201219679 六、發明說明： 【發明所屬之技術領域】 本發明係關於一種同軸式凸輪變速機構，特別是關 於一種藉由第一、第二共軛凸輪組以及滚子輪組與行星 架來構成具有多種輸入/輸出傳動方式之同軸式凸輪變 速機構。 【先前技術】 傳動機構(transmission mechanism)是用來改變或者 調節各種機器設備或動力機器設備之輸出轉速的一種 媒介機構，其也是構成變速箱不可或缺的機構，在許多 生産、加工、製造及運輸用的動力機械内都具有不同之 傳動機構與變速箱的設計。例如，在汽車或機車内，通 常會在引擎及車輪之間設置具有傳動機構之變速箱，以 進行減速或增速，使引擎能藉由傳動機構的調速來輸出 具適當轉速之動力驅動車輪轉動。現有的傳動機構大多 使用普通齒輪相互傳動調速，另也有使用行星齒輪或凸 輪來相互傳動調速的設計。 舉例來說，美國公告第5,247,847號發明專利揭示一 種凸輪齒輪組合構造(Cam Gear Assembly)，其使用一凸 輪齒輪（cam gear)與一滾子齒輪(roller gear)相互搭配， 因此屬於一種行星齒輪傳動式之傳動機構。 再者，美國公告第6,902,507號發明專利揭示一種滾 子凸輪組合構造(Roller Cam Assembly)，其使用一滾子 201219679 轉環(roller ring)與一個凸輪齒輪相互搭配，因此屬於另 一種行星齒輪傳動式之傳動機構。 另外，美國公告第2,986,949號發明寻利揭示一種分 度凸輪構造(Indexing Cam Structure)，其使用一組共軛 凸輪與一組具數個從動件（follower)之轉輪相互搭配，因 此屬於一種凸輪傳動式之傳動機構。201219679 VI. Description of the Invention: The present invention relates to a coaxial cam shifting mechanism, and more particularly to a configuration by a first and a second conjugate cam set and a roller wheel set and a carrier A variety of input/output transmission type coaxial cam shifting mechanisms. [Prior Art] A transmission mechanism is a medium mechanism for changing or adjusting the output rotational speed of various machine equipment or power equipment, and is also an indispensable mechanism for constructing a gearbox, in many production, processing, manufacturing, and The power machinery for transportation has different transmission mechanisms and gearbox designs. For example, in a car or a locomotive, a gearbox with a transmission mechanism is usually provided between the engine and the wheel for deceleration or speed increase, so that the engine can output the power with the appropriate speed by the speed regulation of the transmission mechanism. Turn. Most of the existing transmission mechanisms use common gears for mutual drive speed regulation, and there are also designs that use planetary gears or cams to drive speed adjustments. For example, U.S. Patent No. 5,247,847 discloses a Cam Gear Assembly which uses a cam gear and a roller gear to match each other and thus belongs to a planetary gear transmission. Type of transmission mechanism. Further, U.S. Patent No. 6,902,507 discloses a Roller Cam Assembly which uses a roller 201219679 roller ring to be matched with a cam gear, and thus belongs to another planetary gear transmission type. Transmission mechanism. In addition, U.S. Patent No. 2,986,949 discloses an indexing cam structure that uses a set of conjugate cams to mate with a set of runners having a plurality of followers, and thus belongs to a type Cam-driven transmission mechanism.
此外，美國公告第6,382,038號發明專利揭示一種傳 動裝置(Transmission Device)，其使用一組共輕齒輪與 一個具二凸輪板之轉軸相互搭配，因此屬於一種齒輪與 凸輪複合傳動式之傳動機構。 上述各種現有傳動機構皆具有減速或增速的作用， 但若要達成較高之減速或增速比，則其機構尺寸將會過 於龐大’且若使用齒輪與齒輪相互响合之作動方气則必 然在二齒輪的凸齒之間產生背隙誤差及容易磨損等問 題’因而不利於應用在高精密動力機械中進行高精产^ 傳動。再者，上述各種現有傳動機構僅具有單—種^力 輸入端及動力輸出端之設計，無法在相同構造下提供不 同動力輸入端及動力輸出端的選擇，因而相對限縮其了 應用的範圍。 、β 故，仍有必要提供一種改良式傳動機構，以解決习 用技術所存在的問題。 【發明内容】 本發明之主要目的在於提供一種同軸式凸輪變速機 5 201219679 構，其係藉由第一、第二共軛凸輪組以及滾子輪組與行 星架的相互搭配，以構成多種輸入/輸出傳動方式以供 選擇使用，因而有利於增加傳動機構之應用多樣性。 本發明之次要目的在於提供一種同軸式凸輪變速機 構，其中上述第一共軛凸輪組、第二共軛凸輪組及滾子 輪組之間的組裝沒有傳統齒輪與齒輪之間因相互喃合 而產生的背隙及磨損問題，因而有利於應用在高精度動 力機械的動力傳動，以提升傳動機構之耐磨損強度與傳 動精度。 本發明之另一目的在於提供一種同軸式凸輪變速機 構，其中可依傳動需求選擇調整第一凸輪及第二凸輪的 鈍凸齒數比例，以設計出適當的減速或增速比例，因而 有利於應用在高負載、高扭力輸出之動力機械内，以增 加傳動機構之負載承受強度及扭力輸出值。 本發明之又一目的在於提供一種同轴式凸輪變速機 構，其中上述第一共軛凸輪組、第二共軛凸輪組及滾子 輪組之構造相對簡單，且容易變更設計成不同尺寸或不 同凸輪面形狀，因而有利於降低製造成本及增加組件設 計裕度。 為達上述之目的，本發明提供一種同轴式凸輪變速 機構，其包含：一第一傳動軸；一第一共軛凸輪組，與 該第一傳動軸同步轉動，並具有至少二共輛結合之第一 凸輪，該第一凸輪各具有一第一凸輪面；一第二共輛凸 輪組，環設於該第一共軛凸輪組之外圍，並具有至少二 201219679 共軛結合之第二凸輪，該第二凸輪各具有一第二凸輪 面，該第二凸輪面分別對應於該第一凸輪面；至少一滾 子輪組，各具有至少二滾子輪，該滚子輪各具有數個滚 子，該滾子輪分別夾設於該第一及第二凸輪面之間，並 在該第一及第二凸輪面之間被動進行轉動；至少一行星 架，各自可轉動的樞接支撐該滚子輪組；以及一第二傳 動軸，與該行星架同步轉動。 在本發明之一實施例中，該第一凸輪、該第二凸輪 及該滾子輪之數量彼此相等。 在本發明之一實施例中，各該行星架具有一第一支 架及一第二支架，該第一支架之兩端分別可轉動的樞接 於該第一傳動軸及該滾子輪組之一側；該第二支架之一 端可轉動的樞接該滾子輪組之另一侧，及其另一端與該 第二傳動軸同步轉動。 在本發明之一實施例中，各該滚子輪組另包含數個 轉動盤，其與該數個滾子共同構成該至少二滚子輪。 在本發明之一實施例中，各該滾子輪組另包含一旋 轉軸，其中該至少二滚子輪可轉動的設於該旋轉軸上， 且該旋轉軸之二端分別樞接於該行星架之第一及第二 支架。 在本發明之一實施例中，該第一傳動轴用以做為一 動力輸入端，該第二傳動軸用以做為一動力輸出端，及 該第二共輛凸輪組用以做為一固定端。該動力輸出端與 該動力輸入端之一傳動速度比等於N1/(N1+N2)，其中 201219679 N1為該第一凸輪面之鈍凸齒數，N2為該第二凸輪面之 純凸齒數。 在本發明之一實施例中，該第二傳動軸用以做為一 動力輸入端，該第一傳動軸用以做為一動力輸出端，及 該第二共軛凸輪組用以做為一固定端。該動力輸出端與 該動力輸入端之一傳動速度比等於(N1+N2)/N1，其中 N1為該第一凸輪面之鈍凸齒數，N2為該第二凸輪面之 純凸齒數。 在本發明之一實施例中，該第一傳動軸用以做為一 動力輸入端，該第二共軛凸輪組用以做為一動力輸出 端，及該第二傳動轴用以做為一固定端。該動力輸出端 與該動力輸入端之一傳動速度比等於N1/N2，其中N1 為該第一凸輪面之鈍凸齒數，N2為該第二凸輪面之鈍 凸齒數。 在本發明之一實施例中，該第二傳動轴用以做為一 動力輸入端，該第二共軛凸輪組用以做為一動力輸出 端，及該第一傳動轴用以做為一固定端。該動力輸出端 與該動力輸入端之一傳動速度比等於(Nl+N2)/N2,其中 N1為該第一凸輪面之鈍凸齒數，N2為該第二凸輪面之 純凸齒數。 在本發明之一實施例中，該第二共軛凸輪組用以做 為一動力輸入端，該第二傳動軸用以做為一動力輸出 端，及該第一傳動轴用以做為一固定端。該動力輸出端 與該動力輸入端之一傳動速度比等於N2/(N1+N2)，其 201219679 中N1為該第一凸輪面之鈍凸齒數，N2為該第二凸輪面 之純凸齒數。 ； 在本發明之一實施例中，該第二共輛凸輪組用以做 為一動力輸入端，該第一傳動軸用以做為一動力輸出 端，及該第二傳動轴用以做為一固定端。該動力輸出端 與該動力輸入端之一傳動速度比等於N2/N1，其中N1 為該第一凸輪面之鈍凸齒數，N2為該第二凸輪面之鈍 凸齒數。 【實施方式】 為了讓本發明之上述及其他目的、特徵、優點能更 明顯易懂，下文將特舉本發明較佳實施例，並配合所附 圖式，作詳細說明如下。再者，本發明所提到的方向用 語，例如「上」、「下」、「前」、「後」、「左」、「右」、「内」、 「外」或「側面」等，僅是參考附加圖式的方向。因此， 使用的方向用語是用以說明及理解本發明，而非用以限 制本發明。 請參照第1及2圖所示，本發明第一實施例之同軸 式凸輪變速機構係可應用在各種動力機械、汽車、機車 或其他動力機械内，以做為變速箱或其他減速/增速用 之機構，以便在一動力輸入端及一動力輪出端之間提供 適當的減速/增速功能。本發明第一實施例之同軸式凸 輪變速機構主要包含：一第一傳動軸1、一第一共輛凸 輪組2、一第二共軛凸輪組3、至少一滾子輪組4、至 201219679 少一行星架5及一第二傳動軸6。本發明將於下文利用 第1至8圖逐一詳細說明第一實施例之上述各元件的細 部構造及其運作原理。 請參照第1、2及3圖所示，本發明第一實施例之第 一傳動軸1係由金屬或合金製成之軸桿，其中該第一傳 動軸1之一端（外端）依產品設計需求可選擇做為一動力 輸入端、一動力輸出端或一固定端，以及該第一傳動軸 1之另一端（内端）固定結合在該第一共軛凸輪組2之幾 何中心位置處，以便使該第一傳動軸1與第一共輕凸輪 組2能同步轉動。 請再參照第1、2及3圖所示，本發明第一實施例之 第一共軛凸輪組2係與該第一傳動軸1同步轉動，且依 產品設計需求可選擇該第一傳動轴1帶動該第一共軛 凸輪組2轉動，或者是由該第一共軛凸輪組2帶動該第 一傳動軸1轉動。再者，該第一共輛凸輪組2具有至少 二共軛結合之第一凸輪21、22，該第一凸輪21、22係 由金屬或合金製成之凸輪板，其彼此固定連結成一體且 能同步轉動，因此稱之為“共軛結合”。在本實施例中， 該第一凸輪21、22之數量為二個，但亦可能是三個或 以上。該第一凸輪21、22各具有一第一凸輪面211、 221，其分別是一個相似於鈍凸齒狀、波浪狀或花瓣狀 的外周面，其彼此具有相同的構形。同時，該至少二第 一凸輪面211、221彼此的鈍凸齒狀區段是呈相互交錯 排列的關係，其中一個該第一凸輪面211之鈍凸齒狀區 201219679 * t會對應到另—該第—凸輪面221 鈍凹槽狀區 . 而該第一凸輪面211之純凹槽狀區段也會對應到另 一該第一凸輪面221之一鈍凸齒狀區段。 料參照第1、2及4圖所示，本發明第一實施例之 第二共輛凸輪組3係環設於該第-共輛凸輪組2之外 圍’該第三共輛凸輪組3具有至少二共減合之第二凸 ，31、32 ’該第二凸輪3卜32係由金屬或合金製成之 φ 環體，其彼此固定連結成一體且能同步轉動，因此稱之 為共軛結合”。在本實施例中，該第二凸輪31、32之 數量對應於該第一凸輪21、22，且同樣為二個，但亦 可能是三個或以上。該第二凸輪31、32各具有一第二 凸輪面311、321，其分別是一個相似於鈍凸齒狀、波 浪狀或钯辦狀的内周面，其彼此具有相同的構形。同 時，该至少二第二凸輪面311、321彼此的鈍凸齒狀區 段也是呈相互交錯排列的關係，其中一個該第二凸輪面 _ 311之純凸齒狀區段會對應到另一該第二凸輪面321之 鈍凹槽狀區段，而該第二凸輪面311之鈍凹槽狀區段 也會對應到另一該第二凸輪面321之一鈍凸齒狀區段。 凊再參照第1、2及5圖所示，本發明第一實施例之 ' 至夕一滾子輪組4各具有至少二滾子輪41及一旋轉軸 42，兩者皆係由金屬或合金製成，其中該滾子輪41之 數量係對應等於該第一凸輪21、22及該第二凸輪31、 32之數量’各該滾子輪41包含數個滾子々η及數個轉 動盤412。在本實施例中’該滾子輪組4具有二該滾子 201219679 輪41，各該滚子輪41的滚子411之數量為3個，且該 二滾子輪41共用三個轉動盤412。每一該滾子411皆 是可轉動的等角度排列及樞接於二相鄰該轉動盤412 之間。再者，該至少二滚子輪41係可轉動的設於同一 該旋轉軸42上，該旋轉軸42之二端則分別樞接於該行 星架5上。該滚子輪41及其滾子411分別夾設於該第 一共軛凸輪組2之第一凸輪面211、221及該第二共軛 凸輪組3之第二凸輪面311、321之間，並在該第一凸 輪面211、221及該第二凸輪面311、321之間被動的進 行轉動。另外，該至少二滾子輪41彼此的滾子411也 是呈相互交錯排列的關係，其交錯排列關係對應與該第 一凸輪面211、221以及該第二凸輪面321、322之鈍凸 齒狀區段及鈍凹槽狀區段的交錯排列關係。 請再參照第1、2及6圖所示，本發明第一實施例之 至少一行星架5係用以可轉動的樞接支撐該滚子輪組4 的旋轉軸42與滾子輪41，其中各該行星架5具有一第 一支架51及一第二支架52,兩者皆係由金屬或合金製 成，其中該第一支架51之一第一端511及一第二端512 分別可轉動的柩接於該滚子輪組4之一侧（亦即該旋轉 軸42之一端）及該第一傳動軸1，其中該第二端512較 佳可利用一軸承（未繪示）可轉動的樞接於該第一傳動 軸1 ;同時，該第二支架52之一第一端521可轉動的 樞接該滾子輪組4之另一側（亦即該旋轉軸42之另一 端），及其一第二端522固定結合於該第二傳動軸6並 12 201219679 且可與該第二傳動軸6同步轉動。 請參照第7及8圖所示，其揭示本發明第一實施例 之同軸式凸輪變速機構之簡要操作示意圖。如第1、2、 7及8圖所示，在本實施例中，本發明係定義該第一傳 動軸1做為一動力輸入端，定義該第二傳動軸6做為一 動力輸出端，及定義該第二共軛凸輪組3做為一固定 端。當該第一傳動軸1接受一外部機構(例如引擎之曲 軸）的帶動而逆時針轉動時，由於該第一傳動軸1固定 結合於該第一共軛凸輪組2(如第1圖所示），因此該第 一共軛凸輪組2將與該第一傳動軸1同步逆時針轉動。 接著，該第一共軛凸輪組2之二第一凸輪21、22在轉 動時利用該二第一凸輪面211、221抵推該滚子輪組4 之二滾子輪41的各三個滾子411。如此，該滾子411 可在該二第一凸輪面211、221與該第二共軛凸輪組3 之二第二凸輪面311、321之間各自進行順時針轉動， 並沿著該二第二凸輪面311、321進行逆時針行星運 動，且可同步推動該轉動盤412逆時針轉動。隨後，該 滾子輪組4即可經由該轉動盤412及旋轉軸42來推動 該行星架5另一側之第二支架52逆時針轉動。由於該 第二支架52之第二端522固定結合於該第二傳動軸6, 因此該第二傳動軸6將可同步逆時針轉動，以經由該第 二傳動軸6驅動另一外部機構(例如車輪）以調整後的轉 速進行轉動。 值得注意的是，該動力輸出端（該第二傳動軸6)與該 13 201219679 動力輸入端（該第一傳動轴1)之一傳動速度比等於 N1/(N1+N2)，其中N1為該第一凸輪面211、221之鈍 凸齒數，N2為該第二凸輪面311、321之鈍凸齒數。例 如，在第5及6圖之參考例中，該第一凸輪面211、221 之鈍凸齒數為各6個，及該第二凸輪面311、321之鈍 凸齒數為各9個，因此由該動力輸入端（該第一傳動軸 1)將動力傳遞至該動力輸出端（該第二傳動軸6)後之速 度將變為原轉速的6/(6+9)，也就是該傳動機構屬於一 種減速傳動設計。 另外，在其他實施例中，本發明亦可能定義該第二 傳動軸6做為一動力輸入端，定義該第一傳動軸1用以 做為一動力輸出端，及定義該第二共軛凸輪組3做為一 固定端。此時，該動力輸出端（該第一傳動軸1)與該動 力輸入端（該第二傳動軸6)之一傳動速度比將變成相 反，也就是(N1+N2)/N1，其中N1為該第一凸輪面211、 221之鈍凸齒數，N2為該第二凸輪面311、321之鈍凸 齒數，例如，在第5及6圖之參考例中，其傳動速度比 是（6+9)/6，因而使該傳動機構成為一種增速傳動設 計。 再者，本發明亦可能定義該第一傳動軸1做為一動 力輸入端，定義該第二共軛凸輪組3做為一動力輸出 端，及定義該第二傳動軸6做為一固定端。此時，該動 力輸出端（該第二傳動轴6)與該動力輸入端（該第一傳動 軸1)之一傳動速度比N1/N2，其中N1為該第一凸輪面 14 201219679 211、221之鈍凸齒數，N2為該第二凸輪面311、321 之鈍凸齒數，例如，在第5及6圖之參考例中，其傳動 速度比是6/9,因而使該傳動機構成為一種減速傳動 設計。 或者，本發明亦可能定義該第二傳動軸6做為一動 力輸入端，定義該第二共軛凸輪組3做為一動力輸出 端，及定義該第一傳動轴1做為一固定端。此時，該動 力輸出端（該第二共軛凸輪組3)與該動力輸入端（該第二 傳動軸6)之一傳動速度比(Nl+N2)/N2,其中N1為該第 一凸輪面211、221之鈍凸齒數，N2為該第二凸輪面 311、321之鈍凸齒數，例如，在第5及6圖之參考例 中，其傳動速度比是(6+9)/9，因而使該傳動機構成為 一種增速傳動設計。 另外，本發明亦可能定義該第二共軛凸輪組3做為 一動力輸入端，定義該第二傳動軸6做為一動力輸出 端，及定義該第一傳動轴1做為一固定端。此時，該動 力輸出端（該第二傳動軸6)與該動力輸入端（該第二共軛 凸輪組3)之一傳動速度比N2/(N1+N2)，其中N1為該 第一凸輪面211、221之鈍凸齒數，N2為該第二凸輪面 311、321之鈍凸齒數，例如，在第5及6圖之參考例 中，其傳動速度比是9/(6+9)，因而使該傳動機構成為 一種減速傳動設計。 此外，本發明亦可能定義該第二共軛凸輪組3做為 一動力輸入端，定義該第一傳動軸1用以做為一動力輸 15 201219679 出端，及定義該第二傳_6做為 :力輸出端(該第一傳動轴,與該動力輸入:二= =輪組3)之—傳動速度比似m，其中 凸輪面叫、功之純凸齒數，N2為該第二凸輪面^一 ^之純凸齒數，例如，在第5及6圖之參 傳動速度比是9/6，ra而/* # & τ 其 傳動設計。Α因而使該傳動機構成為一種增速 :參照第9圖所不’其揭示本發明第二實施例之 :式凸輪:速機構之簡要操作示意圖，其 施 例相似於本發明第—實施 =施 時參照第1及J該第 構包含三個滾子…例之同轴式凸輪變速機 =施例之同軸式凸輪變速機構僅包含—個滾子輪組第 * 固订星架5。該第二實施例藉由增加該滾子輪组* ^星架5之對應組數到二個、三個或以上，可以相對 二==輪變速機構在進行減速或增速等傳動 期間之傳動穩疋性與可靠度。 及Λ上Ζ述，相較於各種現有傳動機構具有背隙誤差 〜tif ^其通常❹單一種動力輸入/輸出 s又计等缺點，第1至8圖之本發明藉由第-、第二丘輛 m2、3以及滾子輪組4與行星架5的相互搭配， =構成多種輸入/輸出傳動方式以供選擇使用，因而有 利於增加傳動機構之應用多樣性。再者，上述第一 201219679 凸輪組2、筮-崖心„ 沒有錢子齡4之w的組裝 磨損問題，因而有痛相/嘴合而產生的背隙及 動，以提;應用在鬲精度動力機械的動力傳 t二==之耐磨損強度與傳動精度。另外，. 二凸輪3i、32 Γ選擇調整該第—凸輪21、22及第 或择速m 顿凸餘比例’以設計出適當的減速 .θ ，因而有利於應用在高負載、古杻力耠出$ 動力機械内，以描上/;fe 知门貝戰冋扭力輸出之 出值。此外，上^ 構之貞載承受強度及扭力輸 3及滾子輪也4之描—共輛凸輪組2、第二共輛凸輪組 同尺寸或5之構造相對簡單，且容易變更設計成不 及增加組狀，因而也有利於降低製造成本 告·ι^Γ本發明已以較佳實施例揭露’然其並非用以限 之籍袖^々任何熟習此項技藝之人士，在不脫離本發明 之佯1一範圍内，當可作各種更動與修飾，因此本發明 保濩乾圍當視後附之申請專利範圍所界定者為準。 【圖式簡單說明】 之:合Li圖本發明第-實施例之同軸式凸輪變速機構 之分解立:圖本發明第一實施例之同軸式凸輪變速機構 輛凸於έ且夕民本發明第一實施例之第一傳動轴與第一共 輪、、且之局部放大圖。 17 201219679 第4圖：本發明第一實施例之第二共輛凸輪組之局 部放大圖。 第5圖：本發明第一實施例之滾子輪組之局部放大 圖。 第6圖：本發明第一實施例之行星架及第二傳動軸 之局部放大圖。 第7及8圖：本發明第一實施例之同軸式凸輪變速 機構之簡要操作示意圖。 第9圖：本發明第二實施例之同軸式凸輪變速機構 之簡要操作示意圖。 【主 要元件符號說明】 1 第 一傳動軸 2 第一共軛凸輪組 21 第 一凸輪 211 第一凸輪面 221 第 一凸輪面 22 第一凸輪 3 第 二共輛凸輪組 31 第二凸輪 311 第 二凸輪面 32 第二凸輪 321 第二凸輪面 4 滾子輪組 41 滾子輪 411 滾子 412 轉動盤 42 旋轉軸 5 行星架 51 第一支架 511 第 一端 512 第二端 52 第二支架 521 第一端 522 第 二端 6 第二傳動轴 18In addition, U.S. Patent No. 6,382,038 discloses a transmission device that uses a set of common light gears to mate with a rotating shaft having two cam plates, and thus belongs to a gear and cam combined transmission type transmission mechanism. All of the above-mentioned existing transmission mechanisms have the function of decelerating or increasing the speed. However, if a higher deceleration or speed increase ratio is to be achieved, the size of the mechanism will be too large, and if the gears and the gears are used to make a mutual sound, then It is inevitable that there will be problems such as backlash error and easy wear between the convex teeth of the two gears, which is not conducive to the application of high-precision transmission in high-precision power machinery. Moreover, the above various conventional transmission mechanisms have only a single type of force input end and a power output end design, and cannot select different power input ends and power output ends in the same structure, thereby relatively narrowing the scope of application. Therefore, it is still necessary to provide an improved transmission mechanism to solve the problems of conventional technology. SUMMARY OF THE INVENTION The main object of the present invention is to provide a coaxial cam gear transmission 5 201219679 structure, which is composed of first and second conjugate cam sets and a roller wheel set and a carrier to form a plurality of inputs. / Output drive mode for optional use, thus contributing to increased application diversity of the transmission mechanism. A secondary object of the present invention is to provide a coaxial cam shifting mechanism in which the assembly between the first conjugate cam group, the second conjugate cam group and the roller wheel set is free of compositing between the conventional gear and the gear The resulting backlash and wear problems are beneficial to the power transmission of high-precision power machinery to improve the wear resistance and transmission accuracy of the transmission mechanism. Another object of the present invention is to provide a coaxial cam shifting mechanism in which the ratio of the number of blunt teeth of the first cam and the second cam can be adjusted according to the transmission demand, so as to design an appropriate ratio of deceleration or speed increase, thereby facilitating application. In the high-load, high-torque output power machine, to increase the load bearing strength and torque output value of the transmission mechanism. It is still another object of the present invention to provide a coaxial cam shifting mechanism in which the first conjugate cam group, the second conjugate cam set and the roller wheel set are relatively simple in construction and are easily designed to be different in size or different. The shape of the cam surface is thus advantageous in reducing manufacturing costs and increasing component design margin. In order to achieve the above object, the present invention provides a coaxial cam shifting mechanism including: a first transmission shaft; a first conjugate cam set that rotates synchronously with the first transmission shaft and has at least two common axle combinations a first cam, each of the first cams has a first cam surface; a second common cam set, disposed at a periphery of the first conjugate cam group, and having at least two second ridges of conjugated combination of 201219679 The second cams each have a second cam surface corresponding to the first cam surface; at least one roller wheel set each having at least two roller wheels, each of the roller wheels having a plurality of Roller, the roller wheels are respectively disposed between the first and second cam faces, and passively rotate between the first and second cam faces; at least one planet carrier, each of which is pivotable support The roller wheel set; and a second drive shaft rotate in synchronization with the carrier. In an embodiment of the invention, the number of the first cam, the second cam, and the roller wheel are equal to each other. In an embodiment of the present invention, each of the planet carriers has a first bracket and a second bracket, and the two ends of the first bracket are pivotally coupled to the first transmission shaft and the roller wheel set respectively. One side of the second bracket is pivotally connected to the other side of the roller set, and the other end thereof rotates synchronously with the second transmission shaft. In one embodiment of the invention, each of the roller wheel sets further includes a plurality of rotating disks that together with the plurality of rollers constitute the at least two roller wheels. In an embodiment of the present invention, each of the roller sets further includes a rotating shaft, wherein the at least two roller wheels are rotatably disposed on the rotating shaft, and the two ends of the rotating shaft are respectively pivotally connected to the rotating shaft The first and second brackets of the planet carrier. In an embodiment of the invention, the first transmission shaft is used as a power input end, the second transmission shaft is used as a power output end, and the second common cam group is used as a power input end. Fixed end. A transmission speed ratio of the power output end to the power input end is equal to N1/(N1+N2), wherein 201219679 N1 is the number of blunt teeth of the first cam surface, and N2 is the number of pure convex teeth of the second cam surface. In an embodiment of the invention, the second transmission shaft is used as a power input end, the first transmission shaft is used as a power output end, and the second conjugate cam group is used as a power input end. Fixed end. A transmission speed ratio of the power output end to the power input end is equal to (N1 + N2) / N1, wherein N1 is the number of blunt teeth of the first cam surface, and N2 is the number of pure convex teeth of the second cam surface. In an embodiment of the invention, the first transmission shaft is used as a power input end, the second conjugate cam group is used as a power output end, and the second transmission shaft is used as a power transmission end. Fixed end. A transmission speed ratio of the power output end to the power input end is equal to N1/N2, wherein N1 is the number of blunt teeth of the first cam surface, and N2 is the number of blunt teeth of the second cam surface. In an embodiment of the invention, the second transmission shaft is used as a power input end, the second conjugate cam group is used as a power output end, and the first transmission shaft is used as a power transmission end. Fixed end. A transmission speed ratio of the power output end to the power input end is equal to (Nl + N2) / N2, wherein N1 is the number of blunt teeth of the first cam surface, and N2 is the number of pure convex teeth of the second cam surface. In an embodiment of the invention, the second conjugate cam group is used as a power input end, the second transmission shaft is used as a power output end, and the first transmission shaft is used as a power transmission end. Fixed end. A transmission speed ratio of the power output end to the power input end is equal to N2 / (N1 + N2), wherein in 201219679, N1 is the number of blunt teeth of the first cam surface, and N2 is the number of pure convex teeth of the second cam surface. In an embodiment of the invention, the second common cam group is used as a power input end, the first transmission shaft is used as a power output end, and the second transmission shaft is used as A fixed end. A transmission speed ratio of the power output end to the power input end is equal to N2/N1, wherein N1 is the number of blunt teeth of the first cam surface, and N2 is the number of blunt teeth of the second cam surface. The above and other objects, features and advantages of the present invention will become more <RTIgt; Furthermore, the directional terms mentioned in the present invention, such as "upper", "lower", "before", "after", "left", "right", "inside", "outside" or "side", etc. Just refer to the direction of the additional schema. Therefore, the directional terminology used is for the purpose of illustration and understanding of the invention. Referring to Figures 1 and 2, the coaxial cam shifting mechanism of the first embodiment of the present invention can be applied to various power machines, automobiles, locomotives or other power machines as a gearbox or other deceleration/speed increase. A mechanism is used to provide an appropriate deceleration/growth function between a power input and a power wheel outlet. The coaxial cam shifting mechanism of the first embodiment of the present invention mainly comprises: a first transmission shaft 1, a first common cam group 2, a second conjugate cam group 3, at least one roller wheel set 4, and 201219679. One less planet carrier 5 and one second transmission shaft 6. The present invention will be described in detail below with reference to Figs. 1 to 8 in detail of the detailed construction of the above-described respective elements of the first embodiment and the principle of operation thereof. Referring to Figures 1, 2 and 3, the first transmission shaft 1 of the first embodiment of the present invention is a shaft made of metal or alloy, wherein one end (outer end) of the first transmission shaft 1 is a product. The design requirement can be selected as a power input end, a power output end or a fixed end, and the other end (inner end) of the first transmission shaft 1 is fixedly coupled to the geometric center position of the first conjugate cam group 2 In order to enable the first transmission shaft 1 to rotate synchronously with the first common cam group 2. Referring to FIGS. 1, 2 and 3 again, the first conjugate cam set 2 of the first embodiment of the present invention rotates synchronously with the first transmission shaft 1, and the first transmission shaft can be selected according to product design requirements. 1 drives the first conjugate cam group 2 to rotate, or the first conjugate cam group 2 drives the first transmission shaft 1 to rotate. Furthermore, the first common cam group 2 has at least two conjugated first cams 21, 22, which are cam plates made of metal or alloy, which are fixedly coupled to each other and It can rotate synchronously, so it is called "conjugated bonding". In the present embodiment, the number of the first cams 21, 22 is two, but it may be three or more. The first cams 21, 22 each have a first cam surface 211, 221 which is an outer peripheral surface similar to a blunt, wavy or petal shape, respectively, which have the same configuration as each other. At the same time, the blunt-toothed sections of the at least two first cam faces 211, 221 are in a staggered relationship with each other, wherein one of the first cam faces 211 has a blunt convex toothed region 201219679*t corresponding to the other The first cam surface 221 has a blunt groove-like region. The pure groove-like portion of the first cam surface 211 also corresponds to one of the other first cam faces 221. Referring to Figures 1, 2 and 4, a second common cam set 3 of the first embodiment of the present invention is disposed on the periphery of the first common cam group 2. The third common cam set 3 has a second convex, 31, 32', the second cam 3b 32 is a φ ring body made of metal or alloy, which is fixedly coupled to each other and can rotate synchronously, so called conjugate In the present embodiment, the number of the second cams 31, 32 corresponds to the first cams 21, 22, and is also two, but may also be three or more. The second cams 31, 32 Each has a second cam surface 311, 321 which is respectively an inner peripheral surface similar to a blunt-toothed, wavy or palladium-like shape, which have the same configuration with each other. Meanwhile, the at least two second cam faces The blunt convex sections of 311 and 321 are also in a staggered relationship with each other, wherein a pure convex tooth section of the second cam surface 311 corresponds to a blunt groove of the other second cam surface 321 a blunt section of the second cam surface 311 corresponding to one of the other second cam faces 321 A blunt-toothed section. Referring to Figures 1, 2 and 5, the first embodiment of the present invention has at least two roller wheels 41 and a rotating shaft 42. Both are made of metal or alloy, wherein the number of the roller wheels 41 is correspondingly equal to the number of the first cams 21, 22 and the second cams 31, 32. Each of the roller wheels 41 comprises a plurality of rollers a plurality of rotating disks 412. In the present embodiment, the roller set 4 has two rollers 201219679 wheels 41, and the number of rollers 411 of each of the roller wheels 41 is three, and the two The roller wheels 41 share three rotating disks 412. Each of the rollers 411 is rotatably equiangularly arranged and pivotally connected between two adjacent rotating disks 412. Further, the at least two roller wheels 41 are Rotatingly disposed on the same rotating shaft 42 , the two ends of the rotating shaft 42 are respectively pivotally connected to the planet carrier 5 . The roller wheel 41 and the roller 411 are respectively respectively disposed on the first conjugate cam Between the first cam faces 211, 221 of the group 2 and the second cam faces 311, 321 of the second conjugate cam set 3, and on the first cam faces 211, 221 and the second cam face 311 The rollers 411 of the at least two roller wheels 41 are also arranged in a staggered relationship with each other, and the staggered relationship corresponds to the first cam faces 211, 221 and the second cam faces. The staggered arrangement of the blunt-toothed section and the blunt-shaped section of 321 and 322. Referring to Figures 1, 2 and 6, the at least one carrier 5 of the first embodiment of the present invention is used for The pivoting pivot supports the rotating shaft 42 of the roller wheel set 4 and the roller wheel 41. Each of the carrier 5 has a first bracket 51 and a second bracket 52, both of which are made of metal or alloy. The first end 511 and the second end 512 of the first bracket 51 are respectively rotatably coupled to one side of the roller wheel set 4 (that is, one end of the rotating shaft 42) and the first transmission The first end 512 is rotatably pivotally connected to the first transmission shaft 1 by a bearing (not shown); and the first end 521 of the second bracket 52 is pivotable Connecting the other side of the roller set 4 (that is, the other end of the rotating shaft 42), and a second end 522 thereof is fixedly coupled The second transmission shaft 6 and the second 12201219679 and may be rotated synchronously with the drive shaft 6. Referring to Figures 7 and 8, there is shown a schematic operation diagram of the coaxial cam shifting mechanism of the first embodiment of the present invention. As shown in the first, second, seventh and eighth embodiments, in the present embodiment, the first transmission shaft 1 is defined as a power input end, and the second transmission shaft 6 is defined as a power output end. And defining the second conjugate cam group 3 as a fixed end. When the first transmission shaft 1 is driven by an external mechanism (for example, a crankshaft of an engine) to rotate counterclockwise, since the first transmission shaft 1 is fixedly coupled to the first conjugate cam group 2 (as shown in FIG. 1 Therefore, the first conjugate cam set 2 will rotate counterclockwise in synchronization with the first transmission shaft 1. Then, the first cams 21 and 22 of the first conjugate cam group 2 are used to push the three rollers of the two roller wheels 41 of the roller wheel set 4 by the two first cam faces 211 and 221 when rotating. Sub 411. In this way, the roller 411 can rotate clockwise between the two first cam faces 211, 221 and the second cam faces 311, 321 of the second conjugate cam group 3, and along the second and second The cam faces 311, 321 perform counterclockwise planetary motion and can synchronously push the rotating disk 412 to rotate counterclockwise. Subsequently, the roller wheel set 4 can push the second bracket 52 on the other side of the carrier 5 to rotate counterclockwise via the rotating disk 412 and the rotating shaft 42. Since the second end 522 of the second bracket 52 is fixedly coupled to the second transmission shaft 6, the second transmission shaft 6 will be synchronously counterclockwise rotated to drive another external mechanism via the second transmission shaft 6 (eg The wheel) rotates at the adjusted speed. It is worth noting that the transmission speed ratio of the power output end (the second transmission shaft 6) and the 13 201219679 power input end (the first transmission shaft 1) is equal to N1/(N1+N2), where N1 is the The number of blunt teeth of the first cam faces 211, 221, and N2 is the number of blunt teeth of the second cam faces 311, 321 . For example, in the reference examples of FIGS. 5 and 6, the number of blunt teeth of the first cam faces 211 and 221 is six, and the number of blunt teeth of the second cam faces 311 and 321 is nine, so The power input end (the first transmission shaft 1) transmits power to the power output end (the second transmission shaft 6), and the speed will become 6/(6+9) of the original rotation speed, that is, the transmission mechanism It belongs to a reduction drive design. In addition, in other embodiments, the present invention may also define the second transmission shaft 6 as a power input end, define the first transmission shaft 1 as a power output end, and define the second conjugate cam. Group 3 is used as a fixed end. At this time, the transmission speed ratio of the power output end (the first transmission shaft 1) and the power input end (the second transmission shaft 6) will become opposite, that is, (N1+N2)/N1, where N1 is The number of blunt teeth of the first cam faces 211, 221, N2 is the number of blunt teeth of the second cam faces 311, 321 . For example, in the reference examples of FIGS. 5 and 6, the transmission speed ratio is (6+9). ) / 6, thus making the transmission a design for a speed increase transmission. Furthermore, the present invention may also define the first transmission shaft 1 as a power input end, define the second conjugate cam group 3 as a power output end, and define the second transmission shaft 6 as a fixed end. . At this time, the power output end (the second transmission shaft 6) and the power input end (the first transmission shaft 1) have a transmission speed ratio N1/N2, wherein N1 is the first cam surface 14 201219679 211, 221 The number of blunt teeth, N2 is the number of blunt teeth of the second cam faces 311, 321 . For example, in the reference examples of FIGS. 5 and 6, the transmission speed ratio is 6/9, thereby making the transmission a deceleration Transmission design. Alternatively, the present invention may also define the second drive shaft 6 as a power input end, define the second conjugate cam set 3 as a power output end, and define the first drive shaft 1 as a fixed end. At this time, the power output end (the second conjugate cam group 3) and the power input end (the second transmission shaft 6) have a transmission speed ratio (N1+N2)/N2, wherein N1 is the first cam The number of blunt teeth of the faces 211, 221, N2 is the number of blunt teeth of the second cam faces 311, 321 , for example, in the reference examples of Figs. 5 and 6, the transmission speed ratio is (6 + 9) / 9, Therefore, the transmission mechanism becomes a speed increasing transmission design. In addition, the present invention may also define the second conjugate cam set 3 as a power input end, define the second drive shaft 6 as a power output end, and define the first drive shaft 1 as a fixed end. At this time, the power output end (the second transmission shaft 6) and the power input end (the second conjugate cam group 3) have a transmission speed ratio N2 / (N1 + N2), wherein N1 is the first cam The number of blunt teeth of the faces 211 and 221, and N2 is the number of blunt teeth of the second cam faces 311 and 321 . For example, in the reference examples of FIGS. 5 and 6, the transmission speed ratio is 9/(6+9). Thus, the transmission mechanism becomes a reduction transmission design. In addition, the present invention may also define the second conjugate cam group 3 as a power input terminal, defining the first transmission shaft 1 as a power transmission 15 201219679, and defining the second transmission _6 Is: the force output end (the first transmission shaft, and the power input: two = = wheel set 3) - the transmission speed ratio is m, wherein the cam surface is called, the pure convex number of the work, and the second cam surface is N2 ^一^ The pure convex tooth number, for example, the transmission speed ratio in the 5th and 6th figures is 9/6, ra and /* # & τ its transmission design. Α Thus, the transmission mechanism is a speed increase: Referring to FIG. 9 , a second embodiment of the present invention is disclosed: a schematic diagram of a brief operation of the speed cam mechanism, the embodiment of which is similar to the first embodiment of the present invention. Referring to the first and the third, the first embodiment includes three rollers. For example, the coaxial cam shifting machine of the embodiment includes a single roller set. In the second embodiment, by increasing the number of corresponding groups of the roller wheel set *^the star frame 5 to two, three or more, the transmission can be performed during the transmission period such as deceleration or speed increase relative to the two== wheel shifting mechanism. Stability and reliability. As described above, compared with various existing transmission mechanisms, the backlash error ~ tif ^ is usually a single power input / output s and other disadvantages, the first to the second embodiment of the present invention by the first - and second The mounds of m2, 3 and the combination of the roller wheel set 4 and the planet carrier 5, which constitute a plurality of input/output transmission modes for selective use, are advantageous for increasing the application diversity of the transmission mechanism. Furthermore, the above-mentioned first 201219679 cam group 2, 筮-beach heart „ has no assembly and wear problems of money age 4, so there is a backlash and movement caused by pain phase/mouth combination; The power transmission of the power machine is t=== the wear resistance and the transmission accuracy. In addition, the two cams 3i, 32 Γ choose to adjust the first cam 21, 22 and the first or the selected speed m convex ratio to design Appropriate deceleration. θ, thus facilitating the application of the high-load, 杻 耠 $ $ 动力 动力 动力 动力 动力 动力 动力 ; ; ; ; ; ; ; ; ; ; ; ; ; ; ; ; ; ; ; ; ; ; ; ; ; ; ; ; ; ; ; ; The strength and torque transmission 3 and the roller wheel are also described as follows - the common cam group 2, the second common cam group of the same size or the structure of 5 is relatively simple, and is easily designed to be less than increased in group shape, thereby also contributing to reduction The present invention has been disclosed in its preferred embodiments, and it is not intended to limit the scope of the invention to any person skilled in the art, without departing from the scope of the invention. Make various changes and modifications, so the invention patents are attached to the patent application The definition is based on the following: [Comprehensive description of the drawings]: Li diagram of the coaxial cam shifting mechanism of the first embodiment of the present invention: the coaxial cam shifting mechanism of the first embodiment of the present invention is convex And a partial enlarged view of the first transmission shaft and the first common wheel of the first embodiment of the present invention. 17 201219679 FIG. 4 is a partial enlarged view of the second common cam group of the first embodiment of the present invention. Fig. 5 is a partially enlarged view of the roller wheel set of the first embodiment of the present invention. Fig. 6 is a partially enlarged view of the carrier and the second drive shaft of the first embodiment of the present invention. Figs. 7 and 8: BRIEF DESCRIPTION OF THE DRAWINGS Fig. 9 is a schematic view showing the operation of the coaxial cam shifting mechanism of the second embodiment of the present invention. [Main component symbol description] 1 First transmission shaft 2 First conjugate cam group 21 first cam 211 first cam surface 221 first cam surface 22 first cam 3 second common cam group 31 second cam 311 second cam surface 32 second cam 321 second cam surface 4 Roller Wheel set 41 Roller wheel 411 Roller 412 Rotating disc 42 Rotary shaft 5 Planetary frame 51 First bracket 511 First end 512 Second end 52 Second bracket 521 First end 522 Second end 6 Second drive shaft 18