200417492 ⑴ .· 玖、發明說明 【發明所屬之技術領域】 本發明相關於自行車的輪轂傳動裝置，其也被稱爲內 部輪轂傳動裝置。更特別地，輪轂傳動裝置包含被致動來 選擇齒輪速率的一可移動離合器構件。 【先前技術】 內部輪轂傳動裝置一般包含固定於自行車車架的一輪 轂軸及可繞輪轂軸旋轉的一輪轂體。一行星齒輪機構容納 在輪轂體內，因而使旋轉驅動力可經由由行星齒輪機構所 界定的不同傳動路徑而連通至輪轂體。包含一離合器構件 的一離合器機構被設置用來藉著離合器構件的被選擇的軸 向移動而選擇傳動路徑，其中軸向移動係例如藉由一推桿 〇 上述類型的輪轂傳動裝置被揭示在歐洲專利申請案 E P 0 8 7 6 9 5 3中，其中設置有另外的機構來方便離合器構件 的致動。 在此傳統輪轂傳動裝置中，不論所嚙合的齒輪速率爲 何，例如高速，中速，或低速，驅動構件始終與離合器構 件嚙合。如此，當倒踏（b a c k p e d a 1 i n g )時，驅動構件的 向後旋轉始終伴隨有離合器構件的向後旋轉。另外，當高 速齒輪被選擇時’不只是離合器構件，連行星齒輪托架也 在實施倒踏時向後旋轉。如此，當離合器構件以及（在某 些情況中）行星齒輪機構的部件也向後旋轉時，反向旋轉 -6 - (2) , · (2) , ·200417492 不平順且有些笨重。 【發明內容】 因此，本發明的目的爲提供一種輪轂傳動裝置，其容 許驅動構件且因而容許傳動裝置在倒踏時有平滑且靈活的 反向運轉。另一目的爲提供一種具有內部齒輪改變機構的 輪轂傳動裝置，其中經由鏈條移位來容許額外的外部變速 〇 根據本發明，提供如申請專利範圍第1項所界定的輪 轂傳動裝置。一驅動構件被設置成爲繞一輪轂軸可旋轉地 安裝。一輪轂體也被安裝成可繞輪轂軸旋轉，其中一行星 齒輪機構被設置用來將向前的旋轉力從驅動構件經由不同 的力傳動路徑而連通至輪轂體。行星齒輪機構包含由一行 星齒輪托架支撐以繞輪轂軸旋轉的一行星齒輪，嚙合行星 齒輪的一環形齒輪，及設置在輪轂軸上的一中心齒輪。一 離合器構件被設置成可於輪轂軸的軸向移動。另外，一掣 爪體被配置在驅動構件與離合器構件之間。一第一單向離 合器被配置來將向前的旋轉驅動力從驅動構件傳輸至掣爪 體。 以此配置，驅動構件經由第一單向離合器而始終嚙合 離合器構件，以於被選擇的齒輪速率的任一個將向前的旋 轉運動傳輸至離合器構件。另一方面，當反向旋轉運動經 由倒踏而施加於驅動構件時，第一單向離合器使驅動構件 從離合器構件脫離。此係根據本發明藉著在驅動構件與離 -7 - (3)200417492 合器構件之間設置一掣爪體且第一單向離 置在掣爪體上而有利地達成。因此，驅動 滑地且靈活地運轉，因爲輪轂傳動裝置的 構件脫離。因此，可達成輪轂傳動裝置的 其幾乎與例如通常與一撥鏈器一起使用的 靈活。 在一實施例中，離合器構件在一外周 有齒或花鍵，其被配置成可與在掣爪體的 齒可滑動地嚙合。以此方式，離合器構件 的連接，不論離合器構件的軸向位置如何 在另一實施例中，第一單向離合器包 的一外周邊上的至少一掣爪，而互補的棘 件的一內周邊上。較佳地，此至少一掣爪 及彈簧偏壓，以在向前的旋轉驅動力施加 棘齒嚙合。棘齒被配置成爲在反向旋轉驅 構件時從該至少一掣爪脫離。如此，可用 掣爪體及相關聯的第一單向離合器來達成 反向旋轉。 在另一實施例中，一第二單向離合器 與行星齒輪機構的環形齒輪之間，用來只 傳輸至環形齒輪。較佳地，第二單向離合 安裝在掣爪體的一外周邊上的至少二掣爪 地被彈簧偏壓，以與形成在環形齒輪的一 棘齒嚙合。此配置容許在構造上方便地將 合器較佳地被配 構件在倒踏時平 內部組件從驅動 平滑向後運轉， 自由輪轂同樣地 邊上設置有設置 一內周邊上的鋸 保持其與掣爪體 〇 含安裝在掣爪體 齒形成在驅動構 被可樞轉地安裝 於驅動構件時與 動力施加於驅動 構造相當簡單的 驅動構件的自由 被配置在掣爪體 將向前的旋轉力 器包含可樞轉地 。這些掣爪較佳 內周邊上的互補 向前的旋轉驅動 -8 - (4) · ， (4) · ，200417492 力從驅動構件經由掣爪體傳輸至環形齒輪，而同時不將反 向旋轉驅動力傳輸至環形齒輪。 在另一實施例中，一第三單向離合器被配置在環形齒 輪與輪轂體之間，其中第三單向離合器可在第三單向離合 器嚙合輪轂體的棘齒的一動力傳動狀態與第三單向離合器 從輪轂體的棘齒脫離的一動力中斷狀態之間切換。較佳地 ，離合器構件包含一切換部份，用來根據離合器構件的軸 向位置將第三單向離合器在動力傳動狀態與動力中斷狀態 之間切換。 在另一較佳實施例中，離合器構件也與行星齒輪托架 嚙合，用來界定經由離合器構件至行星齒輪托架的傳動路 徑，以用於高速傳動路徑。較佳地，離合器構件的相反於 驅動構件的端部設置有嚙合齒，用來與位在行星齒輪托架 的一周邊上的鋸齒嚙合。 最後，在一非常較佳的實施例中，驅動構件的外周邊 可供至少一鏈輪安裝。較佳地，外周邊具有一軸向延伸部 份，以容許數個鏈輪被安裝。在此實施例中，本發明的輪 轂傳動裝置可被採用在一驅動鏈條從一鏈輪移位至另一鏈 輪以提供外部變速的組合中。並且，齒輪變速可在本發明 的輪轂傳動裝置內部進行。此種與多級鏈輪總成的組合導 致非常多用途的自行車變速設備。 本發明的另外有利點會在以下相關於圖式所進行的實 施例的敘述中顯明。 (5) . * (5) . *200417492 【實施方式】 參考圖1，圖中所示的輪轂傳動裝置的實施例具有可 固定於自行車的車架本體的後方下懸部份（drop-out，未 顯示）的輪轂軸2。驅動構件1 1繞輪轂軸2被設置，並 且被可旋轉地安裝在輪轂軸2的在一端部處的外周邊上。 輪轂體4可旋轉地安裝於輪轂軸2，並且一行星齒輪機構 5容納在輪轂體4中。一離合器控制機構2 5經由離合器 構件2 6的軸向調整而提供用來選擇動力傳動路徑的機構 〇 如圖1以及圖2及3所示，輪轂軸2爲在其中心處具 有較大直徑且在兩端部處具有較小直徑的圓筒構件。輪轂 軸2的中心設置有用來安置控制桿3的鑽孔。控制桿3經 由由一換檔控制纜線（未顯示）控制的致動器機構而在圖 ]中的右端處被啓動。控制桿3的軸向移動傳輸通過延伸 通過輪轂軸的一軸向凹槽的移位鍵7。移位鍵7與離合器 構件2 6嚙合，因而達成離合器構件2 6的軸向定位，以用 來選擇力傳動路徑。 驅動構件1 1藉著滾珠軸承總成8而被可旋轉地支提 在輪轂軸2上。輪轂體4也被安裝於滾珠軸承總成中以繞 輪轂軸2旋轉’並且包含徑向向外延伸凸緣，用來支撐固 定於自行車車輪的輻條（未顯示）。 行星趟輪機構5包含形成在輪轂軸上的中心齒輪，可 旋轉地安裝在輪轂軸2的外周邊上的行星齒輪托架52, 以及在常態下二個行星齒輪5 1 (只有一行星齒輪顯示在 -10- (6) , · (6) , ·200417492 圖1中）。行星齒輪與中心齒輪以及與一環形齒輪3 4的 內周邊咬合。另外，行星齒輪托架5 2在面向驅動構件1 ] 的一端部處設置有形成在行星齒輪托架5 2的周邊（較佳 地爲內周邊）上的鋸齒52a。鍵齒52a被設置用來與離合 器構件2 6的相應嚙合鋸齒2 6b嚙合，如以下會討論的。 再次參考圖1，第一單向離合器2 0被配置在驅動構 件11與掣爪體22之間。第一單向離合器包含安裝在掣爪 體22的外周邊上的至少一掣爪20a。一個掣爪即足以用 於旋轉力傳動，但是如果想要，可設置二或二個以上的掣 爪。掣爪20a可樞轉地安裝在掣爪體22的外周邊上，並 且被彈簧偏壓以與驅動構件1 1的內周邊上的棘齒]1 a嚙 合。棘齒1 1 a的形成方式爲使得施加於驅動構件1 1的向 前的旋轉驅動力被傳遞至掣爪體22，而當反向旋轉力在 例如倒踏時存在於驅動構件上時，掣爪2 0 a從棘齒]]a脫 如在圖1，2，及3中可看見的，掣爪體22相對於驅 動構件1 1的軸向位置對於輪轂傳動裝置的高速，常態速 率，及低速而言均維持不變。換句話說，沒有任何相對的 軸向移動發生在驅動構件1 1與掣爪體22之間。 由於此配置的結果，只有向前的旋轉驅動力被從驅動 構件1 1傳遞至輪轂傳動裝置的內部元件，而當驅動構件 反向旋轉時，沒有任何或至少大致上沒有任何反向旋轉驅 動力被傳輸。以此方式，以本發明的輪轂傳動裝置，在倒 踏時可達成極平滑且靈活的運轉情況。只有驅動構件本身 -11 - (7) , 200417492 反向運轉，而離合器構件藉著單向離合器2 0而從驅 件]1脫離。特別是在圖1所示的高速情況中，不只 合器構件從驅動構件脫離，並且與離合器構件26嚙 行星齒輪托架5 2也從驅動構件脫離。驅動構件的此 運轉在數個鏈輪於外部安裝在驅動構件上時很重要。 在此實施例中，第二單向離合器2 3如圖1中所 被配置在掣爪體2 2與環形齒輪3 4之間。第二單向離 2 3包含可樞轉地安裝在掣爪體2 2的外周邊上的至少 爪23a。掣爪23a被彈簧偏壓以與形成在環形齒輪34 周邊上的棘齒3 4 a嚙合。在此實施例中，採用二掣爪 ’而在實務上可根據情況設置四個或四個以上的掣爪 如根據要被傳遞的力。 如圖1，2，及3中可見的，環形齒輪3 4在繞軸 可旋轉地安裝之下於軸向維持固定。環形齒輪3 4從 端（圖1中的左側）處的行星齒輪5 1的位置延伸至 一端處的相鄰於驅動構件1 1的位置。在環形齒輪3 4 另一端處，設置有與行星齒輪 5 1咬合的內周邊齒。 齒輪3 4也設置有包含至少一離合器掣爪3 5 a的第三 離合器3 5，而離合器掣爪3 5 a由一螺旋彈簧偏壓於 或豎立的位置。離合器掣爪3 5 a與在輪轂體4的內周 的棘齒4 a嚙合。離合器掣爪3 5 a在環形齒輪於向前 方向旋轉時與棘齒4 a咬合。但是，在此第三單向離 中’離合器掣爪3 5 a如以下會討論的可被放置在動力 狀態或動力中斷狀態中。在動力傳動狀態中，向前的 動構 是離 合的 靈活 見的 合器 二掣 的內 23a ，例 2被 在一 在另 的該 環形 單向 站立 邊上 驅動 合器 傳動 驅動 -12 - (8) . . (8) . .200417492 旋轉從環形齒輪傳遞至掣爪3 5 a及棘齒4 a而至輪轂體4。 在動力中斷狀態中，離合器掣爪3 5 a如圖3所示被離合器 構件2 6的一切換部份2 6 c壓倒。在此動力中斷狀態中， 沒有任何向前或反向的旋轉驅動力可被傳輸至輪轂體的棘 齒4 a。 以下用三種向前速率來敘述根據此實施例的輪轂傳動 裝置的操作。但是，對於熟習此項技術者而言很明顯，驅 動構件1 1與掣爪體22之間的此單向離合器的配置可被設 置在具有任何數目的速率的輪轂傳動裝置。 圖1顯示高速傳動路徑。施加於驅動構件1 1的向前 旋轉力經由單向離合器2〇而被傳輸至掣爪體22，而掣爪 體22又將力經由鋸齒26a而傳輸至離合器構件26。離合 器構件2 6已經被離合器控制機構2 5放置於向圖1中的左 側的軸向位置。於此位置，離合器構件的嚙合鋸齒2 6 b與 在行星齒輪托架5 2上的鋸齒5 2 a嚙合。然後，旋轉從行 星齒輪托架5 2經由行星齒輪機構5而傳輸至環形齒輪3 4 ，並且隨後至處於豎立狀態（亦即於動力傳動狀態）中的 第三單向離合器35。最後，單向離合器35將向前的驅動 力傳遞至輪轂體4。 在此情況中，所輸入的旋轉的速率增加，然後根據由 中心齒輪，行星齒輪5 1，及環形齒輪3 4上的齒的數目所 決定的齒輪比輸出。在圖1所示的情況中，驅動構件11 的向前旋轉也被傳輸至第二單向離合器23，但是環形齒 輪3 4的旋轉比驅動構件1 1的旋轉快，使得沒有任何旋轉 > 13 - (9) · · (9) · ·200417492 經由第二單向離合器2 3而傳輸至環形齒輪3 4。 常態速率操作情況顯示在圖2中。離合器構件2 6藉 著離合器控制機構2 5而被定位於一中間軸向位置。來自 驅動構件1 1的向前的驅動旋轉經由單向離合器2 0而傳輸 至掣爪體22，然後經由第二單向離合器23而直接傳輸至 環形齒輪3 4。第三單向離合器3 5仍然處於動力傳動狀態 中，使得環形齒輪3 4的向前的旋轉驅動力直接傳輸至輪 轂體4。在此情況中，環形齒輪3 4的向前的旋轉驅動力 也經由行星齒輪5 1而傳輸至行星齒輪托架5 2，並且從該 處傳輸至嚙合輪轂蓋5 6的滾子5 7。輪轂蓋5 6被固定於 輪轂體4，並且作用成爲將旋轉力進一步傳輸至輪轂體4 的傳動機構。但是，行星齒輪托架5 2的旋轉速率被行星 齒輪5 1減小，使得經由滾子5 7及輪轂蓋5 6的旋轉傳動 被第三單向離合器3 5的較快的旋轉運動超程（overrun ) 〇 圖3顯示低速傳動路徑，其中離合器構件2 6此時於 驅動構件1 1的方向被軸向定位於右手側。於此位置，離 合器構件26的切換部份26c已經與離合器掣爪3Sa嚙合 ，因而將其放置於壓倒狀態中，亦即第三單向離合器3 5 處於動力中斷狀態中。驅動構件1 1的向前旋轉經由單向 離合器20而傳輸至掣爪體22，並且從該處經由第二單向 離合器2 3而傳至環形齒輪3 4。如上所述，單向離合器 3 5被壓倒’使得沒有任何旋轉於此位置處傳輸至輪轂體 。然後，環形齒輪的向前旋轉經由行星齒輪機構5而傳輸 -14 - (10) · (10) ·200417492 至行星齒輪托架52，並且從該處經由滾子57及輪轂蓋56 而傳輸至輪轂體4。環形齒輪3 4的旋轉速率被行星齒輪 5 1減小，導致低速傳動情況。 本發明的一特別有利點在於驅動構件1 1的外周邊例 如圖1所示可設置有軸向延伸部份，以容許數個鏈輪（未 _ 顯示）被固定於外周邊。如此，可例如將數個鏈輪安裝於 驅動構件1 1以及提供鏈條移位機構，此可容許藉著將鏈 條從一鏈輪移位至另一鏈輪來變速。 Φ 屆時，本發明的輪轂傳動裝置的一有利應用爲本發明 的輪轂傳動裝置與安裝於驅動構件U的多級鏈輪總成的 組合’因而形成自行車的組合式變速設備。本發明的輪轂 傳動裝置可有利地用於此種設備，因爲掣爪體22及第一 單向離合器2 0的設置容許驅動構件1 1可平滑且靈活地運 轉’特別是在反向旋轉中。在此種設備中，驅動構件I】 的平滑運轉可與在通常用於多級鏈輪總成中的自由輪（ f r e e w h e e 1 )配置中在常態下所達成者相當。 φ 【圖式簡單說明】 圖1顯不在離合器構件嚙合以選擇筒速傳動路徑之下 的本發明的輪穀傳動裝置的實施例。 圖2顯示圖1的實施例，其中離合器構件被軸向定位 成用來嚙合常態速率傳動路徑。 圖3顯示圖1的實施例，其中離合器構件被軸向定位 成用來嚙合低速傳動路徑。 -15 - (11) 4. 200417492 元件對照表 2 輪 轂 軸 j 控 制 桿 4 輪 軟 體 4 a 棘 ΪΑΛΓ 閱 5 行 星 齒 輪 機 構 7 移 位 鍵 8 滾 珠 軸 承 總 成 11 驅 動 構 件 1 1 a 棘 tAAr isg 20 第 — σα 早 向 離 合 器 20a 掣 爪 22 掣 爪 體 22a 鋸 丄匕 園 23 第 二 tn 口 早 向 離 合 器 23 a 掣 爪 25 離 合 器 控 制 機 構 26 離 合 器 構 件 26a 鋸 齒 26b 鋸 齒 回 26c 切 換 部 份 34 形 齒 輪 34a 棘 齒 3 5 第 三 單 向 離 合 器200417492 ⑴. · 玖, description of the invention [Technical field to which the invention belongs] The present invention relates to a wheel hub transmission of a bicycle, which is also referred to as an internal wheel hub transmission. More particularly, the hub transmission includes a movable clutch member that is actuated to select a gear speed. [Prior Art] The internal hub transmission generally includes a hub shaft fixed to a bicycle frame and a hub body rotatable about the hub shaft. A planetary gear mechanism is housed in the hub body, so that the rotational driving force can be communicated to the hub body via different transmission paths defined by the planetary gear mechanism. A clutch mechanism including a clutch member is provided to select a transmission path by a selected axial movement of the clutch member, wherein the axial movement is, for example, a push rod. A hub transmission of the above type is disclosed in Europe In the patent application EP 0 8 7 6 9 5 3, another mechanism is provided to facilitate the actuation of the clutch member. In this conventional hub transmission, the driving member is always engaged with the clutch member regardless of the engaged gear speed, such as high speed, medium speed, or low speed. As such, when stepping down (b a c k p d a 1 i n g), the rearward rotation of the driving member is always accompanied by the rearward rotation of the clutch member. In addition, when the high-speed gear is selected, '' is not only the clutch member, but also the planetary gear carrier is rotated backward when the downshift is performed. As such, when the clutch member and (in some cases) the components of the planetary gear mechanism are also rotated backwards, the reverse rotation -6-(2), · (2), · 200417492 is uneven and somewhat bulky. SUMMARY OF THE INVENTION Therefore, an object of the present invention is to provide a wheel hub transmission device that allows a driving member and thus allows the transmission device to have a smooth and flexible reverse operation when stepping down. Another object is to provide a hub transmission having an internal gear changing mechanism in which additional external shifting is allowed via a chain shift. According to the present invention, a hub transmission as defined in item 1 of the scope of patent application is provided. A drive member is provided to be rotatably mounted about a hub shaft. A hub body is also mounted to be rotatable about the hub shaft, and a planetary gear mechanism is provided to communicate forward rotational force from the driving member to the hub body via different force transmission paths. The planetary gear mechanism includes a planetary gear supported by a planetary gear carrier to rotate around a hub shaft, a ring gear that meshes with the planetary gear, and a sun gear provided on the hub shaft. A clutch member is provided to be axially movable with the hub shaft. In addition, a pawl body is disposed between the driving member and the clutch member. A first one-way clutch is configured to transmit forward rotational driving force from the driving member to the pawl body. With this configuration, the driving member always engages the clutch member via the first one-way clutch, so that any one of the selected gear rates transmits the forward rotational motion to the clutch member. On the other hand, when a reverse rotational motion is applied to the driving member by down-stepping, the first one-way clutch disengages the driving member from the clutch member. This is advantageously achieved according to the present invention by providing a pawl body between the drive member and the clutch member and the first unidirectional disengagement on the pawl body. As a result, the drive runs smoothly and flexibly because the components of the hub gear are disengaged. Thus, it is possible to achieve a hub transmission that is almost as flexible as it is usually used with a derailleur. In one embodiment, the clutch member has teeth or splines on an outer periphery which are configured to be slidably engaged with the teeth on the pawl body. In this way, the clutch member is connected, regardless of the axial position of the clutch member. In another embodiment, at least one pawl on an outer periphery of the first one-way clutch bag and an inner periphery of the complementary ratchet member on. Preferably, the at least one pawl and the spring are biased to apply ratchet teeth to the forward rotational driving force. The ratchet is configured to disengage from the at least one pawl when the drive member is rotated in the reverse direction. In this way, the pawl body and the associated first one-way clutch can be used to achieve reverse rotation. In another embodiment, a second one-way clutch is connected to the ring gear of the planetary gear mechanism for transmission to the ring gear only. Preferably, at least two pawls mounted on an outer periphery of the pawl body of the second one-way clutch are biased by a spring to mesh with a ratchet tooth formed on the ring gear. This configuration allows the structurally convenient assembly of the preferred components to be smoothly reversed from the drive when the pedal is depressed. The free hub is also provided with a saw on the inner periphery to hold it and the pawl. The body is mounted on the pawl body. The teeth are formed when the drive mechanism is pivotally mounted on the drive member and the power is applied to the drive structure. The drive mechanism is relatively simple. Pivotably. Complementary forward rotation drives on these pawls preferably on the inner periphery -8-(4) ·, (4) ·, 200417492 The force is transmitted from the drive member through the pawl body to the ring gear without simultaneously driving the reverse rotation The force is transmitted to the ring gear. In another embodiment, a third one-way clutch is disposed between the ring gear and the hub body, wherein the third one-way clutch may be in a power transmission state and The three one-way clutch is switched between a power interruption state in which the ratchet teeth of the hub body are disengaged. Preferably, the clutch member includes a switching portion for switching the third one-way clutch between a power transmission state and a power interruption state according to the axial position of the clutch member. In another preferred embodiment, the clutch member is also engaged with the planetary gear carrier to define a transmission path through the clutch member to the planetary gear carrier for a high speed transmission path. Preferably, the end of the clutch member opposite to the driving member is provided with meshing teeth for meshing with saw teeth located on a periphery of the planetary gear carrier. Finally, in a very preferred embodiment, the outer periphery of the drive member can be fitted with at least one sprocket. Preferably, the outer periphery has an axially extending portion to allow several sprockets to be mounted. In this embodiment, the hub transmission of the present invention may be employed in a combination in which a drive chain is shifted from one sprocket to another to provide external speed change. Moreover, gear shifting can be performed inside the hub transmission of the present invention. This combination with a multi-stage sprocket assembly results in a very versatile bicycle transmission. Further advantages of the present invention will be apparent from the following description of the embodiments performed in connection with the drawings. (5). * (5). * 200417492 [Embodiment] Referring to FIG. 1, the embodiment of the wheel transmission device shown in the figure has a rear underhang portion (drop-out, (Not shown) of the hub shaft 2. The driving member 11 is provided around the hub shaft 2 and is rotatably mounted on the outer periphery of the hub shaft 2 at one end portion. The hub body 4 is rotatably mounted on the hub shaft 2, and a planetary gear mechanism 5 is housed in the hub body 4. A clutch control mechanism 25 provides a mechanism for selecting a power transmission path through an axial adjustment of the clutch member 26. As shown in FIGS. 1 and 2 and 3, the hub shaft 2 has a larger diameter at its center and A cylindrical member having a smaller diameter at both end portions. The center of the hub shaft 2 is provided with a drilled hole for arranging the control rod 3. The control lever 3 is activated at the right end in the figure by an actuator mechanism controlled by a shift control cable (not shown). The axial movement of the control lever 3 is transmitted through a shift key 7 extending through an axial groove of the hub shaft. The shift key 7 is engaged with the clutch member 26, thereby achieving the axial positioning of the clutch member 26 to select a force transmission path. The driving member 11 is rotatably supported on the hub shaft 2 by a ball bearing assembly 8. The hub body 4 is also mounted in a ball bearing assembly to rotate around the hub shaft 2 and includes a radially outwardly extending flange for supporting a spoke (not shown) fixed to a bicycle wheel. The planetary wheel mechanism 5 includes a sun gear formed on the hub shaft, a planetary gear carrier 52 rotatably mounted on the outer periphery of the hub shaft 2, and two planetary gears 5 1 (only one planetary gear is shown in the normal state). (In -10- (6), · (6), · 200417492 in Figure 1). The planetary gear meshes with the sun gear and the inner periphery of a ring gear 34. In addition, the planetary gear carrier 52 is provided with a saw tooth 52a formed at a periphery (preferably an inner periphery) of the planetary gear carrier 52 at one end portion facing the driving member 1]. The key teeth 52a are provided to mesh with the corresponding meshing teeth 26b of the clutch member 26, as will be discussed below. Referring again to FIG. 1, the first one-way clutch 20 is disposed between the driving member 11 and the pawl body 22. The first one-way clutch includes at least one pawl 20a mounted on the outer periphery of the pawl body 22. One pawl is sufficient for rotational force transmission, but two or more pawls can be provided if desired. The pawl 20a is pivotally mounted on the outer periphery of the pawl body 22 and is biased by a spring to engage with ratchet teeth 1a on the inner periphery of the driving member 11. The ratchet teeth 1 1 a are formed in such a manner that a forward rotational driving force applied to the driving member 11 is transmitted to the pawl body 22, and when a reverse rotational force is present on the driving member when, for example, the pedal is depressed, The pawl 20 a is from the ratchet teeth]] a. As can be seen in FIGS. 1, 2 and 3, the axial position of the pawl body 22 with respect to the drive member 11 is high-speed, normal speed for the hub transmission, and In terms of low speed, they remain unchanged. In other words, no relative axial movement occurs between the driving member 11 and the pawl body 22. As a result of this configuration, only forward rotational driving force is transmitted from the driving member 11 to the internal elements of the hub transmission, and when the driving member rotates in the reverse direction, there is no or at least substantially no reverse rotational driving force Be transmitted. In this way, with the wheel hub transmission of the present invention, extremely smooth and flexible running conditions can be achieved when pedaling down. Only the drive member itself -11-(7), 200417492 operates in reverse, and the clutch member is disengaged from the drive member 1 by the one-way clutch 20. Particularly in the high-speed case shown in FIG. 1, not only the clutch member is disengaged from the driving member, but also the planetary gear carrier 52 which is engaged with the clutch member 26 is disengaged from the driving member. This operation of the drive member is important when several sprockets are externally mounted on the drive member. In this embodiment, the second one-way clutch 23 is disposed between the pawl body 22 and the ring gear 34 as shown in FIG. The second one-way separation 23 includes at least claws 23a pivotably mounted on the outer periphery of the pawl body 22. The pawl 23a is spring-biased to engage the ratchet teeth 3 4 a formed on the periphery of the ring gear 34. In this embodiment, two pawls are used, and in practice, four or more pawls can be provided according to the situation, such as according to the force to be transmitted. As can be seen in Figs. 1, 2, and 3, the ring gear 34 is axially fixed while being rotatably mounted around the shaft. The ring gear 34 extends from the position of the planetary gear 51 at the end (left side in FIG. 1) to the position adjacent to the driving member 11 at one end. At the other end of the ring gear 3 4, inner peripheral teeth that mesh with the planetary gear 51 are provided. The gear 34 is also provided with a third clutch 35 including at least one clutch pawl 35a, and the clutch pawl 35a is biased to the or upright position by a coil spring. The clutch pawl 3 5 a is engaged with a ratchet tooth 4 a on the inner periphery of the hub body 4. The clutch pawl 3 5 a meshes with the ratchet tooth 4 a when the ring gear rotates in the forward direction. However, the third one-way clutch ' clutch pawl 5a may be placed in a power state or a power interruption state as discussed below. In the power transmission state, the forward moving mechanism is the inner 23a of the clutch's flexible see-through clutch. Example 2 is driven by a clutch drive drive on another ring-shaped one-way standing -12-(8 (8) .. 200417492 The rotation is transmitted from the ring gear to the pawl 3 5 a and the ratchet 4 a to the hub body 4. In the power interruption state, the clutch pawl 3 5 a is overwhelmed by a switching portion 2 6 c of the clutch member 26 as shown in FIG. 3. In this power interruption state, no forward or reverse rotational driving force can be transmitted to the ratchet teeth 4 a of the hub body. The operation of the hub transmission according to this embodiment will be described below using three forward speeds. However, it is obvious to those skilled in the art that the configuration of this one-way clutch between the driving member 11 and the pawl body 22 can be set to a hub transmission having any number of speeds. Figure 1 shows the high-speed drive path. The forward rotational force applied to the driving member 11 is transmitted to the pawl body 22 via the one-way clutch 20, and the pawl body 22 transmits the force to the clutch member 26 via the saw tooth 26a. The clutch member 26 has been placed in the axial position to the left in FIG. 1 by the clutch control mechanism 25. In this position, the meshing teeth 2 6 b of the clutch member mesh with the teeth 5 2 a on the planetary gear carrier 5 2. Then, the rotation is transmitted from the planetary gear carrier 52 through the planetary gear mechanism 5 to the ring gear 3 4 and then to the third one-way clutch 35 in an upright state (i.e., a power transmission state). Finally, the one-way clutch 35 transmits a forward driving force to the hub body 4. In this case, the input rotation rate is increased, and then outputted according to a gear ratio determined by the number of teeth on the sun gear, the planetary gear 51, and the ring gear 34. In the case shown in FIG. 1, the forward rotation of the driving member 11 is also transmitted to the second one-way clutch 23, but the rotation of the ring gear 34 is faster than that of the driving member 11 so that there is no rotation> 13 -(9) · · (9) · · 200417492 is transmitted to the ring gear 3 4 via the second one-way clutch 2 3. Normal rate operation is shown in Figure 2. The clutch member 26 is positioned at an intermediate axial position by the clutch control mechanism 25. The forward driving rotation from the driving member 11 is transmitted to the pawl body 22 via the one-way clutch 20, and then directly transmitted to the ring gear 34 via the second one-way clutch 23. The third one-way clutch 35 is still in a power transmission state, so that the forward rotational driving force of the ring gear 34 is directly transmitted to the hub body 4. In this case, the forward rotational driving force of the ring gear 34 is also transmitted to the planetary gear carrier 5 2 via the planetary gear 51, and from there to the roller 57 of the meshing hub cover 56. The hub cover 56 is fixed to the hub body 4 and functions as a transmission mechanism that further transmits the rotational force to the hub body 4. However, the rotation speed of the planetary gear carrier 5 2 is reduced by the planetary gear 51 so that the rotational transmission via the roller 57 and the hub cover 56 is overrun by the faster rotational movement of the third one-way clutch 35. overrun) 〇 FIG. 3 shows a low-speed transmission path, in which the clutch member 26 is axially positioned on the right-hand side in the direction of the driving member 11 at this time. In this position, the switching portion 26c of the clutch member 26 has been engaged with the clutch pawl 3Sa, so it is placed in an overwhelming state, that is, the third one-way clutch 35 is in a power interruption state. The forward rotation of the drive member 11 is transmitted to the pawl body 22 via the one-way clutch 20, and from there to the ring gear 34 through the second one-way clutch 23. As described above, the one-way clutch 35 is overwhelmed 'so that no rotation is transmitted to the hub body at this position. Then, the forward rotation of the ring gear is transmitted via the planetary gear mechanism 5-14-(10) · (10) · 200417492 to the planetary gear carrier 52 and from there to the hub via the roller 57 and the hub cover 56. Body 4. The rotation speed of the ring gear 34 is reduced by the planetary gear 51, resulting in a low-speed transmission situation. A particularly advantageous point of the present invention is the outer peripheral example of the driving member 11 as shown in FIG. 1. An axially extending portion may be provided to allow several sprocket wheels (not shown) to be fixed to the outer peripheral. In this way, for example, a plurality of sprocket wheels can be mounted on the driving member 11 and a chain shift mechanism can be provided, which allows shifting by shifting the chain from one sprocket to another. Φ At that time, an advantageous application of the in-wheel transmission device of the present invention is the combination of the in-wheel transmission device of the present invention and a multi-stage sprocket assembly mounted on the driving member U ', thus forming a combined transmission device for bicycles. The in-wheel transmission of the present invention can be advantageously used in such a device because the arrangement of the pawl body 22 and the first one-way clutch 20 allows the driving member 11 to be smoothly and flexibly operated ', especially in the reverse rotation. In such a device, the smooth operation of the driving member I] can be comparable to what is normally achieved in a free wheel (f r e w h e e 1) configuration commonly used in multi-stage sprocket assemblies. φ [Brief Description of the Drawings] Fig. 1 shows an embodiment of the wheel valley transmission device of the present invention which is not under the clutch member engagement to select the barrel speed transmission path. Fig. 2 shows the embodiment of Fig. 1 with the clutch member axially positioned to engage a normal rate drive path. Fig. 3 shows the embodiment of Fig. 1 with the clutch member axially positioned to engage a low speed drive path. -15-(11) 4. 200417492 Component comparison table 2 Hub shaft j Control lever 4 Wheel software 4 a Spindle ΑΛΓ See 5 Planetary gear mechanism 7 Shift key 8 Ball bearing assembly 11 Drive member 1 1 a Spindle tAAr isg 20 No. — Σα Early clutch 20a Pawl 22 Pawl body 22a Saw dagger 23 Second tn port early clutch 23 a Pawl 25 Clutch control mechanism 26 Clutch member 26a Saw tooth 26b Saw tooth return 26c Switching part 34 Gear 34a Ratchet Tooth 3 5 third one-way clutch
-16 - (12) (12)200417492 3 5a 離合器掣爪 5 1 行星齒輪 5 2 行星齒輪托架 5 2a 鋸齒 56 輪轂蓋 5 7 滾子-16-(12) (12) 200417492 3 5a Clutch pawl 5 1 Planetary gear 5 2 Planetary gear carrier 5 2a Serration 56 Hub cover 5 7 Roller
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