圖的X-X’截面圖。如第3圖所示，轉 子9的內齒齒輪9 g的直徑比固定外齒齒輪6的外齒齒輪 6g大，內齒齒輪9g的齒數比外齒齒輪6g多。因此，內 齒齒輪9g與外齒齒輪6g會在其一部分嚙合，但是在其他 部分是分開的。外齒齒輪6g與內齒齒輪9g的齒數比，也 就是齒輪比並沒有特別的限制，但最好是整數比，較佳 爲，外齒齒輪6g與內齒齒輪9g的齒輪比爲2 : 3。外齒 齒輪6 g與內齒齒輪9 g的齒輪比爲2 : 3的情況，在轉子 9 一邊使內齒齒輪9 g與外齒齒輪6 g嚙合，一邊繞外齒齒 輪6g旋轉一次的期間，偏心輪1 3會旋轉三次，可獲得適 當的增速比。此外，關於相位齒輪機構的齒輪比與旋轉數 的關係，例如詳述於GP企劃中心編「馬自達•旋轉式引 擎（Mazda· Rotary engine)的歷史」GRAND PRIX 株式會 -13- 201109232 社出版、2003年2月10日初版發行、28-36頁、44頁。 第4圖是第2圖的Y-Y’截面圖。符號l〇c是旋轉軸 1 〇的軸心，符號1 3 c是偏心輪1 3的中心，固定有偏心輪 1 3的旋轉軸1 0的軸心1 〇 c是從偏心輪1 3的中心1 3 c偏 移圖中e所不的長度。 接下來，利用第5圖〜第8圖來說明本例之踏板踩踏 型驅動力傳遞機構的動作。第5圖〜第8圖中，各圖的（a) 是顯示出踩踏踏板4時經由曲柄臂5使曲軸14旋轉，藉 此，轉子9使其內齒齒輪9g與固定外齒齒輪6的外齒齒 輪6g嚙合，同時繞固定外齒齒輪6的周圍旋轉的轉子9 之運動；各圖的（b)顯示出這時的偏心輪13之運動；各圖 的（c)顯示出這時的旋轉軸1 〇之運動。此外，爲了方便， 並未顯示出內齒齒輪9g及外齒齒輪6g。 如第5圖~第8圖所示，當轉子9繞固定外齒齒輪6 的周圍旋轉時，同時，被轉子9的軸承部可滑動旋轉自如 地支承的偏心輪1 3會以偏心軸，也就是以旋轉軸丨〇的軸 心1 0c爲中心朝圖中箭頭方向旋轉，該結果，固定有偏心 輪13的旋轉軸10也會朝圖中箭頭方向旋轉。這時，如各 圖（b)所示’由於偏心輪1 3之旋轉的中心，也就是旋轉軸 1 0的軸心1 0 c從偏心輪1 3的中心1 3 c偏移前述距離e， 因此由轉子9施加在偏心輪1 3的旋轉力，會形成以從軸 心1 0 c通過中心1 3 c到偏心輪丨3之外周的距離作爲力臂 長度的力矩’而高效率地傳遞至旋轉軸1 〇。因此，能以 減輕踩踏力的狀態使旋轉軸1 〇旋轉，且使驅動輪2旋轉 -14- 201109232 而使自行車1行進。 又，如前所述，在外齒齒輪6g與內齒齒輪 比爲2 : 3的情況，在轉子9繞固定外齒齒輪6 轉一次的期間，偏心輪1 3會旋轉三次，因此比 的旋轉，旋轉軸10的旋轉數會加快三倍，可高 驅動輪2旋轉，而使自行車1以高速行進。 第2圖之比車體8更靠近左側，也就是自行 進方向左側的驅動力傳遞機構的動作也是與根據 第8圖所說明的右側機構的動作相同，但是第 1 3 2的偏心方向與偏心輪1 3的偏心方向相差1 8 0 因此，利用左右腳踩踏踏板4，經由曲柄臂5及 臂52，使曲軸14及第2曲軸142，更進一步使 第2轉子9 2以1 8 0度的相位差旋轉，以利用雙 力，使驅動輪2旋轉，並使自行車〗行進。 此外，以上的例子中，自行車1之行進方向 就是驅動輪2存在側的固定外齒齒輪6是藉 8a、8b及固定構件7a、7b固定在車體8，但是 齒齒輪6相對於車體8予以固定的方法並不限定 如，在自行車1於驅動輪2及傳動帶3周圍具有 的情況下’亦可藉由將固定外齒齒輪6固定在此 而相對於車體8予以固定。 第9圖是驅動力傳遞機構之其他例子的部分 圖。本例的動力傳遞機構，固定外齒齒輪6是安 形支承構件1 6的一端。支承構件1 6的另一端是 9 g的齒輪 的周圍旋 起曲軸14 效率地使 車1之行 第5圖~ 2偏；L·、輪 度相位。 第2曲柄 轉子9及 腳的踩踏 右側，也 由支承柱 將固定外 於此。例 鏈條蓋板 鏈條蓋板 截面俯視 裝在圓筒 安裝在底 '15- 201109232 d托架11，因此固定外齒齒輪6相對於自行車1的車體8 得以固定。支承構件1 6亦可不經由底部托架n，而是直 接安裝在車體8。偏心輪13是在支承構件16的周圍經由 軸承1 2可旋轉自如地支承。圓筒形的支承構件1 6是與旋 轉軸1 0同軸’因此偏心輪1 3可繞旋轉軸1 〇的軸心旋 轉。此外，支承構件1 6的形狀並不限於圓筒形。支承構 件16是只要可將固定外齒齒輪6相對於車體8予以固 定，則可具有任何形狀，例如亦可爲截面三角形、四角 形、五角形、六角形、橢圓形等的筒狀構件，或亦可僅爲 用來連結固定外齒齒輪6及車體8或底部托架丨】的複數 根棒狀構件。 在偏心輪13的周邊部藉由螺栓螺帽等的固定具17來 安裝驅動輪2 ’驅動輪2會隨著偏心輪1 3的旋轉而繞旋 轉軸1 0的軸心旋轉。此外’在本例，驅動輪2是直接安 裝在偏心輪1 3，但是亦可將會繞旋轉軸1 〇之軸心旋轉的 其他構件安裝在偏心輪1 3，並將驅動輪2安裝在其他構 件。 在固定外齒齒輪6的中心部設有貫穿旋轉軸1 〇之軸 方向的貫通孔6a’曲軸14是貫穿該貫通孔6a而連結成 與旋轉軸1 0同軸。符號1 8是設在轉子9之端部的凸部， 符號1 9是中間節，符號2 0是驅動板，符號2 1是將驅動 板2 0固定在曲軸1 4的固定構件，由凸部！ 8、中間節i 9 及驅動板20構成歐丹連結機構21。曲軸14與轉子9是 藉由該歐丹連結機構2 1而連結，曲軸1 4的旋轉可經由歐 -16- 201109232 丹連結機構21傳遞至轉子9。 第10圖是第9圖的X-X，截面圖。符號l〇c是旋轉軸 1 〇的軸心’也是曲軸1 4的軸心，符號1 3 c是偏心輪1 3 的中心。如圖所示，偏心輪1 3的中心1 3 c是從旋轉軸1 0 的軸心1 0 c偏移圖中e所示的長度。因此，與先前所舉的 例子相同，由轉子9施加在偏心輪13的旋轉力’會形成 以從軸心1 0 c通過中心1 3 c到偏心輪1 3之外周的距離作 爲力臂長度的力矩而高效率地傳遞至驅動輪2 »因此，能 以減輕踩踏力的狀態使驅動輪2旋轉而使自行車1行進。 第1 1圖是第9圖的Y-Y’截面圖。如第1 1圖所示， 轉子9的內齒齒輪9g的直徑比固定外齒齒輪6的外齒齒 輪6g大，內齒齒輪9g的齒數比外齒齒輪6g多。因此， 內齒齒輪9g與外齒齒輪6g會在其一部分嚙合，但在其他 部分是分開的。本例的驅動力傳遞機構，外齒齒輪6 g與 內齒齒輪9g的齒數比，也就是齒輪比也沒有特別的限 制，但最好是整數比，較佳爲，外齒齒輪6g與內齒齒輪 9 g的齒輪比爲2 : 3。外齒齒輪6 g與內齒齒輪9 g的齒輪 比爲2 : 3的情況，轉子9會使內齒齒輪9 g與外齒齒輪 6g嚙合，同時在繞外齒齒輪6g的周圍旋轉一次的期間， 偏心輪1 3會旋轉三次’可獲得適當的增速比。 第12圖是歐丹連結機構21的分解圖。如圖所示，在 轉子9的端部是以彼此隔著1 80度之間隔的方式設有凸部 1 8、1 8，在中間節1 9的一側是在與凸部1 8、1 8相對向的 位置，以彼此隔著1 8 0度之間隔的方式設有溝槽1 9 a、 -17- 201109232 1 9 a。在中間節1 9的相反側’同樣以隔著丨8 〇度之 方式設有溝槽1 9b、1 9b ’但是其位置與溝槽丨9a、 差90度。又，在驅動板20是在與溝槽19b、19b 的位置，以彼此隔著1 8 0度之間隔的方式設有凸部 2 0 a ° 歐丹連結機構21可藉由使轉子9的凸部1 8、 間節19的溝槽19a、19a嵌合，使驅動板20 20a、20a與中間節1 9的溝槽19b、1 9b嵌合而組 部18' 18及凸部20a、20a分別在溝槽19a、19a 1 9b、1 9b內可滑動移動自如，因此旋轉時，即使 相對於驅動板20，朝連結溝槽！ 9a、1 9a的方向、 其相差90度之連結溝槽19b、19b的方向任一方向 其移動也會因爲凸部18、18及20a、20a分別 19a、19a內及溝槽19b、19b內滑動移動而被吸收 板20的中心20c並不會移動。曲軸14由於是藉由 件22以貫穿驅動板20的中心20c的方式固定於 2〇，因此曲軸14的中心也不會移動。 如上所述，即使藉由歐丹連結機構2 1連結曲車 轉子9，使曲軸1 4旋轉而使轉子9 一邊讓其內齒j 與外齒齒輪6g嚙合，一邊繞固定外齒齒輪6的周 移動，曲軸 14也不會移動，因此可將曲軸 14與 1 〇同軸地連結，因而可獲得驅動力傳遞機構之構 單的優點。又，由於可將曲軸與旋轉軸1 〇同軸地 因此與驅動輪存在側之相反側的曲軸1 4的旋轉力 間隔的 19a相 相對向 2 0a、 1 8與中 的凸部 裝。凸 及溝槽 轉子 9 以及與 移動， 在溝槽 ，驅動 固定構 驅動板 由14及 齒輪9g 圍旋轉 旋轉軸 造變簡 連結， 也可經 -18 - 201109232 由旋轉軸10，一倂利用於轉子9的旋轉，也就是驅動輪2 的旋轉，因此具有可發揮利用雙腳踩踏踏板的自行車的最 大優點的長處。再者，由於可將曲軸14與旋轉軸10同軸 地連結，因此不需要對以往的自行車的驅動機構施以大幅 度的變更，即可成爲本發明之具備踏板踩踏型驅動力傳遞 機構之自行車。 此外’亦可將設在轉子9的凸部1 8、1 8作成溝槽， 將設在中間節1 9的溝槽1 9 a、1 9 a作成凸部，同樣的，亦 可將設在中間節1 9的溝槽1 9b、1 9b作成凸部，將設在驅 動板20的凸部20a、20a作成溝槽。又，亦可在凸部 18、 18 及 20a、 20a 與溝槽 19a、 19a 及 19b、 19b 的一方 或雙方’例如設置乾式軸承（dry bearing)、平面滾柱軸承 (flat roller bearing)，或是設爲含油軸承，以提高凸部 18、18 及 20a、20a 與溝槽 19a、19a 及 19b、19b 的滑動 性而減少摩擦。 接下來，利用第13圖〜第15圖來說明本發明之踏板 踩踏型驅動力傳遞機構的動作。第1 3圖〜第1 5圖中，各 圖的（a)顯示出踩踏踏板4使曲軸1 4旋轉，經由歐丹連結 機構2 1使轉子9旋轉’轉子9使其內齒齒輪9g與固定外 齒齒輪ό的外齒齒輪6g嚙合，同時繞固定外齒齒輪6的 周圍旋轉的轉子9之運動；各圖的（b)顯示出這時的偏心 輪1 3以及與偏心輪1 3 —同旋轉的驅動輪2之運動。 如第1 3圖〜第1 5圖所示，轉子9繞固定外齒齒輪6 的周圍旋轉時，同時，被轉子9的軸承部可滑動旋轉自如 -19- 201109232 地支承的偏心輪1 3會以偏心軸，也就是以曲軸1 4及旋轉 軸1 0的軸心1 〇 c爲中心朝圖中箭頭方向旋轉，該結果， 被固定在偏心輪1 3的驅動輪2也會朝圖中箭頭方向旋 轉。這時’如各圖（b)所示，由於偏心輪1 3之旋轉的中 心’也就是’曲軸1 4及旋轉軸1 〇的軸心1 〇c是從偏心輪 1 3的中心1 3 c偏移前述距離e，因此由轉子9施加在偏心 輪1 3的旋轉力，會形成以從軸心！ 〇 c通過中心丨3 c到偏 心輪1 3之外周的距離作爲力臂長度的力矩而高效率地傳 遞至驅動輪2。因此，能以減輕踩踏力的狀態使驅動輪2 旋轉而使自行車1行進。 又，如前所述，外齒齒輪6g與內齒齒輪9g的齒輪比 爲2 : 3的情況，在轉子9繞固定外齒齒輪6的周圍旋轉 一次的期間，偏心輪13會旋轉三次，因此比起曲軸14的 旋轉，旋轉軸1 0或驅動輪2的旋轉數會加快三倍，可使 驅動輪2高效率地旋轉，因而可獲得能使自行車丨以高速 行進的優點。如上所述，在本發明之具備踏板踩踏型驅動 力傳遞機構之自行車，雖然也跟外齒齒輪6 g與內齒齒輪 9g的齒輪比有關，但是比起曲軸1 4的旋轉數，驅動輪2 的旋轉數得以加快，因此比起以往的自行車，可將驅動輪 2的直徑縮小，反之，可將藉由傳動帶3與驅動輪2連結 的從動輪的直徑加大，而可減輕踏板4之踩踏所需的力。 如前所述即使減輕踏板4之踩踏所需的力，在本發明之自 行車，驅動輪2的旋轉數比起曲軸1 4的旋轉數仍會加 快，因此可獲得能使自行車以不比習知自行車低的速度行 -20- 201109232 進的優點。附帶一提的，縮小驅動輪2的直徑，在驅動輪 2爲鏈輪的情況，相當於縮小其直徑以減少齒數；加大前 述從動輪的直徑，在前述從動輪爲鏈輪的情況，相當於加 大其直徑以增加齒數。 [產業上的利用可能性] 根據具備踏板踩踏型驅動力傳遞機構之自行車，由於 能以較輕的踩踏力高效率地使自行車行進，因此即使是腳 力不夠的使用者，仍可容易地利用自行車。又，由於踩踏 力的傳遞效率高，因此起步時及上坡路段的負擔減輕將可 實現比以往更長時間、更長距離的行進，因而帶來自行車 之使用機會 '使用範圍、及使用者年齡層的擴大。因此， 本發明實際上會對該產業領域帶來相當大的影響。 【圖式簡單說明】 第1圖是本發明之具備踏板踩踏型驅動力傳遞機構之 自行車之一例的側視圖。 第2圖是驅動力傳遞機構之主要部位的部分截面俯視 圖。 第3圖是第2圖的X-X’截面圖。 第4圖是第2圖的Y-Y’截面圖。 第5(a)〜（c)圖是利用轉子之旋轉，經由偏心輪使旋轉 軸旋轉之動作的說明圖。 第6(a)〜（c)圖是利用轉子之旋轉，經由偏心輪使旋轉 -21 - 201109232 軸旋轉之動作的說明圖。 第7(a)〜（c)圖是利用轉子之旋轉，經由偏心輪使旋轉 軸旋轉之動作的說明圖。 第8(a)~(c)圖是利用轉子之旋轉，經由偏心輪使旋轉 軸旋轉之動作的說明圖。 第9圖是本發明之具備踏板踩踏型驅動力傳遞機構之 自行車的驅動力傳遞機構之其他例子的部分截面俯視圖。 第10圖是第9圖的X-X’截面圖。 第11圖是第9圖的Y-Y’截面圖。 第1 2圖是歐丹連結機構的分解圖。 第13(a)(b)圖是利用轉子之旋轉，經由偏心輪使驅動 軸旋轉之動作的說明圖。 第1 4 ( a)(b)圖是利用轉子之旋轉，經由偏心輪使驅動 軸旋轉之動作的說明圖。 第15(a)(b)圖是利用轉子之旋轉，經由偏心輪使驅動 軸旋轉之動作的說明圖。 【主要元件符號說明】 1 :自行車 2 :驅動輪 3 :傳動帶 4 :踏板 5、 52 :曲柄臂 6、 62:固定外齒齒輪 6 a、6 2 a :貫通孔 -22- 201109232 6g、62g :外齒齒輪 7a、7b :固定構件 8 :車體 8 a、8 b :支承柱 9 、 92 :轉子 9g、92g:內齒齒輪 1 〇 __旋轉軸 l〇c :旋轉軸的軸心 1 1 :底部托架 1 2 :軸承 1 3、1 3 2 :偏心輪 1 3 c :偏心輪的中心 1 4、1 4 2 :曲軸 1 5 :固定構件 1 6 :支承構件 1 7 :固定具 1 8 :凸部 1 9 :中間節 1 9 a、1 9 b :溝槽 2 0 _驅動板 2 〇 a :凸部 2 1 :歐丹連結機構 2 2 :固定構件 e :偏心距離 -23BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a bicycle, and more particularly to a bicycle having a pedal-type driving force transmission mechanism. [Prior Art] Various bicycles having a pedal-type driving force transmission mechanism have been proposed to reduce the pedaling force or to enhance the transmission force. For example, Patent Document 1 discloses a bicycle in which a sun gear is fixed concentrically with a crankshaft of a bicycle pedal, and a sun gear that is rotatably supported by the crankshaft is the same diameter as the sun gear and meshed with the sun gear and the internal tooth. The planetary gear of the gear is rotatably supported by an extension arm extending from the crank arm of the bicycle pedal along an extension line of the crank arm, and the front wheel side sprocket is coaxially fixed to the sun gear. According to the bicycle disclosed in Patent Document 1, since the sun gear has the same diameter as the planetary gear, when the pedal is rotated once, the sun gear rotates four times, and the gear ratio forms four to one, which is faster than in the past. However, in the bicycle disclosed in Patent Document 1, since the planetary gear that can transmit the pedaling force is interposed between the internal gear and the sun gear, the action of rotating the rear wheel is close to the crankshaft side, so that it will be applied to the pedal. The length of the arm that transmits the pedaling force to the sun gear becomes shorter. In addition, the frictional resistance between the internal gear and the sun gear becomes large, and thus there is a disadvantage that a large pedaling force is required. Further, Patent Document 2 proposes a bicycle which is provided with an internal gear of -5 to 201109232 at the front end of the crank arm, and a gear ratio of the externally toothed gear and the externally driven gear which is rotated by meshing with the internal gear is set to be two to one, and The crankshaft forming the center of rotation of the crank arm faces forward, and the wheel meshes under the teeth of the side of the internal gear that is separated from the crankshaft, and is fixed to the external gear with a substantially horizontal posture on the stepping surface of the pedal, and is obtained with less pedaling force. Greater force. However, in the bicycle disclosed in Patent Document 2, since the axial ratio of the plate is provided on the outer circumferential side of the internal gear of the crank arm, the length of the arm from the point of application of the force to the rotating shaft may be reduced. The pedaling force gives a large rotation. Generally, in bicycles, when the pedaling force is to be efficiently driven by the driving force, the length of the crank arm to which the pedal is attached has a large effect, but the length of the crank arm is limited by the distance and cannot be lengthened freely. . Therefore, in the past, it has not been possible to efficiently transmit force in a state where the pedaling force is reduced. [Prior Art Document] [Patent Document] [Patent Document 1] 曰本特开平6- 1 7 1 5 74 [Patent Document 2] Japanese Patent Laid-Open No. 9 _ 3 〇丨 2 5 7 [Invention Content] Wheel, will The state of the front and the outer gear portion of the inner crank arm drives the rotation of the pedal to be shorter than the crankshaft when the pedal is mounted, so that the driving force is turned into a rotation of the "lever crankshaft and the ground bicycle." DRIVER STATEMENT -6-201109232 [Technical Problem to be Solved] The present invention has been made to solve the above-described problems of the prior art, and an object of the present invention is to provide a pedal-type type that can transmit a rotational driving force with a reduced pedaling force. [Means for Solving the Problem] In order to solve the above problems, the inventors of the present invention have focused on the phase gear mechanism for rotation, and rotated the rotating shaft of the rotor by rotating the member corresponding to the rotor via the crank arm. The concept of repeating the attempt to erroneously fix the fixed externally toothed gear fixed relative to the bicycle body, so that the internal gear of the rotor meshing with the fixed externally toothed gear The present invention provides a bicycle having a stepping type driving force transmission mechanism, in order to solve the above problem, in order to solve the above problem, the rotation of the rotary wheel is transmitted to the driving force of the sprocket or the like. The present invention has: a rotating shaft rotatably supported by the body; and a driving shaft that is eccentric and rotatable about an axis of the rotating shaft, and is rotatable about the axis as the eccentric rotates a fixed external gear that is fixed to the body of the bicycle with the axis of the rotating shaft; and a self-rotating type with a high-efficiency transmission mechanism developed in a state along the axial direction of the fixed external gear point The engine is transferred from the rotary engine to the bicycle for discovery, and by rotating the arm through the crank arm, the biasing wheel can be lightened to complete the shaft center wheel having the pedal rotating shaft of the bicycle; And the inner tooth of the aforementioned rotating shaft, and the inner tooth tooth 201109232 wheel meshed with respect to the aforementioned rotating shaft, and the eccentric wheel on the other side a rotor that is rotatably supported, a rotor that is eccentric with respect to the center of the fixed externally toothed gear, and a crankshaft that rotates the rotor. The bicycle with the pedal-type driving force transmission mechanism of the present invention is stepped on by bicycle The pedal does not directly rotate the rotary shaft, but rotates the rotor first, and the rotation shaft is rotated by the rotation via the eccentric wheel, so that the distance from the eccentric shaft of the eccentric to the point of action of the rotational force generated by the rotor can be utilized. As a moment of the length of the arm, the rotation axis and the drive wheel can be rotated by a light pedaling force compared to the case where the crank arm is directly rotated by the crank arm. The bicycle having the pedal stepping type driving force transmission mechanism of the present invention In a preferred aspect, the eccentric wheel is mounted on the rotating shaft, and the fixed externally toothed gear has a through hole penetrating through the axial direction of the rotating shaft at a central portion, and the crankshaft is penetrated through the fixed externally toothed gear. The through hole is attached to the center of the rotor. In the case where the driving force transmission mechanism is configured in this manner, the crankshaft is rotated by the crank arm, and the rotor can rotate around the fixed external gear while meshing the internal gear with the fixed external gear, and at the same time, the bearing of the rotor The eccentrically rotatably supported eccentric is rotatable about the axis of the rotating shaft to rotate the driving wheel. In the case where the bicycle having the pedal-type driving force transmission mechanism of the present invention is configured as described above, the same driving force transmission mechanism as that of the above-described driving wheel may be provided on the side opposite to the side where the driving wheel is present, so that both the left and right pedals are provided. The pedaling force utilizes the rotation of the driving wheels such as the sprocket. That is, the bicycle having the pedal stepping type driving force transmitting mechanism of the present invention has a preferred transmission mechanism in the -8 - 201109232 on the rotating core wheel; and the external gear is inserted through the rotating shaft of the vehicle body. The eccentric wheel of the rotor of the self-aligning externally toothed gear 2 is slidably rotated, and the eccentric wheel of the vehicle is fixed at a fixed core portion of the vehicle body through the aforementioned eccentric wheel that transmits the rotation around the internal gear of the rotor driving force. The same mechanism is used for the same rotor, so the shaft does not make a state. At the same time, the shaft is fixed by the second eccentric with the axis of the shaft, and the center of the meshing with the through hole is eccentric. The eccentric direction of the crankshaft; the other kind of member which is excellent in the invention can be screwed through the aforementioned rotating through hole and is rotated by the rotation of the external tooth at the same time as the fixed external tooth, but the crankshaft rotates even though the rotor The axially-moving moving wheel presence side driving wheel is eccentrically mounted to the second fixed external gear of the shaft center closer to the rotating shaft of the vehicle body, and the second rotation of the bearing core of the bearing body The second partial phase difference is a 180-step pedaling type, and the above-mentioned rotating shaft coupling mechanism is supported by the axial direction of the shaft. When the curved gear is meshed, the rotation of the sub-bearing portion of the movable wheel is fixed. Tooth. Therefore, the opposite side to the side as described above may be provided at the position inside the aforementioned rotation, concentric and in the middle tooth gear; having the eccentric phase of the aforementioned first and opposite sides; and the safety wheel. The driving force transmission core wheel is coaxially coupled to the through hole that is fixed to the outside. Rotating with this axis, rotating the side and fixing the slidable rotation, and the driving force of the crankshaft and the rotation of the above-mentioned Ou Dan connecting wheel are rotated: the second offset of the opposite axis has a supply and a In the second solid- 2 eccentric wheel, the second fixed gear can be freely supported by the externally toothed gear while the second crankshaft is fixed to the crankshaft gear of the bicycle in the first direction. The transmission mechanism transmits to the rotary movement, and the curved shaft is coaxially connected to the -9 - 201109232, and constitutes a simple driving force transmission mechanism. In the bicycle equipped with the pedal-type driving force transmission mechanism of the present invention, the gear ratio of the fixed external gear and the internal gear provided in the rotor is preferably 2:3. When the gear ratio of the external gear to the internal gear is 2:3, when the rotor rotates once, the eccentric wheel rotatably supported by the bearing of the rotor rotates three times, thereby speeding up the rotation of the crank arm. It is transmitted to the rotating shaft and the drive wheel, so that the rotational driving force can be efficiently transmitted to the drive wheels. [Effect of the Invention] The bicycle provided with the pedal-type driving force transmission mechanism according to the present invention can transmit the rotational driving force to the driving wheel by accelerating the rotation of the crankshaft in a state where the pedaling force is reduced, thereby efficiently obtaining the rotational driving force. Even users with weaker feet can easily take advantage of the bicycle. [Embodiment] The present invention will be described in detail below with reference to the drawings, but the present invention is of course not limited to those shown in the drawings. Fig. 1 is a side view showing an example of a bicycle equipped with a pedal-type driving force transmission mechanism according to the present invention. In Fig. 1, the symbol 丨 is a bicycle having a pedal-type driving force transmission mechanism according to the present invention, and the symbol 2 is a driving wheel such as a sprocket or a pulley. The symbol 3 is a chain for transmitting the rotational force of the driving wheel 2 to the rear wheel. Or a belt such as a belt. Reference numeral 4 is a pedal, and symbol 5 is a crank arm. The symbol 6 is a fixed externally toothed gear which is fixed to the vehicle body 8 of the bicycle 1 by fixing members 7a, 7b. Symbol 9 is a rotor having an internal gear that meshes with the fixed externally toothed gear 6. Fig. 2 is a partial cross-sectional plan view showing an enlarged main portion of the driving force transmission mechanism of the second drawing, and the same members as those in Fig. 1 are denoted by the same reference numerals. In Fig. 2, reference numeral 1 is a rotation axis, and symbol u is a bottom bracket. The symbol 1 2 is a bearing. By the bearing 12, the rotary shaft 1 is rotatably supported in the bottom bracket 11. First, the right side of the vehicle body 8 in FIG. 2, that is, the driving force transmission mechanism that faces the right side of the traveling direction of the bicycle 1, will be described. The right side extension of the rotating shaft 1 , is perpendicular to the axis of the rotating shaft 10 Eccentrically mounted with an eccentric wheel} 3. The drive wheel 2 such as a sprocket is also fixed to the right extension portion of the rotary shaft 10. As the rotary shaft 10 rotates, the drive wheel 2 also rotates. The drive wheel 2 may be fixed to the eccentric 13 or not to the rotating shaft 1 〇 ', or may be fixed to both the rotating shaft 10 and the eccentric 13 . The rotor 9 has a bearing portion that slidably and rotatably supports the eccentric 13 via the bearing cymbal 2 on the side closer to the vehicle body 8, and has a meshing gear with the external gear of the fixed external gear 6 on the side away from the vehicle body 8. Gear gear 9g. Reference numeral 6g denotes an externally toothed gear that fixes the externally toothed gear 6, and the state shown in Fig. 2 is a state in which the internal gear 9g in the forward portion of the traveling direction of the bicycle 1 meshes with the externally toothed gear 6g, and in the rear portion in the traveling direction, two The person is in a separate state. Further, the center of the rotor 9 is eccentric with respect to the center of the fixed externally toothed gear 6. Symbols 8a, 8b are support posts for supporting the fixing members 7a'7b with respect to the vehicle body 8. The fixed externally toothed gear 6 is located on an extension of the axial direction -11 - 201109232 of the rotary shaft 1 ,, and is fixed to the vehicle body 8 via the fixing members 7a and 7b and the support columns 8a and 8b. The center of the fixed externally toothed gear 6 coincides with the axis of the rotary shaft 10, and the rotary shaft 10 is concentric with the fixed externally toothed gear 6. The symbol 6a is a through hole that penetrates and fixes the center portion of the externally toothed gear 6 in the axial direction of the rotary shaft 10. Reference numeral 14 is a crankshaft 14 which is a through hole 6a through which the externally toothed gear 6 is fixed, one end of which is fixed to the center of the rotor 9 concentrically with the rotor 9, and the other end of which is fixed to the base end portion of the crank arm 5. Of course, the pedal 4 can be attached or attached to the front end portion of the crank arm 5. In Fig. 2, the left side of the vehicle body 8, that is, the driving force transmission mechanism facing the left side of the traveling direction of the bicycle 1, is basically the same as the mechanism on the right side, but the driving wheel 2 is not required to be provided, so that the structure is relatively simple. That is, in the extension portion on the left side of the rotary shaft 10, first, the second fixed externally toothed gear 6 2 is fixed to the bottom bracket 1 1 of the vehicle body 2 via the fixing member 15. The center of the second fixed externally toothed gear 62 coincides with the axis of the rotating shaft 10'. Both are concentric. In the second fixed externally toothed gear 62, a through hole 62a is formed in the center portion like the fixed externally toothed gear 6 on the right side, and the rotating shaft 10 extends through the through hole 62a and further extends to the left side. Reference numeral 62g is an externally toothed gear of the second fixed externally toothed gear 62. The second eccentric 1 32 is eccentrically attached to the axis of the rotating shaft 10 in the extended portion of the rotating shaft 10 which is further to the left than the second fixed externally toothed gear 62. Reference numeral 92 is a second rotor. Similarly to the rotor 9 on the right side, the second rotor 92 is eccentric with respect to the center of the second fixed externally toothed gear 62, and has the second eccentric 1 2 2 slidably rotatable via the bearing 1 2 on the left side -12-201109232 The bearing portion to be supported has an internal gear 92g that meshes with the second fixed externally toothed gear 62 on the right side. Further, as shown in Fig. 2, the eccentric direction of the second eccentric 1 3 2 is different from the eccentric direction of the right eccentric 13 by 180 degrees, and the state shown on the left side of the second figure is opposite to the right side. The state in which the internal gear 92g in the rear portion of the traveling direction of the bicycle 1 meshes with the externally toothed gear 62g is in a state of being separated from the front portion in the traveling direction. Reference numeral 142 is a second crankshaft, and the second crankshaft 142 has one end fixed to the center of the second rotor 92 concentrically with the second rotor 92, and the other end fixed to the base end portion of the second crank arm 52. Of course, the pedal 4 can be attached to or attached to the front end portion of the second crank arm 52. Fig. 3 is a cross-sectional view taken along line X-X' of Fig. 2. As shown in Fig. 3, the diameter of the internal gear 9g of the rotor 9 is larger than the external gear 6g of the fixed external gear 6, and the number of teeth of the internal gear 9g is larger than that of the external gear 6g. Therefore, the internally toothed gear 9g and the externally toothed gear 6g are engaged at a part thereof, but are separated in other portions. The gear ratio of the external gear 6g to the internal gear 9g, that is, the gear ratio is not particularly limited, but is preferably an integer ratio. Preferably, the gear ratio of the external gear 6g to the internal gear 9g is 2:3. . When the gear ratio of the externally toothed gear 6g and the internal gear 9g is 2:3, the inner gear 9g meshes with the externally toothed gear 6g while the rotor 9 is engaged, and the outer gear 6g rotates once. The eccentric 13 will rotate three times to obtain an appropriate speed increase ratio. In addition, the relationship between the gear ratio and the number of revolutions of the phase gear mechanism is described in detail in the history of the Mazda Rotary engine, edited by the GP Planning Center. GRAND PRIX Ltd.-13-201109232 Press, 2003 The first edition was issued on February 10, 28-36 pages, 44 pages. Fig. 4 is a Y-Y' sectional view of Fig. 2; The symbol l〇c is the axis of the rotation axis 1 ,, the symbol 1 3 c is the center of the eccentric 13 , and the axis 1 〇 c of the rotation axis 10 to which the eccentric 13 is fixed is from the center of the eccentric 13 1 3 c Offset the length of the graph in e. Next, the operation of the pedal-type driving force transmission mechanism of this embodiment will be described using Figs. 5 to 8 . In the fifth to eighth figures, (a) of each figure shows that the crankshaft 14 is rotated via the crank arm 5 when the pedal 4 is stepped on, whereby the rotor 9 has the internal gear 9g and the fixed external gear 6 The tooth gear 6g is meshed while moving about the movement of the rotor 9 that rotates around the fixed externally toothed gear 6; (b) of each figure shows the movement of the eccentric 13 at this time; (c) of each figure shows the rotary shaft 1 at this time The movement of 〇. Further, the internal gear 9g and the external gear 6g are not shown for convenience. As shown in FIGS. 5 to 8, when the rotor 9 rotates around the fixed externally toothed gear 6, the eccentric 13 that is slidably and rotatably supported by the bearing portion of the rotor 9 is also an eccentric shaft. That is, the rotation center 10c of the rotation axis 为 is rotated in the direction of the arrow in the figure. As a result, the rotation shaft 10 to which the eccentric wheel 13 is fixed also rotates in the direction of the arrow in the figure. At this time, as shown in each figure (b), the center of the rotation of the eccentric 13 , that is, the axis 10 c of the rotating shaft 10 is offset from the center 1 3 c of the eccentric 13 by the aforementioned distance e, The rotational force applied to the eccentric 13 by the rotor 9 is formed to be efficiently transmitted to the rotation by the distance from the axial center 10c through the center 13c to the outer circumference of the eccentric rim 3 as the moment of the arm length. Axis 1 〇. Therefore, the rotating shaft 1 can be rotated in a state where the pedaling force is reduced, and the driving wheel 2 can be rotated -14 - 201109232 to advance the bicycle 1. Further, as described above, when the ratio of the external gear 6g to the internal gear ratio is 2:3, the eccentric 13 rotates three times while the rotor 9 rotates around the fixed external gear 6, so the ratio of rotation is The number of rotations of the rotary shaft 10 is increased by three times, and the high drive wheel 2 can be rotated to cause the bicycle 1 to travel at a high speed. Fig. 2 is closer to the left side than the vehicle body 8, that is, the action of the driving force transmission mechanism on the left side of the self-propelled direction is also the same as that of the right side mechanism explained in Fig. 8, but the eccentric direction and eccentricity of the first 32 The eccentric directions of the wheels 13 are different by 180. Therefore, the pedals 4 and the arms 52 are used to pedal the pedals 4, and the crankshaft 14 and the second crankshaft 142 are further made to have the second rotor 9 2 at 180 degrees. The phase difference is rotated to utilize the double force to rotate the drive wheel 2 and to cause the bicycle to travel. Further, in the above example, the fixed externally toothed gear 6 in which the traveling direction of the bicycle 1 is the side where the drive wheels 2 are present is fixed to the vehicle body 8 by the 8a, 8b and the fixing members 7a, 7b, but the toothed gear 6 is opposed to the vehicle body 8 The method of fixing is not limited to, for example, when the bicycle 1 is provided around the drive wheel 2 and the belt 3, it can be fixed relative to the vehicle body 8 by fixing the fixed external gear 6 thereto. Fig. 9 is a partial view showing another example of the driving force transmitting mechanism. In the power transmission mechanism of this embodiment, the fixed externally toothed gear 6 is one end of the mounting support member 16. The other end of the support member 16 is a 9 g gear that rotates the crankshaft 14 to efficiently drive the vehicle 1 to the fifth to the second; L·, the wheel phase. The second crank The rotor 9 and the foot are stepped on the right side, and the support post is fixed to the outside. Example Chain cover Chain cover section Cross-sectional view Mounted on the cylinder Mounted on the bottom '15- 201109232 d bracket 11, the fixed externally toothed gear 6 is fixed relative to the body 8 of the bicycle 1. The support member 16 may also be directly attached to the vehicle body 8 without passing through the bottom bracket n. The eccentric 13 is rotatably supported by a bearing 1 2 around the support member 16. The cylindrical support member 16 is coaxial with the rotary shaft 10 so that the eccentric 13 can be rotated about the axis of the rotary shaft 1 。. Further, the shape of the support member 16 is not limited to a cylindrical shape. The support member 16 may have any shape as long as the fixed externally toothed gear 6 can be fixed relative to the vehicle body 8, and may be, for example, a cylindrical member having a triangular cross section, a quadrangular shape, a pentagon shape, a hexagonal shape, an elliptical shape, or the like, or It may be only a plurality of rod-like members for connecting and fixing the externally toothed gear 6 and the vehicle body 8 or the bottom bracket. The drive wheel 2 is mounted on the peripheral portion of the eccentric 13 by a fixture 17 such as a bolt nut. The drive wheel 2 rotates about the axis of the rotary shaft 10 as the eccentric 13 rotates. Further, in this example, the drive wheel 2 is directly mounted on the eccentric 13 , but other members that will rotate about the axis of the rotary shaft 1 安装 are mounted on the eccentric 13 and the drive wheel 2 is mounted on the other. member. A through hole 6a' passing through the through shaft 6a is provided in the center portion of the fixed externally toothed gear 6 so as to be coaxial with the rotating shaft 10. Reference numeral 18 is a convex portion provided at an end portion of the rotor 9, reference numeral 19 is an intermediate portion, reference numeral 20 is a driving plate, and reference numeral 2 1 is a fixing member for fixing the driving plate 20 to the crankshaft 14 by a convex portion. ! 8. The intermediate section i 9 and the drive plate 20 constitute an Ou Dan connection mechanism 21. The crankshaft 14 and the rotor 9 are coupled by the Olden connection mechanism 21, and the rotation of the crankshaft 14 can be transmitted to the rotor 9 via the Euler-Link 09. Fig. 10 is a cross-sectional view taken along line X-X of Fig. 9. The symbol l〇c is the axis of rotation 1 1 ’ is also the axis of the crankshaft 14 , and the symbol 1 3 c is the center of the eccentric 13 . As shown, the center 1 3 c of the eccentric 13 is offset from the axis 10 c of the axis of rotation 10 by the length indicated by e in the figure. Therefore, as in the previous example, the rotational force 'applied by the rotor 9 to the eccentric 13' is formed as the distance from the axial center 10c through the center 13c to the outer circumference of the eccentric 13 as the length of the arm. The torque is efficiently transmitted to the drive wheels 2 » Therefore, the drive wheel 2 can be rotated to reduce the pedaling force to advance the bicycle 1. Fig. 1 is a Y-Y' sectional view of Fig. 9. As shown in Fig. 1, the diameter of the internal gear 9g of the rotor 9 is larger than the external gear 6g of the fixed external gear 6, and the number of teeth of the internal gear 9g is larger than that of the external gear 6g. Therefore, the internal gear 9g and the external gear 6g are engaged at a part thereof, but are separated in other portions. In the driving force transmission mechanism of the present example, the gear ratio of the external gear 6g to the internal gear 9g, that is, the gear ratio is not particularly limited, but is preferably an integer ratio, preferably, the external gear 6g and the internal tooth. The gear ratio of the gear 9 g is 2:3. In the case where the gear ratio of the external gear 6g to the internal gear 9g is 2:3, the rotor 9 causes the internal gear 9g to mesh with the external gear 6g while rotating around the external gear 6g once. , the eccentric 1 3 will rotate three times 'to obtain the appropriate speed increase ratio. Fig. 12 is an exploded view of the Ou Dan connection mechanism 21. As shown in the figure, at the end of the rotor 9, the convex portions 18, 18 are provided at intervals of 180 degrees apart from each other, and the side of the intermediate portion 19 is at the convex portion 18, 1 The opposite positions are provided with grooves 1 9 a, -17-201109232 1 9 a at intervals of 180 degrees apart from each other. On the opposite side of the intermediate section 19, the grooves 19b, 19b' are provided in such a manner that they are spaced apart from each other by a width of 丨8, but the position is different from the groove 丨9a by 90 degrees. Further, in the position of the drive plate 20 at the positions of the grooves 19b and 19b, the projections are provided at intervals of 180 degrees apart from each other. The distance between the drive plates 20 and the grooves 19b, 19b can be made by making the rotor 9 convex. The first portion 19 and the grooves 19a and 19a of the intermediate portion 19 are fitted, and the driving plates 20 20a and 20a are fitted to the grooves 19b and 19b of the intermediate portion 19, and the group portion 18'18 and the convex portions 20a and 20a are respectively It is slidably movable in the grooves 19a, 19a, 1 9b, and 19b, and therefore, even when rotating, even toward the drive plate 20, the groove is connected! The direction of the 9a, 19a, and the direction of the connecting grooves 19b, 19b which are 90 degrees apart from each other is also moved in the direction of the convex portions 18, 18 and 20a, 20a, 19a, 19a and the grooves 19b, 19b, respectively. The center 20c of the absorbing plate 20 that moves is not moved. Since the crankshaft 14 is fixed to 2 by the member 22 so as to penetrate the center 20c of the drive plate 20, the center of the crankshaft 14 does not move. As described above, even if the crank rotor 9 is coupled by the Ou Dan connecting mechanism 21, the crankshaft 14 is rotated, and the rotor 9 is engaged with the external gear 6g while the inner tooth j is meshed with the external gear 6g. Since the crankshaft 14 does not move, the crankshaft 14 can be coaxially coupled to 1 ,, so that the structure of the driving force transmission mechanism can be obtained. Further, since the crankshaft can be coaxial with the rotating shaft 1 因此, the radial force interval 19a of the crankshaft 14 on the side opposite to the side on which the driving wheels are present is opposed to the convex portions of 20a, 18, and 8 . The convex and grooved rotor 9 and the movement, in the groove, the drive fixed drive plate is rotated by the rotation axis of 14 and the gear 9g, and can also be used for the rotor by the rotary shaft 10 through -18 - 201109232 The rotation of 9, that is, the rotation of the drive wheel 2, has the advantage of being able to exert the greatest advantage of a bicycle that pedals with both feet. Further, since the crankshaft 14 can be coaxially coupled to the rotary shaft 10, it is possible to provide the pedal-type driving force transmission mechanism of the present invention without significantly changing the drive mechanism of the conventional bicycle. Further, the convex portions 18 and 18 provided in the rotor 9 may be formed as grooves, and the grooves 19a and 19a provided in the intermediate portion 19 may be formed as convex portions, and similarly, they may be provided. The grooves 1 9b and 19b of the intermediate portion 19 are formed as convex portions, and the convex portions 20a and 20a provided in the drive plate 20 are formed as grooves. Further, one or both of the convex portions 18, 18 and 20a, 20a and the grooves 19a, 19a and 19b, 19b may be provided, for example, with a dry bearing or a flat roller bearing, or The oil-impregnated bearing is provided to improve the slidability of the convex portions 18, 18 and 20a, 20a and the grooves 19a, 19a and 19b, 19b to reduce friction. Next, the operation of the pedal-type driving force transmission mechanism of the present invention will be described with reference to Figs. 13 to 15 . In the first to third figures, (a) shows that the stepping pedal 4 rotates the crankshaft 14 and rotates the rotor 9 via the ouland connection mechanism 2 to make the rotor 9 9g and fixed. The externally toothed gear 6g of the externally toothed gear 啮合 meshes while moving about the movement of the rotor 9 that rotates around the fixed externally toothed gear 6; (b) of each figure shows the eccentric 13 and the same rotation with the eccentric 13 The movement of the drive wheel 2. As shown in Figs. 1 to 5, when the rotor 9 rotates around the fixed externally toothed gear 6, the eccentric wheel 1 3 which is supported by the bearing portion of the rotor 9 can be slidably rotated -19-201109232. The eccentric shaft, that is, the axis 1 〇c of the crankshaft 14 and the rotating shaft 10 is rotated in the direction of the arrow in the figure. As a result, the driving wheel 2 fixed to the eccentric 13 also points to the arrow in the figure. Direction rotation. At this time, as shown in each figure (b), since the center of the rotation of the eccentric 13 is the crankshaft 1 4 and the axis 1 〇c of the rotary shaft 1 是 is offset from the center 1 3 c of the eccentric 13 The aforementioned distance e is shifted, so that the rotational force applied to the eccentric 13 by the rotor 9 is formed to be from the axis! 〇 c is efficiently transmitted to the drive wheel 2 by the distance from the center 丨 3 c to the outer circumference of the eccentric 13 as the moment of the arm length. Therefore, the drive wheel 2 can be rotated in a state where the pedaling force is reduced, and the bicycle 1 can be moved. Further, as described above, when the gear ratio of the external gear 6g and the internal gear 9g is 2:3, the eccentric 13 rotates three times while the rotor 9 rotates around the fixed external gear 6 three times. The number of rotations of the rotary shaft 10 or the drive wheel 2 is three times higher than the rotation of the crankshaft 14, and the drive wheel 2 can be rotated with high efficiency, so that the bicycle can be driven at a high speed. As described above, the bicycle having the pedal-type driving force transmission mechanism of the present invention is related to the gear ratio of the external gear 6g and the internal gear 9g, but the driving wheel 2 is compared with the number of rotations of the crankshaft 14. The number of rotations is increased, so that the diameter of the drive wheel 2 can be reduced compared to the conventional bicycle. Conversely, the diameter of the driven wheel coupled to the drive wheel 2 can be increased, and the pedal 4 can be reduced. The force required. As described above, even if the force required for stepping on the pedal 4 is alleviated, in the bicycle of the present invention, the number of rotations of the drive wheel 2 is increased faster than the number of rotations of the crankshaft 14, so that it is possible to make the bicycle no more than a conventional bicycle. Low speed line -20- 201109232 Advantages. Incidentally, the diameter of the drive wheel 2 is reduced. When the drive wheel 2 is a sprocket, the diameter is reduced to reduce the number of teeth; the diameter of the driven wheel is increased, and the driven wheel is a sprocket. Increase the diameter to increase the number of teeth. [Industrial Applicability] According to the bicycle equipped with the pedal-type driving force transmission mechanism, since the bicycle can be efficiently moved with a light pedaling force, the bicycle can be easily used even by a user who has insufficient foot force. . In addition, since the transmission efficiency of the pedaling force is high, the burden on the starting and uphill sections can be reduced, and the travel can be carried out for a longer period of time and longer distances, thereby providing a bicycle use opportunity, a use range, and a user age layer. The expansion. Therefore, the present invention actually has a considerable influence on the industrial field. BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a side view showing an example of a bicycle having a pedal-type driving force transmission mechanism according to the present invention. Fig. 2 is a partial cross-sectional plan view showing the main part of the driving force transmission mechanism. Fig. 3 is a cross-sectional view taken along line X-X' of Fig. 2. Fig. 4 is a Y-Y' sectional view of Fig. 2; The fifth (a) to (c) are explanatory views of the operation of rotating the rotary shaft via the eccentric wheel by the rotation of the rotor. Fig. 6(a) to (c) are explanatory views of the operation of rotating the shaft - 21 - 201109232 by the rotation of the rotor. The seventh (a) to (c) are explanatory views of the operation of rotating the rotary shaft via the eccentric wheel by the rotation of the rotor. Figs. 8(a) to 8(c) are explanatory views of the operation of rotating the rotary shaft via the eccentric wheel by the rotation of the rotor. Fig. 9 is a partial cross-sectional plan view showing another example of a driving force transmission mechanism for a bicycle equipped with a pedal-type driving force transmission mechanism according to the present invention. Fig. 10 is a cross-sectional view taken along line X-X' of Fig. 9. Fig. 11 is a Y-Y' sectional view of Fig. 9. Figure 12 is an exploded view of the Ou Dan connection mechanism. Fig. 13 (a) and (b) are explanatory views of the operation of rotating the drive shaft via the eccentric wheel by the rotation of the rotor. Fig. 14 (a) and (b) are explanatory views of the operation of rotating the drive shaft via the eccentric by the rotation of the rotor. Fig. 15(a)(b) is an explanatory view showing an operation of rotating the drive shaft via the eccentric by the rotation of the rotor. [Description of main components] 1 : Bicycle 2 : Drive wheel 3 : Drive belt 4 : Pedal 5 , 52 : Crank arm 6 , 62 : Fixed external gear 6 a , 6 2 a : Through hole -22- 201109232 6g, 62g : External gears 7a, 7b: fixing member 8: body 8a, 8b: support columns 9, 92: rotors 9g, 92g: internal gear 1 〇__ rotational axis l〇c: axis of rotation axis 1 1 : Bottom bracket 1 2 : Bearing 1 3, 1 3 2 : Eccentric wheel 1 3 c : Center of eccentric wheel 1 4, 1 4 2 : Crankshaft 1 5 : Fixing member 1 6 : Supporting member 1 7 : Fixing device 1 8 : convex portion 1 9 : intermediate portion 1 9 a, 1 9 b : groove 2 0 _ drive plate 2 〇 a : convex portion 2 1 : oudan connection mechanism 2 2 : fixing member e : eccentric distance -23