1254013 (1) 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 ΕΡ0 8 7695 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) 1254013 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) 1254013 合器構件之間設置一掣爪體且第一單向離合器較佳地被配 置在掣爪體上而有利地達成。因此，驅動構件在倒踏時平 滑地且靈活地運轉，因爲輪轂傳動裝置的內部組件從驅動 構件脫離。因此，可達成輪轂傳動裝置的平滑向後運轉， 其幾乎與例如通常與一撥鏈器一起使用的自由輪轂同樣地 靈活。 在一實施例中，離合器構件在一外周邊上設置有設置 有齒或花鍵，其被配置成可與在掣爪體的一內周邊上的鋸 齒可滑動地嚙合。以此方式，離合器構件保持其與掣爪體 的連接，不論離合器構件的軸向位置如何。 在另一實施例中，第一單向離合器包含安裝在掣爪體 的一外周邊上的至少一掣爪，而互補的棘齒形成在驅動構 件的一內周邊上。較佳地，此至少一掣爪被可樞轉地安裝 及彈簧偏壓，以在向前的旋轉驅動力施加於驅動構件時與 棘齒嚙合。棘齒被配置成爲在反向旋轉驅動力施加於驅動 構件時從該至少一掣爪脫離。如此，可用構造相當簡單的 掣爪體及相關聯的第一單向離合器來達成驅動構件的自由 反向旋轉。 在另一實施例中，一第二單向離合器被配置在掣爪體 與行星齒輪機構的環形齒輪之間，用來只將向前的旋轉力 傳輸至環形齒輪。較佳地，第二單向離合器包含可樞轉地 安裝在掣爪體的一外周邊上的至少二掣爪。這些掣爪較佳 地被彈簧偏壓，以與形成在環形齒輪的一內周邊上的互補 棘齒嚙合。此配置容許在構造上方便地將向前的旋轉驅動 -8 - (4) 1254013 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) 1254013 【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 1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26嚙合，因而達成離合器構件26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而被可旋轉地支撐 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（未顯不）。 行星齒輪機構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5 2， 以及在常態下三個行星齒輪5 1 (只有一行星齒輪顯示在 -10- (6) 1254013 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 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。鋸齒52a被設置用來與離合 器構件26的相應嚙合鋸齒26b嚙合，如以下會討論的。 再次參考圖1，第一單向離合器20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 1 a嚙 合。棘齒11 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20a從棘齒1 1 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2 2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) 1254013 反向運轉，而離合器構件藉著單向離合器2 〇而從驅動構 件1 1脫離。特別是在圖1所示的高速情況中，不只是離 合器構件從驅動構件脫離，並且與離合器構件26嚙合的 行星齒輪托架5 2也從驅動構件脫離。驅動構件的此靈活 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中所見的 被配置在掣爪體22與環形齒輪3 4之間。第二單向離合器 23包含可樞轉地安裝在掣爪體22的外周邊上的至少二掣 爪23a。掣爪23a被彈簧偏壓以與形成在環形齒輪34的內 周邊上的棘齒34a嚙合。在此實施例中，採用二掣爪23a ，而在實務上可根據情況設置四個或四個以上的掣爪，例 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2被 可旋轉地安裝之下於軸向維持固定。環形齒輪3 4從在一 端（圖1中的左側）處的行星齒輪5 1的位置延伸至在另 一端處的相鄰於驅動構件1 1的位置。在環形齒輪3 4的該 另一端處，設置有與行星齒輪5 1咬合的內周邊齒。環形 齒輪34也設置有包含至少一離合器掣爪35a的第三單向 離合器35，而離合器掣爪35a由一螺旋彈簧偏壓於站立 或豎立的位置。離合器掣爪35a與在輪轂體4的內周邊上 的棘齒4a嚙合。離合器掣爪3 Sa在環形齒輪於向前驅動 方向旋轉時與棘齒4a咬合。但是，在此第三單向離合器 中’離合器掣爪3 5 a如以下會討論的可被放置在動力傳動 狀態或動力中斷狀態中。在動力傳動狀態中，向前的驅動 -12 - (8) 1254013 旋轉從環形齒輪傳遞至掣爪3 5 a及棘齒4 a而至輪穀體L 在動力中斷狀態中，離合器掣爪3 5 a如圖3所示被離合 構件26的一切換部份26c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 齒4a。 以下用三種向前速率來敘述根據此實施例的輪轂傳 裝置的操作。但是，對於熟習此項技術者而言很明顯， 動構件1 1與掣爪體22之間的此單向離合器的配置可被 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 旋轉力經由單向離合器20而被傳輸至掣爪體22，而掣 體2 2又將力經由鋸齒2 6 a而傳輸至離合器構件2 6。離 器構件26已經被離合器控制機構25放置於向圖1中的 側的軸向位置。於此位置，離合器構件的嚙合鋸齒26b 在行星齒輪托架52上的鋸齒52a嚙合。然後，旋轉從 星齒輪托架5 2經由行星齒輪機構5而傳輸至環形齒輪 ，並且隨後至處於豎立狀態（亦即於動力傳動狀態）中 第三單向離合器3 5。最後，單向離合器3 5將向前的驅 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 中心齒輪，行星齒輪5 1，及環形齒輪3 4上的齒的數目 決定的齒輪比輸出。在圖1所示的情況中，驅動構件 的向前旋轉也被傳輸至第二單向離合器23，但是環形 輪3 4的旋轉比驅動構件1 1的旋轉快，使得沒有任何旋 器 5 棘 動 驅 設 刖 爪 合 左 與 行 34 的 動 由 所 11 齒 轉 -13 - (9) 1254013 經由第二單向離合器23而傳輸至環形齒輪34。 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35的較快的旋轉運動超程（〇verrun) 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35a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n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23而傳輸至環形齒輪34。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) 1254013 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。 · 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1 1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20的設置容許驅動構件11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11 的平滑運轉可與在通常用於多級鏈輪總成中的自由輪（ freewheel)配置中在常態下所達成者相當。 · 【圖式簡單說明】 圖1顯示在離合器構件嚙合以選擇高速傳動路徑之下 ^ 的本發明的輪轂傳動裝置的實施例。 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)1254013 兀件對照表 2 輪 奉 軟 軸 3 控 制 桿 4 輪 轂 體 4 a 棘 Τααγ 网 5 行 星 TaaF 固 ΐ八 m 機 構 7 移 位 鍵 8 滾 珠 軸 承 總 成 11 』驅 動 構 件 11a 棘 齒 20 第 一 單 向 離 合 器 20a 掣 爪 22 掣 爪 體 22a 鋸 ΪΑΑΓ 回 23 第 一 口口 早 向 離 合 器 23 a 掣 爪 25 離 合 器 控 制 機 構 26 離 合 器 構 件 2 6a 鋸 ΐΑΑΤ 回 26b 鋸 Γ^ΑΓ 固 2 6c 切 換 部 份 34 形 齒 W 卑冊 3 4a 棘 ΐ^ΑΓ 3 5 第 三 單 向 離 合 器1254013 (1) Description of the Invention [Technical Field] The present invention relates to a hub transmission of a bicycle, which is also referred to as an internal hub transmission. More particularly, the hub transmission includes a moveable clutch member that is actuated to select a gear ratio. [Prior Art] The internal hub transmission generally includes a hub axle fixed to the bicycle frame and a hub body rotatable about the hub axle. A planetary gear mechanism is housed within the hub such that the rotational drive force is communicated to the hub body via different transmission paths defined by the planetary gear mechanism. A clutch mechanism including a clutch member is provided for selecting a transmission path by selective axial movement of the clutch member, wherein the axial movement is revealed in Europe, for example, by a push rod 〇 a hub transmission of the type described above Patent application ΕΡ 0 8 7695 3, in which an additional mechanism is provided to facilitate actuation of the clutch member. In this conventional hub transmission, the drive member always engages the clutch member regardless of the engaged gear speed, such as high speed, medium speed, or low speed. Thus, when stepping (b a c k p e d a 1 i n g ), the backward rotation of the drive member is always accompanied by the backward rotation of the clutch member. In addition, when the high speed gear is selected, not only the clutch member but also the planetary gear carrier is rotated backward when the reverse step is performed. Thus, when the clutch member and, in some cases, the components of the planetary gear mechanism are also rotated backwards, the reverse rotation -6 - (2) 1254013 is not smooth and somewhat cumbersome. SUMMARY OF THE INVENTION Accordingly, it is an object of the present invention to provide a hub transmission that allows for a drive member and thus allows for smooth and flexible reverse operation of the transmission when pedaling. Another object is to provide a hub transmission having an internal gear changing mechanism in which additional external shifting is permitted via chain shifting. According to the present invention, a hub transmission as defined in claim 1 is provided. A drive member is arranged to be rotatably mounted about a hub axle. A hub body is also mounted for rotation about the hub axle, wherein a planetary gear mechanism is provided for communicating forward rotational forces from the drive member to the hub body via different force transmission paths. The planetary gear mechanism includes a planetary gear supported by the planetary carrier to rotate about the hub axle, a ring gear that meshes with the planetary gear, and a sun gear disposed on the hub axle. A clutch member is arranged to be movable in the axial direction of the hub axle. Further, a pawl body is disposed between the drive member and the clutch member. A first one-way clutch is configured to transmit the forward rotational driving force from the drive member to the pawl body. With this configuration, the drive member always engages the clutch member via the first one-way clutch to transmit the forward rotational motion to the clutch member at any of the selected gear speeds. On the other hand, when the reverse rotational motion is applied to the drive member by stepping, the first one-way clutch disengages the drive member from the clutch member. According to the invention, this is advantageously achieved by providing a pawl body between the drive member and the _ 7 - (3) 1254013 combiner member and the first one-way clutch is preferably disposed on the jaw body. Therefore, the drive member operates smoothly and flexibly when stepping down because the internal components of the hub transmission are disengaged from the drive member. Thus, a smooth rearward operation of the hub transmission can be achieved, which is almost as flexible as, for example, a free hub that is typically used with a derailleur. In one embodiment, the clutch member is provided on an outer periphery with teeth or splines that are configured to slidably engage serrations on an inner periphery of the jaw body. In this manner, the clutch member maintains its connection to the jaw body regardless of the axial position of the clutch member. In another embodiment, the first one-way clutch includes at least one pawl mounted on an outer periphery of the pawl body, and complementary ratchet teeth are formed on an inner periphery of the drive member. Preferably, the at least one pawl is pivotally mounted and spring biased to engage the ratchet when a forward rotational drive force is applied to the drive member. The ratchet is configured to be disengaged from the at least one pawl when a reverse rotational driving force is applied to the driving member. Thus, freely reverse rotation of the drive member can be achieved with a relatively simple jaw member and associated first one-way clutch. In another embodiment, a second one-way clutch is disposed between the pawl body and the ring gear of the planetary gear mechanism for transmitting only the forward rotational force to the ring gear. Preferably, the second one-way clutch includes at least two jaws pivotally mounted on an outer periphery of the jaw body. The jaws are preferably spring biased to engage complementary ratchet teeth formed on an inner periphery of the ring gear. This configuration allows the construction of the forward rotary drive -8 - (4) 1254013 force to be transmitted from the drive member to the ring gear via the pawl body while transmitting the reverse rotational drive force 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 engages a ratcheting power transmission state of the hub body at the third one-way clutch The three one-way clutch switches 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 the power transmission state and the power interruption state in accordance with the axial position of the clutch member. In another preferred embodiment, the clutch member is also meshed with the planet carrier for defining a transmission path to the planet carrier via the clutch member for use in the high speed transmission path. Preferably, the end of the clutch member opposite the drive member is provided with engaging teeth for engaging the serrations on a periphery of the planet carrier. Finally, in a very preferred embodiment, the outer periphery of the drive member is mountable by at least one sprocket. Preferably, the outer periphery has an axially extending portion to permit installation of a plurality of sprockets. In this embodiment, the hub transmission of the present invention can be employed in a combination in which a drive chain is displaced from one sprocket to another to provide external shifting. Also, 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 shifting device. Additional advantages of the invention will be apparent from the following description of the embodiments of the drawings. (5) 1254013 [Embodiment] Referring to Fig. 1, an embodiment of a hub transmission shown in the drawings has a hub shaft 2 that can be fixed to a rear drop-out (not shown) of a frame body of a bicycle. . The drive member 11 is disposed around the hub axle 2 and rotatably mounted on the outer periphery of the hub axle 2 at one end. The hub body 4 is rotatably mounted to the hub axle 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 via axial adjustment of the clutch member 26, as shown in Figures 1 and 2 and 3, the hub axle 2 having a larger diameter at its center and A cylindrical member having a smaller diameter at both ends. The center of the hub shaft 2 is provided with a bore for arranging the control rod 3. The lever 3 is activated at the right end in Fig. 1 via an actuator mechanism controlled by a shift control cable (not shown). The axial movement of the lever 3 is transmitted through a shift key 7 that extends through an axial groove of the hub axle. The shift key 7 engages the clutch member 26, thereby achieving axial positioning of the clutch member 26 for use in selecting the force transmission path. The drive member 1 1 is rotatably supported on the hub axle 2 by the ball bearing assembly 8. The hub body 4 is also mounted in the ball bearing assembly for rotation about the hub axle 2 and includes a radially outwardly extending flange for supporting spokes (not shown) that are secured to the bicycle wheel. The planetary gear mechanism 5 includes a sun gear formed on a hub axle, a planetary gear carrier 52 that is rotatably mounted on an outer periphery of the hub axle 2, and three planetary gears 5 1 in a normal state (only one planetary gear display In -10- (6) 1254013 Figure 1). The planet gear meshes with the sun gear and with the inner periphery of a ring gear 34. Further, the planetary gear carrier 52 is provided at one end portion facing the drive member 1 1 with serrations 52a formed on the periphery (preferably the inner periphery) of the planetary carrier 55. The serrations 52a are configured to engage corresponding engagement serrations 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 drive member 11 and the pawl body 22. The first one-way clutch includes at least one pawl 20a mounted on an outer periphery of the pawl body 22. One paw is sufficient for the rotational force transmission, but two or more jaws can be provided if desired. The pawl 20a is pivotally mounted on the outer periphery of the pawl body 22 and is spring biased to engage the ratchet 11a on the inner periphery of the drive member 11. The ratchet 11a is 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 the reverse rotational force is present on the driving member, for example, when the pedal is stepped, the pawl 20a is removed from the ratchet 1 1 a as can be seen in Figures 1, 2, and 3, the axial position of the pawl body 22 relative to the drive member 11 for the high speed, normal speed, and low speed of the hub transmission Both remain unchanged. In other words, no relative axial movement occurs between the drive member 11 and the jaw body 22. As a result of this configuration, only the forward rotational driving force is transmitted from the drive member 11 to the internal components of the hub transmission, and when the drive member is rotated in the reverse direction, there is no or at least substantially no reverse rotational driving force. Being transmitted. In this way, with the hub transmission of the present invention, extremely smooth and flexible operation can be achieved when stepping down. Only the drive member itself -11 - (7) 1254013 operates in the reverse direction, and the clutch member is disengaged from the drive member 11 by the one-way clutch 2 。. 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 engaged with the clutch member 26 is also detached from the driving member. This flexible operation of the drive member is important when several sprocket wheels are externally mounted on the drive member. In this embodiment, the second one-way clutch 2 3 is disposed between the pawl body 22 and the ring gear 34 as seen in FIG. The second one-way clutch 23 includes at least two jaws 23a pivotally mounted on the outer periphery of the jaw body 22. The pawl 23a is spring biased to mesh with the ratchet teeth 34a formed on the inner periphery of the ring gear 34. In this embodiment, the two jaws 23a are employed, and in practice four or more jaws can be provided depending on the situation, for example, depending on the force to be transmitted. As can be seen in Figures 1, 2, and 3, the ring gear 34 is maintained axially fixed about the axis 2 being rotatably mounted. The ring gear 34 extends from the position of the planetary gear 51 at one end (left side in Fig. 1) to the position adjacent to the driving member 11 at the other end. At the other end of the ring gear 34, inner peripheral teeth that mesh with the planetary gears 51 are disposed. The ring gear 34 is also provided with a third one-way clutch 35 including at least one clutch pawl 35a, and the clutch pawl 35a is biased by a coil spring in a standing or upright position. The clutch pawl 35a meshes with the ratchet 4a on the inner periphery of the hub body 4. The clutch pawl 3 Sa engages with the ratchet 4a when the ring gear rotates in the forward drive direction. However, in this third one-way clutch, the 'clutch pawl 35 a can be placed in the power transmission state or the power interruption state as will be discussed below. In the power transmission state, the forward drive -12 - (8) 1254013 is transmitted from the ring gear to the pawl 35 a and the ratchet 4 a until the wheel body L is in the power interruption state, the clutch pawl 3 5 A is overwhelmed by a switching portion 26c of the clutch member 26 as shown in FIG. In this power interruption state, no forward or reverse rotational driving force can be transmitted to the teeth 4a of the hub body. The operation of the hub transmission device according to this embodiment will be described below using three forward rates. However, it will be apparent to those skilled in the art that the configuration of the one-way clutch between the movable member 11 and the pawl body 22 can be placed in a hub transmission having any number of rates. Figure 1 shows the high speed transmission path. The rotational force applied to the drive member 11 is transmitted to the pawl body 22 via the one-way clutch 20, and the body 2 2 transmits the force to the clutch member 26 via the saw teeth 26a. The disconnector member 26 has been placed in the axial position to the side in Fig. 1 by the clutch control mechanism 25. In this position, the engaging serrations 26b of the clutch members mesh with the serrations 52a on the planet carrier 52. Then, the rotation is transmitted from the star gear carrier 52 to the ring gear via the planetary gear mechanism 5, and then to the third one-way clutch 35 in the erected state (i.e., in the power transmission state). Finally, the one-way clutch 35 transmits the forward drive to the hub body 4. In this case, the rate of the input rotation is increased, and then the gear ratio is determined according to 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 drive member is also transmitted to the second one-way clutch 23, but the rotation of the annular wheel 34 is faster than the rotation of the drive member 11 so that no spinner 5 is turbulent The driving of the left and the rows 34 of the pawl is transmitted to the ring gear 34 via the second one-way clutch 23 by the 11-tooth rotation -13 - (9) 1254013. The normal rate operation is shown in Figure 2. The clutch member 26 is positioned in an intermediate axial position by the clutch control mechanism 25. The forward drive rotation from the drive 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 the 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 carrier 55 via the planetary gear 51, and from there to the roller 57 of the engaging hub cover 56. The hub cover 56 is fixed to the hub body 4 and functions as a transmission mechanism for further transmitting the rotational force to the hub body 4. However, the rate of rotation of the planet gear carrier 52 is reduced by the planet gears 51, so that the rotational transmission via the rollers 57 and the hub cover 56 is overtraveled by the faster one of the third one-way clutches 35 (〇 Verrun 3 shows a low speed transmission path in which the clutch member 26 is now axially positioned on the right hand side in the direction of the drive member 11. In this position, the switching portion 26c of the clutch member 26 has engaged with the clutch pawl 35a' thus placing it in the depressed state, i.e., the third one-way clutch 35 is in the power interruption state. The forward rotation of the drive member n is transmitted to the pawl body 22 via the one-way clutch 20, and from there to the ring gear 34 via 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. The forward rotation of the 'ring gear is then transmitted via the planetary gear mechanism 5 -14 - (10) 1254013 to the planet carrier 52 and from there to the hub body 4 via the roller 57 and the hub cover 56. The rate of rotation of the ring gear 34 is reduced by the planet gears 51, resulting in a low speed transmission condition. A particularly advantageous aspect of the present invention is that the outer periphery of the drive member 11 can be provided with an axially extending portion as shown in Figure 1 to allow a plurality of sprockets (not shown) to be secured to the outer periphery. Thus, for example, a plurality of sprockets can be mounted to the drive member 1 1 and a chain shifting mechanism can be provided which allows for shifting by shifting the chain from one sprocket to the other. At that time, an advantageous application of the hub transmission of the present invention is a combination of the hub transmission of the present invention and the multi-stage sprocket assembly mounted to the drive member 1 1 thus forming a combined shifting device for the bicycle. The hub transmission of the present invention can be advantageously used in such a device because the arrangement of the jaw body 22 and the first one-way clutch 20 allows the drive member 11 to be smoothly and flexibly operated, particularly in reverse rotation. In such an apparatus, the smooth operation of the drive member 11 can be comparable to that achieved under normal conditions in a freewheel configuration typically used in multi-stage sprocket assemblies. BRIEF DESCRIPTION OF THE DRAWINGS Figure 1 shows an embodiment of a hub transmission of the present invention with the clutch members engaged to select a high speed transmission path. Figure 2 shows the embodiment of Figure 1 in which the clutch member is axially positioned for engaging a normal rate transmission path. Figure 3 shows the embodiment of Figure 1 in which the clutch member is axially positioned for engaging the low speed transmission path. -15 - (11)1254013 对照 对照 2 软 软 软 软 软 软 软 软 软 软 软 软 软 软 软 软 软 软 软 软 软 软 软 软 软 软 软 软 软 软 软 软 软 软 软 软 软 软 软 软 软 软 软 软 软 软 软 软 软 软 软 软 软 软 软 控制 控制 m m Tooth 20 first one-way clutch 20a 掣 claw 22 掣 claw body 22a saw ΪΑΑΓ back 23 first port early clutch 23 a 掣 claw 25 clutch control mechanism 26 clutch member 2 6a saw ΐΑΑΤ back 26b saw Γ ^ ΑΓ solid 2 6c Switching part 34-shaped tooth W 卑册3 4a ΐΐ^ΑΓ 3 5 third one-way clutch
-16 - (12)1254013 3 5a 離合器掣爪 5 1 行星齒輪 52 行星齒輪托架 52a 鋸齒 5 6 輪轂蓋 57 滾子-16 - (12)1254013 3 5a Clutch pawl 5 1 Planetary gear 52 Planetary gear carrier 52a Serrated 5 6 Hub cap 57 Roller
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