201219260 六、發明說明： 【發明所屬之技術領域】 本發明是.__踩纽__妓，尤於 適於裝置在自行車上，且可藉由腳踏驅動曲柄反轉^行 複數段樓位之變速操作的一種倒踩多段變棺内變速器。 【先前技術】 隨著人們對於環保、脑、健身以及天然#源耗竭的 意識囉起’已有越來越多的人們以兼具無污染、不消耗天 然資源以及運動健身優點的自行車來代步，以取代耗能又 造成污染的汽機車。 目别市售的可變速自行車’大多是採用外變速器之撥 桿來撥動鏈條嚙合於不同尺寸的齒盤，來達到變 雖然，曾有人揭露-種裝設於自行車輪轂之内變速器，其 可藉由腳踏驅動齒盤反轉來進行高、低速變檔操作；然 而’由於此種習知的内變速器機構通常具有只能做兩段^ 變速，或是有機構複雜、成本高、變槽操作之反應不夠迅 速破實等缺失，而有進一步改善之空間。 【發明内容】 本發明的第一目的是在於提供一種倒踩多段變檔内 變速器’可藉由腳踏驅動曲柄反轉來進行至少三段擋位之 變檔操作，且兼具有機構簡單、成本低、以及變檔操作反 應迅速確實等優點。 為達上述之目的，本發明之倒踩多段變檔内變速器的 201219260 一較佳實施例係包括有： 一傳動軸心’其結合於一動力輸入端並可受該動力輸 入端之驅動而進行正、反轉運動，於該傳動轴心上並設置 有沿一軸心延伸之複數棘爪容置座； 一變速軸心’與該傳動軸心平行且相隔一預定距離設 置； 一變速齒輪組單元’其包括有複數傳動齒輪以及複數 變速齒輪；該複數傳動齒輪係套設於傳動轴心上，且該複 數變速齒輪係套設於該變速軸心上且係與該複數傳動齒 輪對應嚙合； 一變檔凸輪組單元’其包括有複數凸輪、複數轴心棘 爪以及至少一變檔控制棘爪；該複數凸輪與複數軸心棘爪 料設於轉雜处，且賊數轴心棘爪係與傳動轴心 ^動同步额_，讀爪齡聰·該複數棘爪 谷置座内且可受該複數凸輪之旋轉的控制而個別切換於 一内縮位置與-頂植置之間；該至少控讎爪係 鄰靠於複數凸輪之-賴，且可對應於傳練心之反轉運 動而抵頂該複數凸輪使其進行相對於該傳動軸心的旋轉 運動進而控制該複數轴心棘爪之位置切換操作；其中該 她軸心棘爪分別具有—制_，且各細棘爪之制動齒 的位置洽为別對應於該複數傳動齒輪中的其中之一傳動 齒輪；當某-轴心棘爪係位於該頂起位置時，該頂起之軸 心棘爪的她鱗會_住其觸紅傳_輪且將會 被傳動軸錢正轉時所帶_婦，至鄕餘於該内縮 位置之輛心棘爪所對應之傳動齒輪則將不會被傳動軸心 5 201219260 於正轉時所直接帶動；以及， 一傳動基座，結合於一動力輸出端與該複數傳動齒輪 之間’可受該複數傳動齒輪之帶動旋轉進而將正轉時之旋 轉動力輸出至該動力輸出端；其中，被該傳動軸心所帶動 旋轉之該傳動齒輪搭配與其所對應嚙合之該複數變速齒 輪中的其中之一變速齒輪可以決定該傳動基座的旋轉速 度，因此，被該傳動軸心所帶動旋轉之傳動齒輪改變時， 該傳動基座的旋轉速度也會改變。。 於一較佳實施例中，該倒踩多段變檔内變速器之該複 數傳動齒輪包括有一第一傳動齒輪、一第二傳動齒輪、及 一第三傳動齒輪;該第一傳動齒輪係結合且連動於該傳動 基座，因此該傳動基座係受該第一傳動齒輪所直接帶動旋 轉；並且，於各傳動齒輪之一内環部分別各設有可單向滑 脫之複數抵靠凹座，各傳動齒輪之複數抵靠凹座可在其所 對應之制動齒位於該頂起位置且於傳動軸心正轉時受到 該制動齒之抵頂而傳動。該複數變速齒輪包括有一第一變 速#輪、一第二變速齒輪、及一第三變速齒輪，分別與第 -、第二、及第三傳動齒輪對應嚙合。該複數凸輪包括有 一第-轴心固定凸輪、-變槽控制凸輪、及一第二轴心固 定凸輪；該第-與第二軸心固定凸輪係固定於該傳動轴心 上並與其連動旋轉;該變馳制凸輪係以—可相對滑動的 方式套設於傳動軸心上且是失置於第—與第二軸心固定 凸輪之間；於第-與第二軸心固定凸輪之一外環部分別各 叹有複數凸輪塊，且第-與第二轴心固定凸輪之複數凸輪 塊於旋轉方向上雜有-她差；於變碰制凸輪之一外 201219260 環部設有複數頂靠凸塊，且於變檔控制凸輪之一内環部設 有複數内凹部。該複數轴心棘爪包括有一第一轴心棘爪、 一第二轴心棘爪及一第三轴心棘爪；各轴心棘爪分別具有 包括該制動齒以及一切換齒’且各轴心棘爪之制動齒與切 換齒是同步切換於該内縮位置與該頂起位置之間；該第一 軸心棘爪之制動齒的位置係對應於該第一傳動齒輪之内 環部’該第二轴心棘爪之制動齒的位置係對應於該第二傳 動齒輪之内環部’且該第三轴心棘爪之制動齒的位置係對 應於該第二傳動齒輪之内環部；此外，各轴心棘爪之切換 齒的位置均是對應於該變檔控制凸輪之内環部處，當該變 擋控制凸輪之某一内凹部的位置恰對應於某軸心棘爪之 切換齒的位置時，該對應之軸心棘爪的切換齒將可頂入其 所對應之該内凹部中，進而使該對應之軸心棘爪的制動齒 也同步頂起而切換至該頂起位置；相對地，當某軸心棘爪 之切換齒的位置並無對應到任一内凹部的位置時，則該軸 心棘爪是處於該内縮位置。該至少一變檔控制棘爪包括有 -第-變檔㈣棘爪以及-第二_控制棘爪，且該第一 與第二變檔控制棘爪均可分別切換於一滑脫位置以及一 抵頂位置之間；該第-變槽控制棘爪的位置係對應於該第 -轴心固定凸輪之外環部與該㈣控制凸輪之外環部，且 該第-變檔鋪棘爪的位置係對應於該第二轴心固定凸 輪之外環部與該變權控制凸輪之外環部；該第一變槽控制 棘爪係受到該第-轴心固定凸輪之複數凸輪塊的旋轉影 響而切換⑽滑脫位置與抵雜置之間，並且，當第一變 檔控制棘爪錄她職置時，該第―__棘爪可抵 201219260 頂住該變檔控制凸輪之頂靠凸塊，而當第一變檔控制棘爪 位於該滑脫位置時則不會抵頂住該變檔控制凸輪之頂靠 凸塊；該第二變檔控制棘爪係受到該第二軸心固定凸輪之 複數凸輪塊的旋轉影響而切換於該滑脫位置與抵頂位置 之間，並且，當第二變檔控制棘爪位於該抵頂位置時，該 第二變檔控制棘爪可抵頂住該變檔控制凸輪之頂靠凸 塊’而當第一變槽控制棘爪位於該滑脫位置時則不會抿頂 住該變檔控制凸輪之頂靠凸塊。 於一較佳實施例中，本發明之隹彳踩多段變檔内變速器 之該第_、第二與第三傳動錄巾至少有兩個傳動齒輪的 齒數不相同。該第-、第二與第三變速齒輪巾至少有兩個 變速齒輪的齒數不相同。該第一與第二軸心固定凸輪兩者 之複數凸輪塊的數量均為三個，並且，該變播控制凸輪之 複數頂靠凸塊的數量為六個，而變標控制凸輪之複數内凹 部的數量為兩個。 【實施方式】 為使貴審查委員能對本發明之特徵、目的及功能有 更進一步的認知與瞭解，茲配合圖式詳細說明如後：201219260 VI. Description of the invention: [Technical field to which the invention pertains] The present invention is a __ step __妓, which is particularly suitable for being mounted on a bicycle, and can be driven by a pedal to reverse the plurality of buildings. The shifting operation is a reverse stepping multi-stage variable internal transmission. [Prior Art] With the awareness of environmental protection, brain, fitness and natural exhaustion, more and more people have traveled with bicycles that have the advantages of pollution-free, natural resources and sports and fitness. To replace the steam locomotive that consumes energy and causes pollution. Most of the commercially available variable speed bicycles use the lever of the outer transmission to move the chain to engage the different sizes of the toothed discs. However, it has been disclosed that the transmission is mounted in the bicycle hub. High- and low-speed shifting operations are performed by pedal-driven reversing of the sprocket; however, 'this type of internal transmission mechanism usually has only two stages of shifting, or has a complicated mechanism, high cost, and variable slot. The response to the operation is not fast enough to break through, and there is room for further improvement. SUMMARY OF THE INVENTION A first object of the present invention is to provide a step-down multi-step shifting internal transmission that can perform a shifting operation of at least three-stage gears by pedal-driven crank reversal, and has a simple mechanism. The advantages are low cost and quick response of the shifting operation. In order to achieve the above object, a preferred embodiment of the reversed stepped multi-speed shifting internal transmission of the present invention includes: a drive shaft that is coupled to a power input and is drivable by the power input. a forward and reverse movement, on the transmission shaft and provided with a plurality of pawl receiving seats extending along an axis; a shifting axis 'parallel to the transmission axis and separated by a predetermined distance; a shifting gear set The unit includes a plurality of transmission gears and a plurality of transmission gears; the plurality of transmission gears are sleeved on the transmission shaft, and the plurality of transmission gears are sleeved on the shift shaft and are correspondingly engaged with the plurality of transmission gears; a shift cam assembly unit includes a plurality of cams, a plurality of spindle pawls, and at least one shift control pawl; the plurality of cams and the plurality of shaft pawls are disposed at the turning, and the number of the claws is And the transmission shaft center synchronization amount _, the reading claw age Cong · the plurality of pawl valleys are seated and can be individually switched between a retracted position and the top implant between the rotation of the plurality of cams; At least control The claws are adjacent to the plurality of cams, and can correspond to the reverse movement of the transmission heart to abut the complex cam to perform a rotational motion relative to the transmission axis to control the plurality of axial pawls Position switching operation; wherein the axial pawl respectively has a system_, and the position of the braking teeth of each thin pawl is coordinated to correspond to one of the plurality of transmission gears; when a certain axis When the claw system is in the jacking position, the scale of the jacking pawl of the jacking will be _ live in the red pass _ wheel and will be carried by the drive shaft when the money is forwarded to the woman The transmission gear corresponding to the pawl of the retracted position will not be directly driven by the transmission shaft 5 201219260 during forward rotation; and a transmission base is coupled between a power output end and the plurality of transmission gears 'Acceptable by the rotation of the plurality of transmission gears, the rotary power during forward rotation is output to the power output end; wherein the transmission gear rotated by the transmission shaft is matched with the plurality of gears meshed with the corresponding gears One of the gears To determine when the rotational speed of the drive base, therefore, is driven by the rotating shaft center of the gear change transmission, the base rotational speed of the transmission will change. . In a preferred embodiment, the plurality of transmission gears of the multi-step shifting internal transmission includes a first transmission gear, a second transmission gear, and a third transmission gear; the first transmission gear train is combined and interlocked The transmission base is driven by the first transmission gear to rotate directly; and the inner ring portion of each of the transmission gears is respectively provided with a plurality of abutting recesses that can be unidirectionally detached. The plurality of transmission gears abut against the recess can be driven by the braking teeth being abutted when the corresponding braking teeth are in the jacking position and when the transmission shaft is rotating forward. The plurality of shifting gears includes a first shifting speed # wheel, a second shifting gear, and a third shifting gear, respectively engaging the first, second, and third transmission gears. The plurality of cams include a first-axis fixed cam, a variable groove control cam, and a second axial fixed cam; the first and second axial fixed cams are fixed on the drive shaft and rotate in conjunction therewith; The camcorder cam is sleeved on the drive shaft in a relatively slidable manner and is displaced between the first and second axial fixed cams; outside one of the first and second axial fixed cams Each of the ring portions has a plurality of cam blocks, and the plurality of cam blocks of the first and second axis fixed cams are mixed in the direction of rotation - she is poor; and one of the cams of the touch is provided with a plurality of abutments at the ring portion of the 201219260 ring portion The bump and the inner ring portion of one of the shift control cams are provided with a plurality of inner recesses. The plurality of axial pawls include a first axial pawl, a second axial pawl and a third axial pawl; each axial pawl has a braking tooth and a switching tooth respectively The brake teeth of the heart pawl and the switching teeth are synchronously switched between the retracted position and the jacking position; the position of the braking teeth of the first shaft pawl corresponds to the inner ring portion of the first transmission gear The position of the brake teeth of the second shaft pawl corresponds to the inner ring portion ' of the second transmission gear and the position of the brake teeth of the third shaft pawl corresponds to the inner ring portion of the second transmission gear; The position of the switching teeth of each of the pivoting pawls is corresponding to the inner ring portion of the shifting control cam, and the position of a certain concave portion of the shifting control cam corresponds to the position of the switching tooth of a certain axial pawl The switching teeth of the corresponding pivot pawl can be inserted into the corresponding recessed portion thereof, so that the braking teeth of the corresponding pivot pawl are simultaneously jacked up and switched to the jacking position; Ground, when the position of the switching teeth of a certain axis pawl does not correspond to When the position of the inner recess is reached, the pivot pawl is in the retracted position. The at least one shift control pawl includes a -first-shift (four) pawl and a second-control pawl, and the first and second shift control pawls are each switchable to a slip position and a Between the abutting positions; the position of the first-slot control pawl corresponds to the outer ring portion of the first-axis fixed cam and the outer ring portion of the (four) control cam, and the first-shift pawl Position corresponding to the second axial fixed cam outer ring portion and the variable weight control cam outer ring portion; the first variable groove control pawl is affected by the rotation of the plurality of cam blocks of the first axial fixed cam And switching (10) between the slip position and the offset, and when the first shift control pawl records her position, the first __ pawl can resist the 201219260 against the top of the shift control cam a block, and when the first shift control pawl is in the slip position, does not resist against the abutting lug of the shift control cam; the second shift control pawl is fixed by the second shaft Switching between the slip position and the abutment position by the rotation of the plurality of cam blocks of the cam, and when the second change When the shift control pawl is in the abutting position, the second shift control pawl can abut against the top bump of the shift control cam and when the first change control pawl is in the slip position The top bump of the shift control cam is not clamped. In a preferred embodiment, the number of teeth of the at least two drive gears of the first, second, and third drive reels of the multi-step shifting internal transmission of the present invention are different. The first, second, and third shifting gears have at least two shifting gears having different numbers of teeth. The number of the plurality of cam blocks of the first and second axial fixed cams is three, and the number of the plurality of abutting bumps of the variable control cam is six, and the number of the variable control cams is plural The number of recesses is two. [Embodiment] In order to enable the reviewing committee to have a further understanding and understanding of the features, purposes and functions of the present invention, the detailed description of the drawing is as follows:
S 請參閱圖一至圖八c，其揭露了本發明之倒踩多段變 檔内變速器1的一較佳實施例。其中，圖一是本發明倒踩 多段變檔内變速器1之一較佳實施例於第一視角之立體 爆炸視圖；圖二是本發明倒踩多段變檔内變速器丨之較佳 實施例於第二視角之立體爆炸視圖；圖三是本發明倒踩多 &變播内變速器1之較佳實施例於組合狀態下之右側視 8 201219260 圖；圖四是圖三中所示之A-A剖面視圖（含曲柄91及齒 片92);圖五是本發明倒踩多段變檔内變速器1於組合狀 態下之立體視圖（不含珠碗681、玉押682及第二固定 座）；圖六A、六B與六C分別是本發明之倒踩多段變檔 内變速器1之第一、第二與第三傳動齒輪31、32、33的 側視圖；圖七A、七B與七C分別是本發明之倒踩多段 變檔内變速器之第一固定凸輪41、軸心固定凸輪42與第 二固定凸輪43的侧視圖；圖八A、八B與八C分別是本 發明之倒踩多段變檔内變速器之第一、第二與第三軸心棘 爪44、45、46的立體視圖。 如圖一至圖五所示’本發明之倒踩多段變檔内變速器 1的一較佳實施例’係可以被裝設於自行車之一車架内 (圖中未示），尤其適合被裝設於用來組設腳踏曲柄91 (Crank)之心轴的車架的五通管位置處》本發明之倒踩 多段變檔内變速器1可藉由腳踏驅動曲柄91反轉（也就 是倒踩腳踏板）來進行至少三段變速之變檔操作。於本實 施例中，該倒踩多段變檔内變速器1包括有：一傳動軸心 10、一變速軸心20、一變速齒輪組單元30、一變檔凸輪 組單元40、一傳動基座50、一第一固定座61、一第二固 定座62、兩滾針培林63、64、一滾珠環65、一齒片固定 座66、至少一支撐柱67、一珠碗68'1以及一玉押682。 該傳動軸心10係結合於一動力輸入端並可受該動力 輸入端之驅動而進行正、反轉運動。於本實施例中，該動 力輸入端就是自行車之兩曲柄91。於該傳動軸心10之外 表面上並設置有沿一軸心延伸之複數棘爪容置座101、 201219260 102、103，且於傳動軸心ι〇之兩末端係分別設置了與曲 柄91結合用之方頭部。於本實施例中，該複數棘爪容置 座包括了一第一棘爪容置座1〇1、一第二棘爪容置座 102、及一第三棘爪容置座1〇3。各棘爪容置座1〇1、1〇2、 103係呈軸向延伸之狹長淺溝狀結構，且各棘爪容置座 101、102、103係大致等距相互間隔。 該變速軸心20係與該傳動軸心1〇平行且相隔一預定 距離設置。該變速齒輪組單元30包括有複數傳動齒輪 31、32、33以及複數變速齒輪34、35、36。該複數傳動 齒輪31、32、33係套設於傳動軸心1〇上’且該複數變速 齒輪34、35、36係套設於該變速軸心20上且係分別與該 複數傳動齒輪31、32、33對應嚙合。 請參閱圖一、圖二及圖四並搭配圖六A、圖六B及 圖六C。於本實施例中，該複數傳動齒輪包括有一第一傳 動齒輪31、一第二傳動齒輪32、及一第三傳動齒輪33。 該第一、第二、及第三傳動齒輪31、32、33三者之間並 非固定在一起而是可以不同步旋轉的。該第一傳動齒輪 31係藉由若干卡塊313結合於該傳動基座5〇之卡槽501 中’使第一傳動齒輪31與傳動基座50連動，因此該傳動 基座5〇係受該第一傳動齒輪31所直接帶動而同步旋轉。 並且’於各傳動齒“31、32、33之一内環部31卜32卜 331分別各設有可單向滑脫之複數抵靠凹座312、322、 332。各傳動齒輪31、32、33之複數抵靠凹座312、322、 332可在其所對應之制動齒44卜451、461位於頂起位置 且於傳動軸心1〇正轉時受到該些制動齒44卜451、461 201219260 其中之一的抵頂而傳動，並在傳動軸心ίο反轉時使各制 動齒441、451、461滑脫不傳動。該複數變速齒輪包括有 一第一變速齒輪34、一第二變速齒輪35、及一第三變速 齒輪36,其分別與第一、第二、及第三傳動齒輪31、32、 33對應嚙合。於本實施例中，該第一、第二、及第三變 速齒輪34、35、36都是與變速軸心20同步旋轉。並且， 該第一、第二與第三傳動齒輪31、32、33中至少有兩個 傳動齒輪的齒數不相同，且該第一、第二與第三變速齒輪 34、35、36中至少有兩個變速齒輪的齒數不相同。於本 實施例中，該第二傳動齒輪32的齒數大於第一傳動齒輪 31 ’且第一傳動齒輪31的齒數又大於第三傳動齒輪33 的齒數；此外，該第三變速齒輪36的齒數大於第一變速 齒輪34 ’且第一變速齒輪34的齒數又大於第二變速齒輪 35的齒數。 請參閱圖一至圖五，該變檔凸輪組單元40包括有複 數凸輪41、42、43、複數轴心棘爪44、45、46以及至少 一變檔控制棘爪47、48。該複數凸輪41、42、43與複數 軸心棘爪44、45、46係套設於該傳動轴心1〇上，且該複 數軸心棘爪44、45、46係與傳動軸心1〇連動同步旋轉。 該複數軸心棘爪44、45、46係分別容納於該傳動軸心10 上之複數棘爪容置座101、102、103内且可受該複數凸輪 41、42、43之旋轉的控制而個別切換於一内縮位置與一 頂起位置之間，因此也可以被稱作為「軸心控制元件」， 意指設置在軸心上的控制元件。該至少一變標控制棘爪 47、48係鄰靠於複數占輪41、42、43之一旁側，且可對 201219260 應於傳動軸、10之反轉運動而抵頂該複數凸輪ΜΑ、 43使其進行相對於該傳動轴心ι〇的旋轉運動進而控制該 、45、46之位置切換操作。其中，該複 〜、、45、46分別具有一制動齒441、45卜461， 且各軸心棘爪44、45、46之制動齒441、收、461的位 置恰分別對應於該複數傳動齒輪3卜32、33中的其中之 一傳動齒輪3卜32、33的内環部3U、32卜331。、當某 轴、棘爪44 (或45、或46)係位於該頂起位置時，該 頂起之軸、棘爪44(或45、或46)的制動齒441 (或45卜 抵頂住其所對應之傳動齒輪31 (或32、或 Λ部311 (或321、或331)上的抵靠凹座312 3 、或332)且將會被傳動軸心10於正轉時所帶動 内祕置之細棘爪所對應之傳 2輪卿不會被傳動細1G於正轉時所直接帶動，而 先經過複數變逮齒輪34、35、36的傳動與變 =後再由第-觸錄31把旋軸力舰給傳動基座 ，例錢，當第—細麻44錄_起位置時， 、他兩轴心棘爪45、46都會位於内縮位置’·此時， 2轴心1G於正轉_會直縣動第—傳麟輪31，進 :旋轉動力經由傳動基座5G而傳送給齒片固定座的， 其他兩傳動齒輪32、33會呈不傳動狀態。而當第 4=^棘爪45錄，鱗其細細棘爪 蔣合古都會錄_位置，·此時，傳雜心於正轉時 將會直接㈣第二傳_輪32，㈣二働錄％會將 12 201219260 動力傳送給與其嚙合之第二變速齒輪35，接著透過變逮 軸心20將動力傳給與第二變速齒輪35同步旋轉之第—變 速齒輪34，再將旋轉動力傳送給與第一變速齒輪34嚙合 之第一傳動齒輪31，進而將旋轉動力經由傳動基座5〇而 傳送給齒片固定座66，同時，第三傳動齒輪33會呈不傳 動狀態。又，當第三軸心棘爪46位於該頂起位置時，此 時其他兩軸心棘爪44、45都會位於内縮位置；此時，傳 動軸心10於正轉時將會直接帶動第三傳動齒輪33 ,而第 三傳動齒輪33會將動力傳送給與其嚙合之第三變速齒輪 36，接著透過變速軸心20將動力傳給與第三變速齒輪％ 同步旋轉之第一變速齒輪34，再將旋轉動力傳送給與第 一變速齒輪34嚙合之第一傳動齒輪31，進而將旋轉動力 經由傳動基座50而傳送給齒片固定座66 ,同時，第二傳 動齒輪32會呈不傳動狀態。藉此，即可達到藉由傳動軸 心10之反轉動作來控制某一轴心棘爪44、45、46切換至 該頂起位置進而改變輸出動力之轉速的三段變速功能。 請參閱圖一、圖二並搭配圖七A、圖七b及圖七c。 於本實施例中，該複數凸輪包括有一第一軸心固定凸輪 41、一變檔控制凸輪42、及一第二轴心固定凸輪43。該 第一與第二軸心固定凸輪41、43係固定於該傳動軸心1〇 上並與其連動旋轉。該變檔控制凸輪42係以一可相對滑 動的方式套設於傳動軸心10上且是夾置於第一與第二軸 〜固疋凸輪41、43之間。於第一與第二軸心固定凸輪々I、 43之一外環部分別各設有可驅使變檔控制棘爪47、48使 之脫離與頂靠凸塊421嚙合之複數凸輪塊411、431，並 13 201219260 且，第一與第二軸心固定凸輪41、43之複數凸輪塊4u、 431於旋轉方向上係具有一相位差。於變檔控制凸輪42 之一外環部設有複數頂靠凸塊421 ’且於變樓控制凸輪42 之一内環部設有複數内凹部422。於本實施例中，該第一 與第二轴心固定凸輪41、43兩者之複數凸輪塊4U、431 的數量均為三個，並且，該變檔控制凸輪42之複數頂靠 凸塊421的數量為六個，而變檔控制凸輪42之複數内凹 部422的數量為兩個。 請參閱圖一、圖二並搭配圖七A、圖七B及圖七c。 於本實施例中’該複數軸心棘爪包括有一第一軸心棘爪 44、一第二軸心棘爪45及一第三軸心棘爪46。各軸心棘 爪44、45、46分別具有包括該制動齒441、451、461以 及一切換齒442、452、462，且個別軸心棘爪44 (或45、 或46)之制動齒441 (或451、或461)與切換齒442 (或 452、或462)兩者是同步切換於該内縮位置與該頂起位 置之間。該第一軸心棘爪44之制動齒441的位置係對應 於該第一傳動齒輪31之内環部311，該第二軸心棘爪幻 之制動齒451的位置係對應於該第二傳動齒輪&之内環 部32卜且該第三軸心棘爪46之制動齒461的位置係對 應於該第三傳動齒輪33之内環部33卜此外，各轴心棘 爪44、45、46之切換齒442、452、462的位置均是對應 於該變樓測凸輪42之内環做，當該控制凸輪们 内環部之某-内凹部422的位置怜對應於某軸心棘爪44 (或45、或46)之切換齒442 (或452、或462)的位置 時，該對應之軸心棘爪44 (或45、或46)的切 201219260 (或452、或462)將可頂入其所對應之該内凹部422申 而抬高到該頂起位置，進而使該對應之軸心棘爪44 (或 45、或46)的制動齒441 (或45卜或461)也同步頂起 而切換至該頂起位置。相對地，當某轴心棘爪44 (或45、 或46)之切換齒442 (或452、或462)的位置並無對應 到任一内凹部422的位置時，則該軸心棘爪44 (或45、 或46)是處於_縮位置，第―、第二與第三轴心棘 爪44、45、46上分別各設置有一彈性元件（例如扭力彈 著等）可以使第…第二與第三轴心棘爪44、45、46在 未受外力影響時會有切換至該頂起位置的趨勢。 琢至>、一變檔控制棘爪包括有一第一變檔控制棘乂 47以及-第二變槽控讎爪48，且該第一與第二變標老 制棘爪47、48均可分_換於—滑紐置以及一抵頂4 置之間。該第-變槽控制棘纟47的位置係對應於該第-轴心固定凸輪41之外環部與該變槽控制凸輪42之相 邛且該第一變播控制棘爪48的位置係對應於該第二車 心固定凸輪43之外環倾該賴㈣凸輪们之外環部 該第-變難雜爪47齡_第—軸心固定凸輪4: ^部之複數凸輪塊411的旋轉帶動而切換於該滑脫仿 =_位置⑽’並且’當第—變迦制棘爪47细 該抵頂^置且傳動軸心1G反轉時，該第—_控_ 可抵頂住該變檔控制凸輪42之其中之一頂靠凸场 而當第-變魅制棘爪47位於該滑脫位置時則不 ^頂住該鋪凸輪42之頂紅塊42 脫。該第二變標控制棘爪48係受到 二= 15 201219260 m之複數凸輪塊431的旋轉帶動而切換於該滑脫 =抵頂位置之間，並且，當第二變樓控制棘爪48位 =抵職置且侧^ 1G反_，該第二變樓控制棘 爪48可抵頂住該變播控制凸輪&之其中之一頂靠凸塊 4儿而當第二變標控制棘爪48位於該滑脫位置時則不會 抵頂住該變播控制凸輪42之頂靠凸塊421。於本實施例 中該第與第一變槽控制棘爪47、48設置方向相同， 也就是都是朝向順著該第-與第二軸心岐凸輪41、化 之複數凸輪塊4U、431的隆起方向凸伸設置，所以無論 第-與第二軸4爾凸㈣、43是正轉狀轉都會滑脫 (換句話說，也就是較朝向可魄頂健賴控制凸輪 42之複數頂靠凸塊421的方向凸伸設置）；並且，該第一 與第二_控繼爪47、48上分別各設置有-彈性元件 (例如扭力彈簧等）可以使第一與第二變檔控制棘爪 47 48在未受外力影響時有切換至該抵頂位置的趨勢。 於本實施例中，該第一與第二軸心固定凸輪41、43 外環部所設之複數凸輪塊4U、431會使傳動軸心1〇在正 轉時，第一與第二變槽控制棘爪47、48無論其位置是在 抵頂位置或滑脫位置都會和變檔控制凸輪42之各頂靠凸 塊421呈互相滑脫狀態，只有在當傳動軸心1〇反轉時才 會使位於抵頂位置的某一變檔控制棘爪47 (或48)去抵 頂到變檔控制凸輪42的某一頂靠凸塊421。並且，也只 有在某一變檔控制棘爪47(或48)已抵頂到變檔控制凸 輪42的某一頂靠凸塊421、且傳動軸心1〇又繼續旋轉一 預定角度時，該變檔控制棘爪47 (或48)才會去推動變 201219260 檔控制凸輪42旋轉，促使變檔控制凸輪42内環部之某一 内凹422的位置位移到與某轴心棘爪44(或45、或46) 之切換齒442 (或452、或462)相對應的位置，進而達 到換播、變速的操作目的。此外，各傳動齒輪31、32、 33内環部311、321、331所設有之複數抵靠凹座312、322、 332的單向滑脫方向，則是會使傳動轴心1〇在反轉時， 第一、第二與第三軸心棘爪44、45、46無論其位置是在 頂起位置或内縮位置都會和各傳動齒輪31、32、33之各 抵靠凹座312、322、332呈互相滑脫狀態，只有當傳動轴 心10在正轉時，才會使位於頂起位置的某一軸心棘爪44 (或45、或46)的制動齒441 (或45卜或461)去抵頂 到其所對應的傳動齒輪31(或32、或33)的抵靠凹座312 (或322、或332)。換句話說，當傳動軸心1〇在反轉時 只能進行換構變速的操作，而只有傳動軸心10在正轉 時，來自傳動轴心10的輸入動力才會經由與傳動齒輪31 相結合之傳動基座50來輸出。簡單來說，於圖七β所示 之變檔控制凸輪42 ,其内環部之内凹部422相對於傳動 轴心10的旋轉角度位置，決定了第一、第二與第三軸心 棘爪44、45、46之制動齒441 (或45卜或461)的頂起 或内縮狀態。而此内凹部422的位置，則是由第二轴心固 定凸輪43外環部之複數凸輪塊431配合變檔控制凸輪42 之複數頂靠凸塊421與第一變檔控制棘爪47的相對位置 來決定左側曲柄91的換擋位置，或也可是第一軸心固定 凸輪41之複數凸輪塊411配合421配合複數頂靠凸塊421 與第二變檔控制棘爪48的相對位置來決定右側曲柄91 17 201219260 換檔位置。此配合的相對位置’是為了達到令曲柄91於 特定位置下可具備換檔操作的功能。 如圖一至圖五所示’該傳動基座50係結合於一動力 輸出端與該複數傳動齒輪31、32、33之間，可受該複數 傳動齒輪中的第一傳動齒輪31之帶動旋轉進而將傳動軸 心10正轉時之旋轉動力輸出至該動力輸出端。於本實施 例中’該動力輸出端就是該齒片92。如前所述，被該傳 動軸心10所帶動旋轉之該傳動齒輪31 (或32、或33) 搭配與其所對應嚙合之該複數變速齒輪中的其中之一變 速齒輪34 (或35、或36)可以決定該傳動基座5〇的旋 轉速度，因此，被該傳動軸心10於正轉時所帶動旋轉之 傳動齒輪31、32、33改變時’該傳動基座5G的旋轉速度 也會改變，進而達到多段變速的目的。 、該第一固定座61與第二固定座62分別位於該傳動軸 ί〇之兩端且是固定概自行車之車架鄰近曲柄91處。 於該第-與第二狀座6卜62上分別各設有—開口 611、 621及變速軸座612、622。該變速軸心20係設置於該 第:與第二固定座6卜62之兩變速軸座612、⑵之間， ;該變逮軸心2〇兩端對應於該第一與第二固定座^、 之變逮轴座6】2、622處分別各設有該滾針培林63、64, =變迷輪心20可相對於第—與第二固定座6卜幻轉動。 =滚珠環65係容置於該第一固定座61之開口 611中。該 =基座50係穿套於該滚珠環&中使傳動基座5〇可相 出^第m疋座61轉動，且該傳動基座5〇之一端係凸伸 一固定座61較遠離第二固定座62之侧外。該齒片固 201219260 定座66係設置於第一固定座61較遠離第二固定座62之 側且係結合於該傳動基座5〇並可受其驅動旋轉：其中， 該齒片92是固定於齒片固定座66上。 該至少一支撐柱67係結合於第一與第二固定座μ、 62之間，用以加強結構強度。於本實施例中支撐柱幻 的數量為兩個，但也可以是其他數量。該傳動軸心1〇係 以可相對旋轉的方式穿套於該傳動基座5〇之中。該傳動 軸心10之一端係凸伸出該第一固定座61之開口 外、 而另一端係凸伸出該第二固定座62之開口 621外並且， 該傳動軸心10之兩端係分別結合於該兩曲柄91。此外， 於該傳動軸心ίο對應於該第二固定座62之開口 621處並 套設有一珠碗681及一玉押682。 以上所述之本發明倒踩多段變檔内變速器的實施 例’主要是以設置在傳動軸心上所設置之容置槽内的棘爪 (尤其是軸心棘爪44、45、46)來作為軸心控制元件， 而可藉由棘爪的位置切換（例如頂起位置或内縮位置）來 決疋哪一傳動齒輪會被傳動軸心於正轉時所帶動旋轉，進 而達到多段變速的功能。然而，在另一實施例中本發明 之倒踩多段變勒變速器，也可以使_樣找置在傳動 軸心上所設置之容置槽内的至少一「鍵」來取代前述的棘 爪以作為軸心控制元件，同樣可藉由該至少一「鍵」（也 就是轴心控制元件）於軸向上之位置切換，來決定決定哪 一傳動齒輪會被傳動軸心於正轉時所帶動旋轉，進而同樣 可達到多段變速的功能。而在此一以至少一「鍵」來作為 軸心控制元件的實施例中，本發明之複數凸輪會包括有： 201219260 至少-軸心固定凸輪及—賴控制凸輪；該賴控制凸輪 係以一可相對旋轉的方式套設於傳動軸心上且連動於該 至少一「鍵」（也就是軸心控制元件），且該變檔控制凸輪 上之凸輪形狀的設計是可用來控制該「鍵」於該傳動軸心 上進行「軸向位移」之位置的切換。至於，於本實施例中 之其他元件例如變速軸心、變速齒輪組單元、傳動基座等 元件則了以使用與前述實施例相同或類似的技術，所以不 予贅述^ Q •mf 清參閱圖九A、圖九B、圖九C以及圖十。其中，圖 九A、圖九B、圖九C分別為本發明之倒踩多段變槽内變 速器之第一軸心固定凸輪41a、變檔控制凸輪42a與第二 轴心固定凸輪43a的另一實施例的側視圖。圖十則為將此 些第一軸心固定凸輪41a、變檔控制凸輪42a與第二轴心 固疋凸輪43a套設於傳動轴心1〇上時的組合視圖（未含 鋼珠426 )。於本實施例中的第一轴心固定凸輪41a、變檔 控制凸輪42a與第二軸心固定凸輪43a的結構與功能大致 上與圓七A、圖七B及圖七C所示者類似，其唯一的不 同點乃在於：於圖九A、圖九B及圖九C中所示之第一 軸心固定凸輪41a與第二軸心固定凸輪43a上分別各設有 位置相對應之三個弧狀滑槽415、435 ;並且，第一軸心 固定凸輪41a之任一弧狀滑槽415於一正轉方向上的前端 恰對應於第二軸心固定凸輪43a之相對應51狀滑槽435的 尾端。此外，在變擋控制凸輪42a上、且對應於各個弧狀 滑槽415、435的兩端位置處，則分別各設有至少一圓洞 425 ’並且於各個該圓洞425中分別設置有一鋼珠426。 20 201219260 該鋼珠426的直徑係相當於或略小於該圓洞似5的内徑。 於本實施例中同樣地，該第-與第二轴心固定凸輪仏、 43a係固定於該傳動軸心10上並與其連動旋轉；且該變 播控制凸輪4如係以-可相對滑動的方式套設於傳動轴 心ίο上且是夹置於第一與第二軸心固定凸輪41a、43a之 間。於第一與第二軸心固定凸輪41a、43a之一外環部分 別各設有可驅使變槽控制棘爪47、48使之脫離與頂靠凸 塊421啼合之複數凸輪塊411、431，並且，第一與第二 軸心固定凸輪41a、43a之複數凸輪塊4U、431於旋轉方 向上係具有一相位差。於變檔控制凸輪42a之一外環部設 有複數頂靠凸塊421 ’且於變檔控制凸輪42之一内環部 設有複數内凹部422。 由於，於圖一所示之變檔凸輪組單元40在配合第 一、第一與第二軸心棘爪44、45、46作動的過程中，當 任一轴心棘爪44、45、46從開啟（頂起）到閉合（内縮） 時的角度’此區段會存在不穩定區，此一不穩定區有可能 會產生空播現象。為了排除此一不穩定區，本發明特別於 圖九A、圖九B、圖九C及圖十所示之實施例中，藉由該 些弧狀滑槽415、435以及位於該些圓洞425中之鋼珠426 的配合來組構成一額外的鋼珠機構。當變擋控制凸輪42a 相對於第一與第二軸心固定凸輪41a、43a滑動時，該些 鋼珠426可在該些弧狀滑槽415、435内滑動，直到到達 滑槽415、435尾端後’該些鋼珠426才會抵靠住第一與 第二轴心固定凸輪41a、43a。又則’當變檔控制凸輪42a 繼續回轉，鋼珠426便會由弧狀滑槽415突破至滑槽 201219260 435，且另一鋼珠426會由弧狀滑槽435突破至滑槽415， 如此，將使鋼珠426與滑槽415、435交互推擠作用。此 交互推擠突破的過程可輔助軸心棘爪44、45、46做快速 的開閉合動作。令變檔控制凸輪42a無法穩定在此推擠的 過程之中’逃避内部之任一軸心棘爪、45、46開啟與 閉合之銜接點，進而免除了切換變檔過程的模糊區間。如 此一來’在檔位為切換的過程中便能避免棘爪發生衝突的 現象，不僅在換檔中不再有空檔現象，且也具有使用者在 換檔後可以感覺倒踩時有否換檔的回饋装置功能。 如前所述，於本實施例中，該些圓洞425位置，需相 對於變播控制凸輪42内環部所設之該複數内凹部422的 特徵，以使第一、第二與第三軸心棘爪44、45、46可在 正確的角度（此角度是對應於内凹部422的位置）被順利 地執行開啟或閉合的操作。並且，滑槽415、435位置則 需相對於這些圓孔425的位置，使得第一、第二與第三轴 心棘爪44、45、46無法定位於開啟與閉合的換檔過程區 域。 唯以上所述之實施例不應用於限制本發明之可應用 範圍’本發明之保護範圍應以本發明之_請專利範圍内容 所界定技術精神及其均等變化所含括之範圍為主者。即大 凡依本發明申請專利範圍所做之均等變化及修飾，仍將不 失本發明之要義所在，亦不脫離本發明之精神和範圍’故 都應視為本發明的進一步實施狀況。 s 22 201219260 【圖式簡單說明】 囷一是本發明倒踩多段變檔内變速器之一較佳實施例 於第一視角之立體爆炸視圖。 圖二是本發明倒踩多段變檔内變速器之較佳實施例於 第二視角之立體爆炸視圖。 圖三是本發明倒踩多段變檔内變速器之較佳實施例於 組合狀態下之右側視圖。 圖四是圖三中所示之A-A剖面視圖（含曲柄及齒片）。 圖五是本發明倒踩多段變檔内變速器於組合狀態下之 立體視圖（不含珠碗、玉押及第二固定座）。 圖六A、六B與六C分別是本發明之倒踩多段變檔内變 速器之第一、第二與第三傳動齒輪的側視圖。 圖七A、七B與七C分別是本發明之倒踩多段變檔内變 速器之第一轴心固定凸輪、變檔控制凸輪與第二軸 心固定凸輪的側視圖。 圖八A、八B與八C分別是本發明之倒踩多段變檔内變 速器之第一、第二與第三軸心棘爪的立體視圖。 圖九A、九B與九C分別是本發明之倒踩多段變檔内變 速器之第一軸心固定凸輪、變檔控制凸輪與第二軸 心固定凸輪的另一實施例的側視圖。 圖十則為將圖九Α、九Β與九C中所示之第一軸心固定 凸輪、變檔控制凸輪與第二軸心固定凸輪套設於傳 動軸心上時的組合視圖（未含鋼珠 23 201219260 【主要元件符號說明】 1〜本發明之倒踩多段變檔内變速器 10〜傳動軸心 101、102、103〜棘爪容置座 20〜變速軸心 30〜變速齒輪組單元 31〜第一傳動齒輪 31卜321、331〜内壤 312、322、332〜抵靠凹座 1 313〜卡塊 32〜第二傳動齒輪 33〜第三傳動齒輪 34〜第一變速齒輪 35〜第二變速齒輪 36〜第三變速齒輪 40〜變檔凸輪組單元 41、41a〜第一軸心固定凸輪 41卜431〜凸輪塊 42、42a〜變樓控制凸輪 415、435〜滑槽 421〜頂靠凸塊 422〜内凹部 425〜圓洞 426〜鋼珠 43、43a〜第二軸心固定凸輪 44〜第一軸心棘爪 45〜第二轴心棘爪 46〜第三轴心棘爪 441、451、461〜制動齒 442、452、462〜切換齒 47〜第一變檔控制棘爪 48〜第二變槽控制棘爪 50〜傳動基座 501〜·槽 61〜第一固定座 611、621 〜開口 612、622〜變速轴座 62〜第二固定座 63、64〜滾針培林 65〜滾珠環 24 201219260 66〜齒片固定座 681〜珠碗 91〜曲柄 67〜支撐柱 682〜玉押 92〜齒片 25Referring to Figures 1 through 8c, a preferred embodiment of the reverse stepped multi-speed shifting internal transmission 1 of the present invention is disclosed. 1 is a perspective exploded view of a preferred embodiment of the reverse multi-speed shifting internal transmission 1 of the present invention in a first viewing angle; FIG. 2 is a preferred embodiment of the reverse multi-step shifting internal transmission of the present invention. A three-dimensional exploded view of the two views; FIG. 3 is a view of the right side of the preferred embodiment of the inverted multi-amplified internal transmission 1 in the combined state of the figure 8 201219260; FIG. 4 is a cross-sectional view of the AA shown in FIG. (including the crank 91 and the tooth piece 92); FIG. 5 is a perspective view of the reverse shifting multi-stage shifting internal transmission 1 in the combined state (excluding the bead bowl 681, the jade 682 and the second fixed seat); FIG. , six B and six C are respectively side views of the first, second and third transmission gears 31, 32, 33 of the multi-step shifting internal transmission 1 of the present invention; FIGS. 7A, 7B and 7C are respectively A side view of the first fixed cam 41, the axial fixed cam 42 and the second fixed cam 43 of the multi-step shifting internal transmission of the present invention; FIGS. 8A, 8B and 8C are respectively the reverse stepping of the present invention A perspective view of the first, second and third pivot pawls 44, 45, 46 of the in-speed transmission. As shown in FIG. 1 to FIG. 5, a preferred embodiment of the multi-step shifting internal transmission 1 of the present invention can be installed in a bicycle frame (not shown), and is particularly suitable for being installed. In the position of the five-way pipe of the frame for assembling the crankshaft of the crank crank 91 (Crank), the reverse shifting multi-speed shifting internal transmission 1 of the present invention can be reversed by the pedal driving crank 91 (that is, the inverted Step on the pedal) to perform at least three-speed shifting. In the embodiment, the reverse step multi-speed shift internal transmission 1 includes: a transmission shaft 10, a shifting shaft 20, a shifting gear unit 30, a shifting cam assembly unit 40, and a transmission base 50. a first fixing seat 61, a second fixing seat 62, two needle rollers 63, 64, a ball ring 65, a tooth holder 66, at least one supporting column 67, a bead bowl 68'1 and a Jade 682. The drive shaft 10 is coupled to a power input end and is capable of being driven by the power input to perform positive and negative movements. In this embodiment, the power input end is the two cranks 91 of the bicycle. The outer surface of the transmission shaft 10 is provided with a plurality of pawl receiving seats 101, 201219260 102, 103 extending along an axis, and the ends of the transmission shaft ι are respectively provided in combination with the crank 91. Use the square head. In the embodiment, the plurality of pawl receptacles include a first pawl receiving seat 1〇1, a second pawl receiving seat 102, and a third pawl receiving seat 1〇3. Each of the pawl accommodating seats 1〇1, 1〇2, and 103 is an elongated shallow groove-like structure extending in the axial direction, and each of the pawl accommodating seats 101, 102, and 103 is substantially equidistantly spaced from each other. The shifting spindle 20 is disposed parallel to the drive shaft 1 且 and spaced apart by a predetermined distance. The shifting gear unit 30 includes a plurality of transmission gears 31, 32, 33 and a plurality of shifting gears 34, 35, 36. The plurality of transmission gears 31, 32, 33 are sleeved on the transmission shaft 1' and the plurality of transmission gears 34, 35, 36 are sleeved on the shifting shaft 20 and respectively coupled to the plurality of transmission gears 31, 32, 33 correspond to the meshing. Please refer to Figure 1, Figure 2 and Figure 4 together with Figure 6A, Figure 6B and Figure 6C. In the embodiment, the plurality of transmission gears includes a first transmission gear 31, a second transmission gear 32, and a third transmission gear 33. The first, second, and third transfer gears 31, 32, 33 are not fixed together but may be rotated asynchronously. The first transmission gear 31 is coupled to the transmission slot 50 by a plurality of latches 313 in the slot 501 of the transmission base 5, so that the transmission base 5 is subjected to the The first transmission gear 31 is directly driven to rotate synchronously. And each of the inner ring portions 31, 32, 331 of each of the transmission teeth "31, 32, 33" is provided with a plurality of abutting recesses 312, 322, 332 which are unidirectionally slidable. Each of the transmission gears 31, 32, The plurality of abutting recesses 312, 322, 332 can be received by the brake teeth 44 when the corresponding brake teeth 44, 451, 461 are in the jacking position and are rotated forward in the transmission shaft 1 451, 461, 201219260 One of the drives is driven against the top, and the brake teeth 441, 451, 461 are slipped off when the drive shaft is reversed. The plurality of shifting gears includes a first shifting gear 34 and a second shifting gear 35. And a third shifting gear 36 that meshes with the first, second, and third transfer gears 31, 32, 33, respectively. In the present embodiment, the first, second, and third shifting gears 34 , 35, 36 are all rotated synchronously with the shifting shaft core 20. And, the number of teeth of at least two of the first, second and third transmission gears 31, 32, 33 is different, and the first and the third The number of teeth of at least two of the second and third shifting gears 34, 35, 36 is different. In this embodiment, The number of teeth of the second transmission gear 32 is greater than that of the first transmission gear 31' and the number of teeth of the first transmission gear 31 is greater than the number of teeth of the third transmission gear 33; moreover, the number of teeth of the third transmission gear 36 is larger than the first transmission gear 34' The number of teeth of the first shifting gear 34 is greater than the number of teeth of the second shifting gear 35. Referring to FIGS. 1 to 5, the shifting cam assembly unit 40 includes a plurality of cams 41, 42, 43 and a plurality of spindle pawls 44, 45. And 46 and at least one shift control pawl 47, 48. The plurality of cams 41, 42, 43 and the plurality of spindle pawls 44, 45, 46 are sleeved on the drive shaft 1 , and the plurality of shafts The pawls 44, 45, 46 are synchronously rotated in conjunction with the drive shaft 1〇. The plurality of spindle pawls 44, 45, 46 are respectively accommodated in the plurality of pawl receptacles 101, 102 on the drive shaft 10, In the 103, the switch can be individually switched between a retracted position and a jacked position by the control of the rotation of the plurality of cams 41, 42, 43. Therefore, it can also be referred to as an "axis control element", which means Control element on the shaft. The at least one indexing control pawl 47, 48 is adjacent to one side of the plurality of wheel 41, 42, 43 and is capable of abutting the complex cam ΜΑ, the reverse movement of the transmission shaft 10 by the 201219260 The rotational movement relative to the drive shaft ι is controlled to control the positional switching operation of the 45, 46. Wherein, the resets ~, 45, 46 respectively have a brake tooth 441, 45 461, and the positions of the brake teeth 441, 461, 461 of the pivot pawls 44, 45, 46 correspond to the plurality of transmission gears, respectively. 3 of the 32, 33, the inner ring portions 3U, 32 of the transmission gear 3 32, 33, 33. When a shaft or pawl 44 (or 45, or 46) is in the jacking position, the jacking shaft, pawl 44 (or 45, or 46) of the brake teeth 441 (or 45 against the top) The corresponding transmission gear 31 (or 32, or the abutment recess 312 3 or 332 on the shank 311 (or 321 or 331)) will be driven by the transmission shaft 10 during forward rotation. The two-wheeled pair corresponding to the fine pawl will not be directly driven by the transmission fine 1G in the forward rotation, but the transmission and change of the complex variable gears 34, 35, 36 will be followed by the first-touch recording. 31 The rotary shaft ship is given to the drive base, for example, when the first-fine hemp 44 is recorded, his two-axis pawl 45, 46 will be in the retracted position '· at this time, 2 axis 1G In the forward direction _ Huizhi County moving the first - Chuan Lin wheel 31, into: the rotating power is transmitted to the toothed holder through the drive base 5G, the other two transmission gears 32, 33 will be in a non-transmission state. =^Pawl 45 recorded, the scale of its thin claws Jiang Hegu will be recorded _ position, · At this time, the transmission of the mixed heart will be direct (four) second pass _ round 32, (four) two records will be 12 201219260 Power transmission to mesh with it The second shifting gear 35 then transmits power to the first shifting gear 34 that rotates synchronously with the second shifting gear 35 through the shifting shaft 20, and transmits the rotational power to the first transmission gear 31 that meshes with the first shifting gear 34. , the rotary power is transmitted to the blade holder 66 via the transmission base 5, and the third transmission gear 33 is in a non-transmission state. Further, when the third spindle pawl 46 is in the jacking position, At this time, the other two axial pawls 44, 45 will be in the retracted position; at this time, the transmission shaft 10 will directly drive the third transmission gear 33 when it is rotating forward, and the third transmission gear 33 will transmit power to it. The meshed third shifting gear 36 then transmits power to the first shifting gear 34 synchronized with the third shifting gear % through the shifting shaft 20, and transmits the rotational power to the first transmission meshing with the first shifting gear 34. The gear 31, in turn, transmits the rotational power to the blade holder 66 via the transmission base 50, and at the same time, the second transmission gear 32 is in a non-transmission state. Thereby, the reverse movement by the transmission shaft 10 can be achieved. To control a certain The three-speed shifting function of the one-axis pawl 44, 45, 46 is switched to the jacking position to change the rotational speed of the output power. Please refer to Fig. 1 and Fig. 2 together with Fig. 7A, Fig. 7b and Fig. 7c. In this embodiment, the plurality of cams include a first axial fixed cam 41, a shift control cam 42, and a second axial fixed cam 43. The first and second axial fixed cams 41, 43 are fixed. Rotating on the drive shaft 1〇 and rotating therewith. The shift control cam 42 is sleeved on the drive shaft 10 in a relatively slidable manner and is clamped to the first and second shafts to the fixed cam. Between 41 and 43. The outer ring portions of the first and second axial fixed cams 、I, 43 are respectively provided with a plurality of cam blocks 411, 431 for driving the shift control pawls 47, 48 to be disengaged from the abutting projections 421. And 13 201219260, the plurality of cam blocks 4u, 431 of the first and second axial fixed cams 41, 43 have a phase difference in the rotational direction. One of the outer ring portions of the shift control cam 42 is provided with a plurality of abutting projections 421', and one of the inner ring portions of the variable floor control cam 42 is provided with a plurality of inner recessed portions 422. In the present embodiment, the number of the plurality of cam blocks 4U, 431 of the first and second axial fixed cams 41, 43 is three, and the plurality of shift control cams 42 are pressed against the bumps 421. The number of the recesses 422 is six, and the number of the plurality of recesses 422 of the shift control cam 42 is two. Please refer to Figure 1 and Figure 2 together with Figure 7A, Figure 7B and Figure 7c. In the present embodiment, the plurality of spindle pawls include a first spindle pawl 44, a second spindle pawl 45 and a third spindle pawl 46. Each of the pivot pawls 44, 45, 46 has a brake tooth 441 including the brake teeth 441, 451, 461 and a switching tooth 442, 452, 462, and an individual spindle pawl 44 (or 45, or 46) Or 451, or 461) and switching teeth 442 (or 452, or 462) are synchronously switched between the retracted position and the jacked up position. The position of the brake teeth 441 of the first spindle pawl 44 corresponds to the inner ring portion 311 of the first transmission gear 31, and the position of the second shaft pawl magic brake tooth 451 corresponds to the second transmission The inner ring portion 32 of the gear & and the position of the braking tooth 461 of the third shaft pawl 46 corresponds to the inner ring portion 33 of the third transmission gear 33. Further, the respective shaft pawls 44, 45, The positions of the switching teeth 442, 452, and 462 of the 46 are all corresponding to the inner ring of the variable measuring cam 42. When the position of the inner concave portion 422 of the control cams corresponds to a certain axial pawl When 44 (or 45, or 46) is switched to the position of the tooth 442 (or 452, or 462), the corresponding pivot pawl 44 (or 45, or 46) of the cut 201219260 (or 452, or 462) will be The corresponding recessed portion 422 is lifted up to the jacking position, thereby synchronizing the braking teeth 441 (or 45 or 461) of the corresponding spindle pawl 44 (or 45, or 46). Lift up to switch to the jacking position. In contrast, when the position of the switching tooth 442 (or 452, or 462) of a certain axis pawl 44 (or 45, or 46) does not correspond to the position of any of the inner recesses 422, the axis pawl 44 (or 45, or 46) is in the _ contraction position, and the first, second and third axis pawls 44, 45, 46 are respectively provided with an elastic element (such as a torsion, etc.) to make the second... There is a tendency to switch to the jacking position when the third shaft pawls 44, 45, 46 are not affected by an external force. A shift control pawl includes a first shift control ratchet 47 and a second variable pitch control pawl 48, and the first and second variable old pawls 47, 48 can be The minute _ is changed between the - slide button and the top 4 position. The position of the first variable groove control ratchet 47 corresponds to the outer ring portion of the first-axis fixed cam 41 and the change of the variable groove control cam 42 and the position of the first broadcast control pawl 48 corresponds to Outside the second center-fixing cam 43, the outer ring portion of the cam is tilted by the fourth (four) cams, and the first and second hard-working claws are 47 years old. The first-axis fixed cam 4: the rotation of the plurality of cam blocks 411 of the ^ portion And switching to the slip-like imitation = _ position (10) ' and 'when the first--------------------------------------------------------------------------------------------------- One of the gear control cams 42 abuts against the convex field and when the first-variable pawl 47 is in the slip position, the top red block 42 of the paving cam 42 is not caught. The second variable control pawl 48 is driven by the rotation of the plurality of cam blocks 431 of two = 15 201219260 m to be switched between the slip-off position and the top position, and when the second variable control pawl 48 bits = The second variable control pawl 48 can withstand one of the variable control cams & one against the bump 4 and the second variable control pawl 48 When it is in the slip position, it does not bear against the abutment protrusion 421 of the variation control cam 42. In the embodiment, the first and second variable groove control pawls 47, 48 are disposed in the same direction, that is, both face the cam cams 4U, 431 along the first and second axial center cams 41. The bulging direction is convexly disposed, so that the first and second shafts 4 (4) and 43 are rotated in a forward direction (in other words, the plurality of slanting projections toward the sturdy control cam 42) The direction of the 421 is convexly disposed; and the first and second control claws 47, 48 are respectively provided with - elastic members (for example, torsion springs, etc.) to enable the first and second shift control pawls 47 48 There is a tendency to switch to the top position when it is not affected by external force. In this embodiment, the plurality of cam blocks 4U, 431 provided by the outer ring portions of the first and second axial fixed cams 41, 43 cause the first and second variable slots when the drive shaft 1 is rotated forward. The control pawls 47, 48 are in a state of being mutually disengaged from the respective abutment projections 421 of the shift control cam 42 regardless of their positions in the abutment position or the disengagement position, only when the transmission shaft center 1 is reversed. A certain shift control pawl 47 (or 48) at the abutment position is caused to abut against a certain abutment projection 421 of the shift control cam 42. Moreover, only when a certain shift control pawl 47 (or 48) has abutted against a certain abutment projection 421 of the shift control cam 42 and the drive shaft center 1 继续 continues to rotate by a predetermined angle, The shift control pawl 47 (or 48) will only push the rotation of the 201219260 shift control cam 42 to cause the position of a recess 422 of the inner ring portion of the shift control cam 42 to be displaced to a certain spindle pawl 44 (or 45, or 46) switch teeth 442 (or 452, or 462) corresponding position, and thus achieve the purpose of switching, shifting operation. In addition, the plurality of inner ring portions 311, 321, 331 of the respective transmission gears 31, 32, 33 are provided with a plurality of unidirectional sliding directions against the recesses 312, 322, 332, so that the transmission shaft 1 is reversed. When turning, the first, second and third shaft pawls 44, 45, 46 are in the jacking position or the retracted position, and each of the transmission gears 31, 32, 33 abuts against the recess 312, 322, 332 are in a state of slipping each other, and only when the drive shaft 10 is rotating forward, the brake teeth 441 (or 45) of a certain spindle pawl 44 (or 45, or 46) located at the jacking position is obtained. Or 461) to abut the abutment recess 312 (or 322, or 332) of its corresponding transmission gear 31 (or 32, or 33). In other words, when the drive shaft 1〇 is reversed, only the shifting operation can be performed, and only when the drive shaft 10 is rotating forward, the input power from the drive shaft 10 is via the transmission gear 31. The drive base 50 is combined for output. Briefly, in the shift control cam 42 shown in FIG. 7β, the rotational angular position of the inner recess 422 of the inner ring portion with respect to the drive shaft 10 determines the first, second and third axial pawls. The jacking or retracting state of the brake teeth 441 (or 45 or 461) of 44, 45, 46. The position of the inner concave portion 422 is the relative of the plurality of cam 431 of the outer ring portion of the second axial fixed cam 43 and the plurality of abutting projections 421 of the shift control cam 42 and the first shift control pawl 47. The position determines the shift position of the left crank 91, or the plurality of cam blocks 411 of the first axial fixed cam 41 cooperate with the relative positions of the plurality of abutting lugs 421 and the second shift control pawl 48 to determine the right side. Crank 91 17 201219260 Shift position. The relative position ' of this fit' is to achieve the function of allowing the crank 91 to have a shifting operation at a specific position. As shown in FIG. 1 to FIG. 5, the transmission base 50 is coupled between a power output end and the plurality of transmission gears 31, 32, 33, and is driven by the first transmission gear 31 of the plurality of transmission gears. The rotational power when the drive shaft 10 is rotated forward is output to the power output end. In the present embodiment, the power output end is the tooth piece 92. As described above, the transmission gear 31 (or 32, or 33) that is rotated by the transmission shaft 10 is matched with one of the plurality of transmission gears (or 35, or 36) that meshes with the corresponding transmission gear. The rotation speed of the transmission base 5〇 can be determined, and therefore, the rotation speed of the transmission base 5G is also changed when the transmission shaft 31, 32, 33 which is rotated by the transmission shaft 10 during forward rotation changes In order to achieve the purpose of multi-speed shifting. The first fixing base 61 and the second fixing base 62 are respectively located at two ends of the transmission shaft 且 and are fixed to the crank frame 91 adjacent to the crank 91. Openings 611 and 621 and shifting shaft seats 612 and 622 are respectively provided on the first and second seats 6 and 62. The shifting shaft center 20 is disposed between the two shifting shaft seats 612 and (2) of the second fixing bracket 6 and the second fixing base 6; the two ends of the shifting shaft center 2〇 correspond to the first and second fixing bases. ^, the change of the shaft seat 6] 2, 622 are respectively provided with the needle roller 63, 64, = the variable wheel core 20 can be pivoted relative to the first and second fixed seat 6. The ball ring 65 is received in the opening 611 of the first mount 61. The base 50 is sleeved in the ball ring & the base 5 of the drive base 5 is rotatable, and one end of the drive base 5 is protruded from the fixed seat 61. The side of the second fixing seat 62 is outside. The lens holder 201219260 is disposed on the side of the first fixing base 61 away from the second fixing base 62 and is coupled to the driving base 5 〇 and can be driven to rotate: wherein the tooth piece 92 is fixed On the tooth holder mount 66. The at least one support post 67 is coupled between the first and second mounts μ, 62 for enhancing structural strength. In this embodiment, the number of support columns is two, but it may be other numbers. The drive shaft 1 is threaded into the drive base 5 相对 in a relatively rotatable manner. One end of the transmission shaft 10 protrudes out of the opening of the first fixing base 61, and the other end protrudes out of the opening 621 of the second fixing base 62, and the two ends of the transmission shaft 10 are respectively Combined with the two cranks 91. In addition, the drive shaft ίο corresponds to the opening 621 of the second fixing base 62 and is provided with a bead bowl 681 and a jade 682. The embodiment of the above-described reverse stepped multi-speed shift internal transmission of the present invention is mainly based on the pawls (especially the spindle pawls 44, 45, 46) disposed in the receiving grooves provided on the drive shaft. As the axis control element, the positional switching of the pawl (for example, the jacking position or the retracted position) can be used to determine which transmission gear will be rotated by the transmission shaft during forward rotation, thereby achieving multi-step shifting. Features. However, in another embodiment, the multi-step shifting transmission of the present invention can also replace at least one "key" in the accommodating groove provided on the transmission shaft to replace the aforementioned pawl. As the axis control element, the position of the at least one "key" (that is, the axis control element) in the axial direction can also be switched to determine which transmission gear will be rotated by the drive shaft during forward rotation. In turn, the multi-step shifting function can also be achieved. In the embodiment where at least one "key" is used as the axis control element, the plurality of cams of the present invention may include: 201219260 at least - the axis fixed cam and the control cam; the control cam is a The sleeve can be sleeved on the drive shaft and interlocked with the at least one "key" (that is, the shaft control element), and the cam shape on the shift control cam can be used to control the "key" The position of the "axial displacement" is switched on the drive shaft. As for the other elements in the embodiment, such as the shifting shaft center, the shifting gear unit, the transmission base, and the like, the same or similar techniques as those of the foregoing embodiment are used, so the details are not described. Nine A, Figure IX B, Figure IX C, and Figure 10. 9A, FIG. 9B, and FIG. 9C are respectively the other of the first axial fixed cam 41a, the shift control cam 42a and the second axial fixed cam 43a of the reverse multi-segment variable transmission in the present invention. Side view of an embodiment. Fig. 10 is a combined view (without the steel ball 426) when the first axial fixed cam 41a, the shift control cam 42a and the second axial fixed cam 43a are sleeved on the drive shaft 1〇. The structure and function of the first axial fixed cam 41a, the shift control cam 42a and the second axial fixed cam 43a in this embodiment are substantially similar to those shown in the circle A, FIG. 7B and FIG. The only difference is that the first axial fixed cam 41a and the second axial fixed cam 43a shown in FIG. 9A, FIG. 9B and FIG. The arcuate chutes 415, 435; and the front end of any one of the arcuate chutes 415 of the first axially fixed cam 41a in a forward direction corresponds to the corresponding 51 chute of the second axial fixed cam 43a The end of 435. In addition, at the position of the two ends of each of the arcuate chutes 415, 435, at least one round hole 425' is disposed on the shift control cam 42a, and a steel ball 426 is respectively disposed in each of the circular holes 425. . 20 201219260 The diameter of the steel ball 426 is equivalent to or slightly smaller than the inner diameter of the circular hole. Similarly, in the embodiment, the first and second axial fixed cams, 43a are fixed on the transmission shaft 10 and rotate in conjunction therewith; and the variable control cam 4 is slidable relative to each other. The method is sleeved on the drive shaft ίο and is sandwiched between the first and second axial fixed cams 41a, 43a. The outer ring portions of the first and second axial fixed cams 41a, 43a are respectively provided with a plurality of cam blocks 411, 431 for driving the variable groove control pawls 47, 48 to be disengaged from the abutting projections 421. Further, the plurality of cam blocks 4U, 431 of the first and second axial fixed cams 41a, 43a have a phase difference in the rotational direction. One of the outer ring portions of the shift control cam 42a is provided with a plurality of abutting projections 421', and the inner ring portion of one of the shift control cams 42 is provided with a plurality of inner recessed portions 422. Since the shift cam assembly 40 shown in FIG. 1 is engaged with the first, first and second pivot pawls 44, 45, 46, any of the pivot pawls 44, 45, 46 From the angle of opening (topping) to closing (retracting), there is an unstable zone in this section, and this unstable zone may cause air play. In order to eliminate such an unstable region, the present invention is particularly useful in the embodiments shown in FIGS. 9A, 9B, 9C, and 10, by the arcuate chutes 415, 435 and in the circular holes. The cooperation of the steel balls 426 in 425 constitutes an additional ball mechanism. When the shift control cam 42a slides relative to the first and second axial fixed cams 41a, 43a, the steel balls 426 can slide in the arc chutes 415, 435 until reaching the end of the chutes 415, 435 After that, the steel balls 426 will abut against the first and second axial fixed cams 41a, 43a. In addition, when the shift control cam 42a continues to rotate, the steel ball 426 will break through the arc chute 415 to the chute 201219260 435, and the other steel ball 426 will break through the arc chute 435 to the chute 415, thus, The steel ball 426 is pushed and pushed by the sliding grooves 415, 435. This interactive push-through process assists the pivot pawls 44, 45, 46 in a quick opening and closing action. The shift control cam 42a cannot be stabilized during the pushing process to evade any of the internal shaft pawls, 45, 46 opening and closing joints, thereby eliminating the blurring interval of the shifting process. In this way, in the process of switching gears, the phenomenon that the pawls collide can be avoided, not only in the shifting, there is no more neutral phenomenon, but also whether the user can feel the reverse stepping after shifting. The function of the feedback device for shifting. As described above, in the present embodiment, the positions of the circular holes 425 need to be relative to the features of the plurality of concave portions 422 provided in the inner ring portion of the variable control cam 42 so that the first, second, and third portions are provided. The pivot pawls 44, 45, 46 can be smoothly opened or closed at the correct angle (this angle is the position corresponding to the inner recess 422). Also, the positions of the chutes 415, 435 are relative to the positions of the circular holes 425 such that the first, second and third axial pawls 44, 45, 46 cannot be positioned in the open and closed shifting process regions. The above-mentioned embodiments are not intended to limit the scope of application of the present invention. The scope of protection of the present invention is intended to be based on the technical spirit defined by the content of the invention and the scope of its equivalent changes. It is to be understood that the scope of the present invention is not limited by the spirit and scope of the present invention. s 22 201219260 [Simple description of the drawings] The first embodiment is a three-dimensional exploded view of a preferred embodiment of the multi-stage shifting internal transmission of the present invention. Fig. 2 is a perspective exploded view of the preferred embodiment of the reverse stepped multi-speed shifting internal transmission of the present invention in a second viewing angle. Figure 3 is a right side elevational view of the preferred embodiment of the reverse stepped multi-speed shifting internal transmission of the present invention in a combined state. Figure 4 is a cross-sectional view of the A-A (including the crank and the teeth) shown in Figure 3. Fig. 5 is a perspective view of the reverse shifting multi-stage shifting internal transmission in the combined state of the present invention (excluding the bead bowl, the jade and the second fixing seat). 6A, 6B, and 6C are side views of the first, second, and third transfer gears of the reverse step multi-step shifting gear of the present invention, respectively. 7A, 7B and 7C are side views of the first axial fixed cam, the shift control cam and the second axial fixed cam of the reverse step multi-step shifting gear of the present invention, respectively. Figures 8A, 8B and 8C are perspective views, respectively, of the first, second and third axial pawls of the inverted stepped multi-speed shifter of the present invention. 9A, 9B and 9C are side views respectively showing another embodiment of the first axial fixed cam, the shift control cam and the second axial fixed cam of the reverse step multi-step shifting gear of the present invention. Figure 10 is a combined view of the first axial fixed cam, the shift control cam and the second axial fixed cam shown in Figures 9Α, 9Β and 9C on the drive shaft (not included) Steel ball 23 201219260 [Description of main components] 1 to the multi-step shifting internal transmission 10 to the drive shaft 101, 102, 103 to the pawl housing 20 to the shifting shaft 30 to the shifting gear unit 31 to The first transmission gear 31, 321 and 331 to the inner soil 312, 322, 332, the abutment recess 313 to the block 32 to the second transmission gear 33 to the third transmission gear 34 to the first transmission gear 35 to the second transmission Gear 36 to third shifting gear 40 to shifting cam group unit 41, 41a to first axial fixed cam 41 431 to cam block 42, 42a to variable building control cam 415, 435 to chute 421 to top bump 422 to inner concave portion 425 to round hole 426 to steel ball 43, 43a to second axial fixed cam 44 to first axial pawl 45 to second axial pawl 46 to third axial pawl 441, 451, 461 ~ Brake teeth 442, 452, 462 ~ switching teeth 47 ~ first shift control pawl 48 ~ The second change groove control pawl 50 - the drive base 501 - the groove 61 - the first fixed seat 611, 621 - the opening 612, 622 - the shift shaft seat 62 - the second fixed seat 63, 64 - the needle pin Palin 65~ Ball ring 24 201219260 66~ tooth holder 681 ~ bead bowl 91 ~ crank 67 ~ support column 682 ~ jade 92 ~ tooth 25