200950924 六、發明說明： 【發明所屬之技術領域】 本發明是關於「將作爲動力來源之馬達的轉動予以減 速後輸出」之齒輪馬達的技術領域。 【先前技術】 在第4圖及第5圖中，顯示已廣爲大眾所知悉的工作 0 機械（請參考專利文獻1)。該工作機械1，在殻體2内 備有「具備複數個工具4」的工具倉匣3。該工具倉匣3 是形成圓盤狀，並將不同種類的工具4配置在每個特定的 間隔而呈現放射狀。此外該工具倉匣3是構成：可藉由配 置在該倉匣3前面的馬達10，而在特定的時間點轉動至 特定的位置。另外，在該工作機械1備有：用來將動力傳 達至工具4的頭部5。此外該頭部5是構成：可在特定的 時間點，於上下方向（第4圖中的上下方向）中進退，且 φ 可在該進退的途中，從工具倉匣3收授工具4。頭部5是 根據對加工對象物（圖面中未顯示）的加工内容，選擇必 要的工具4，並執行加工（例譬如：鑽孔加工、切削加工 等）。該工具4的選擇可藉由以下的方式實現：藉由工具 倉匣3的轉動，而使所需種類的工具4移動至相對於頭部 5的裝卸位置。 [專利文獻1]日本特開昭61 — 50735號公報 【發明內容】 -5- 200950924 [發明欲解決之課題] 在工作機械1中，將馬達10配置於工具倉匣3之前 面的作法，是爲了方便執行譬如馬達10本身的維修保養 作業（交換等）。 然而，在將馬達10配置於工具倉匣3前面（前方側 )的場合中，由於該馬達10部分是形成不可避免地突出 於工具倉匣3前面（亦即，工作機械1的前面）的構造， 而導致工作機械1的深度尺寸變大。不僅如此，在對安裝 於工具倉匣3之工具4.進行維修保養作業（譬如交換）的 場合中，由於該馬達10是位在作業者的頭部附近，而使 馬達10造成妨礙而難以進行維修保養作業。另外，爲了 避免上述的問題而將馬達配置在譬如工具倉匣3的內部方 向，雖然使工具4的交換作業變得容易，卻導致馬達1〇 本身的維修保養作業變得困難。 本發明，正是爲了解決上述問題點所硏發的發明，本 發明的課題在於：在兼顧馬達本身的維修保養性與工具之 維修保養性的同時，提供一種深度尺寸小型化的工具倉匣 用齒輪馬達。 [解決課題之手段] 本發明是用來轉動驅動可保持複數個工具之工具倉匣 的工具倉匣用齒輪馬達，其具備：作爲驅動來源的馬達； 和減速機，該減速機可在輸出部安裝前述工具倉匣的本體 :及固定體，該固定體具備第1連結面，該第1連結面是 -6- 200950924 構成該減速機的一部分或者獨立個體，.而連結前述馬達， 並可在連結著該馬達的狀態下，與前述工作機械的本體側 連結，在透過前述固定體將前述減速機連結於前述工作機 械之本體側的狀態下，使前述馬達可從沿著前述第1連結 面的方向裝卸，藉此可解決上述課題。 藉由採用上述的構造，能提供不會突出於工具倉匣之 前面側的工具倉匣用齒輪馬達。亦即，藉由構成：可相對 0 於連接著工作機械本體與減速機的固定體，而從沿著第1 連結面的方向裝卸馬達，可減少馬達突出於與第1連結面 直交之方向（工具倉匣的前面側、工作機械的前面側、或 作業者側）的量。如此一來，可使工作機械的深度尺寸小 型化，並能兼顧馬達本身的維修保養、工具之維修保養的 作業性。 [發明效果] 〇 藉由採用本發明，可在兼顧馬達本身的維修保養性與 工具之維修保養性的同時，提供深度尺寸小型化的工具倉 匣用齒輪馬達。 【實施方式】 以下’參考圖面詳細地說明本發明之實施形態的其中 ~^例〇 第1圖’是顯示本發明實施形態之其中一例的齒輪馬 達的側剖面圖。第2圖，是已安裝著工具倉匣之狀態的齒 200950924 輪馬達的側剖面圖。第3圖，是工具倉匣的前視 圖中的箭號ΠΙ方向）。 <齒輪馬達的構造> 齒輪馬達100是由以下所構成：減速機102 減速機102連結的固定體104;及連結於該固定j 伺服馬達106。固定體104是使箱狀的固定體殼 中心，並在該箱的其中一面的第1連結面104A 機械本體1〇8(僅顯示圖號）連結固定。然而， 上的說明中第1連結面104 A是構成直接與工作 108連結固定的構造，但也可以是譬如：透過由 所構成的轉接器等其他構件而間接性的連結。此 定體殻117的上側面（第2連結面104B )連接 達106。此外，在構成傾斜於第1連結面i〇4A[ 結面104C，聯接著減速機1〇2。 而在本實施形態中，雖然固定體104是構成 速機102以外的構成構件，但也可以是以下的構 體1 04作爲減速機1 02的一個構成要件（譬如： 102的局部延伸而發揮固定體殻117之功能的構| <固定體的構造> 作爲伺服馬達106之輸出軸的馬達軸11〇是 Π2連結，該連結軸112是透過軸承114及軸承 支於固定體殼117的内周面11 7A。 圖（第2 ;和與該 體104的 1 17構成 ，與工作 雖然在以 機械本體 平面的板 外，在固 著伺服馬 的第3連 獨立於減 造：固定 使減速機 I ) 〇 與連接軸 1 1 6而軸 -8- 200950924 上述的内周面117A、軸承114、116及連接軸112, 是相互地藉由栓承接合（sPig〇t j oint )或扣環而限制軸方 向的位置。在連接軸112，是於其前端直接切削形成小齒 輪1 12P，並於另一端（前端側的相反側）形成有凹部 11 2A。在該凹部11 2A，藉由鍵而結合有前述之馬達軸 110的前端，不僅如此，該鍵是藉由小螺絲（圖面中未顯 示）而形成不會脫落。如此一來’馬達軸11〇與連接軸 ❹ 112是被固定於轉動方向。此外，在連接軸112的前端直 接切削形成的小齒輪1 1 2P，是與傘齒輪（bevel gear ) 118嚙合。如此一來，在固定體104的内部（固定體殼 117的内部）藉由小齒輪112P與傘齒輪118構成減速機 構。該傘齒輪118，是在減速機102之輸入軸122的其中 —端（固定體104側的端部），由螺栓120所連結固定。 此外，小齒輪112P與傘齒輪118之間的嚙合是構成 :使彼此的軸心（小齒輪1 12P的軸心02、傘齒輪1 1 8的 Φ 軸心〇:)之間形成特定的角度α。在本實施形態中，該 角度α爲1 10°。 而固定體104的内部，是藉由油封146、0型環144 、180、184的存在，而形成獨立的密閉空間。 <減速機的構造> 減速機102，是對輸入至輸入軸122的動力（轉動力 )予以減速後輸出。本實施形態中的減速機1 0 2，是所謂 的偏心搖動型内接嚙合行星齒輪減速機。 200950924 在可將軸心〇!作爲中心而轉動的輸入軸122，一體 地形成有偏心體124。在本實施形態中，偏心體124是形 成3個，且分別構成約120°的相位差。此外，雖然隨著上 述的構造而使偏心體用軸承126與外齒齒輪128分別形成 3組的構造，但本發明並不侷限於該構造。即使根據減速 機所要求的傳達容量等，而使外齒齒輪128等爲1組、2 組、或者4組以上的構造也無妨。 偏心體124，是透過偏心體用軸承126而嵌合於外齒 齒輪128的中心孔128Α。該外齒齒輪128在使偏心體用 軸承126嵌合於本身的中心孔12 8 Α的同時，嚙合於内齒 齒輪的内齒（在本實施形態中，相當於外銷130)。此外 ，在外齒齒輪128，於圓周方向的不同位置設有複數個内 銷孔128B(圖面中僅顯示1個）。內銷138是透過內滾 子140而鬆動嵌合於該内銷孔128B。該内滾子140可相 對於内銷138而自由轉動。 此外，與外齒齒輪128嚙合的外銷130，是複數設置 於減速機殼132的内周面。雖然在圖面中並未出現，但是 外齒齒輪128的齒數、與外銷130的數量是設成少量的差 異（1~3左右）。 本實施形態中的内銷138，是與圓盤狀的第1突緣 134 —體形成。不僅如此，内銷138，是藉由螺栓162而 與圓盤狀的第2突緣136連結固定。亦即，内銷138與第 1、第2突緣134、136形成一體化。 此外，在第1突緣134與輸入軸122之間配置有軸承 -10- 200950924 156，在第2突緣136與輸入軸122之間配置有軸承158 ，在第1突緣134與減速機殻132之間配置有軸承148’ 在第2突緣136與減速機殼132之間配置有軸承150° 而蓋152被設成遮掩第2突緣136’該蓋152是藉由 螺栓154而固定於減速機殼132。此外，圖號132A，是 用來將後述的工具倉匣安裝於減速機殻132的螺栓孔 。此外，減速機102的内部是藉由油封142、146、〇型 φ 環1 82的存在，而形成獨立的密閉空間。 <減速機與固定體之間的連結> 減速機102與固定體104之間的連結，在本實施形態 中是藉由「連結第1突緣（非轉動構件）134與固定體殼 1 17」的螺栓160所實現。如同以上所描述，由於第1突 緣134是透過一體形成的内銷138而與第2突緣136連結 固定，因此内銷138或第2突緣136，實際上也連結固定 〇 於固定體殼117。根據上述的構造可形成：被輸入至輸入 軸122的轉動，是透過偏心體124、偏心體用軸承126、 外齒齒輪128而傳達，最終使減速機殻132本身相對於被 固定的内銷138而轉動（詳細的作用稍後說明）。也就是 構成：減速機殻132本身作爲該齒輪馬達1〇〇的輸出軸（ 輸出部）發揮作用。 此外’在減速機102與固定體1〇4之間的連結部分， 也就是指位於減速機102的第1突緣134、與位於固定體 104的固定體殻117之間的連結面（第3連結面104C) -11 - 200950924 ，夾介著〇型環144。此外，在第1突緣I34的内周面、 與輸入軸122的外周面之間設有油封146。 然而，雖然圖面中未顯示，但在固定體104及減速機 1 02的内部分別封入著潤滑劑（黃油等）。 <齒輪馬達與工具倉匣的關係> 接下來，齒輪馬達100與工具倉匣17〇之間的關係顯 示於第2圖中。工具倉匣170是由工具倉匣本體（轉動軸 )171與可保持工具的工具承座172所構成。此外工具倉 匣170，是利用設於減速機102之減速機殼132(輸出部 )的螺栓孔13 2A，而連接固定於減速機殼132。該工具 倉匣170，是以更進一步遮掩減速機102之蓋152的樣態 ，連結固定於減速機1 02的前面側（第2圖中的左側）。 而工具倉匣170，在呈正面視角（箭號III方向：請參考 第3圖）的場合中，是構成圓盤狀。不僅如此，複數個工 具承座172是配置在每個特定的間隔而構成放射狀（以軸 心〇〗作爲中心而在半徑方向上呈放射狀）。此外，在各 個工具承座172’分別保持著各種不同種類的工具丨74。 <齒輪馬達的作用> 接著，說明齒輪馬達100的作用。一旦將轉動指令輸 入伺服馬達106,將僅以所指示的量（角度）促使馬達軸 110轉動。該馬達軸110的轉動，是透過連接軸112而朝 小齒輪112P傳達，進而傳達至所嚙合的傘齒輪118。由 -12- 200950924 於該傘齒輪118連結固定於減速機102的輸入軸122,而 使輸入軸122轉動。而在本實施形態中’是在從小齒輪 112P朝傘齒輪118的傳達時間點（時機），對馬達軸11〇 的轉動減速（減速機構）。 —旦輸入軸122轉動，一體形成於該輸入軸122的偏 心體124將偏心轉動。該偏心體124的偏心轉動’是透過 偏心體用軸承126而朝外齒齒輪128傳達。如此一來’外 0 齒齒輪128是在對軸心0!搖動的狀態中開始轉動。另外 ，由於該外齒齒輪128也嚙合於外銷130而限制了轉動’ 故幾乎僅執行搖動。此外，如先前所描述，由於該外齒齒 輪128的齒數與外銷130的數量間僅設有少量的差（齒數 差），而使外齒齒輪128形成：每搖動轉動1次，便僅以 該齒數差的量，對外銷130形成自轉。外齒齒輪128對該 外銷130的自轉量（相對轉動量），是透過内銷138與内 滾子140而朝第1、第2突緣134、136被取出。但是在 Φ 本實施形態中，由於第1突緣134是被固定於固定體殼 117，因此該相對轉動量是成爲減速機殼132的轉動而被 輸出。而外齒齒輪128的搖動量，由於被外齒齒輪128與 内銷138(及内滾子140)間的鬆動嵌合所抵銷，因此僅 取出該自轉量（相對轉動量）。 如同以上所描述，在本實施形態中，由於第1突緣 134與固定體殻117連結固定，因此上述相對轉動量是以 減速機殼132之轉動的型態輸出。亦即，促使連結固定於 減速機殼132的工具倉匣170轉動。 •13- 200950924 如此一來，在齒輪馬達100中， 1連結面104A的方向（第1圖中的 ，將伺服馬達6自由裝卸於連接工作 速機102的固定體104，而減少伺服 倉匣170之前面（亦即 ，工作機械的前面、作業者側）的量 機械的深度尺寸小型化，並能兼顧伺 、工具174之維修保養的作業性。 此外，工具倉匣170之轉動位置 ，並非依賴凸輪機構等。也就是說 170連結固定於減速機102的輸出軸 速機殼132)，並更進一步以伺服馬 102，而形成可將伺服馬達106的轉 工具倉匣170之轉動位置（停止位置 非如凸輪機構般粗略地階段性定位， 1 06之轉動偵測精度的最小單位程度 藉由小齒輪112P與傘齒輪118之間 機102的減速，是可以執行超越伺服 精度的定位。 舉例來說，在採用凸輪機構來執 位的場合中，由於一旦因設計變更等 ，將使相鄰的工具承座172的節距變 述的改變來變更凸輪機構的設計（譬 變更凸輪溝的節距，使所增設的工具 是構成藉由從沿著第 Z方向··上下方向） 機械之本體1〇8與減 馬達106突出於工具 ，如此一來可使工作 服馬達106維修保養 (停止位置）的取得 ，是藉由將工具倉匣 (在本實施例中爲減 達106驅動該減速機 動偵測精度，應用於 )的取得。亦即，並 而是能形成伺服馬達 的定位。不僅如此， 的減速部分、及減速 馬達106之轉動偵測 行工具承座172之定 而增設工具承座172 更，因此必須配合上 如：必須藉由細微地 承座172定位於特定 -14- 200950924 的位置）。但是，倘若採用本實施形態的構造，無論相鄰 的工具承座172的節距產生哪種變化，也能在不變更齒輪 馬達1 〇〇之設計的狀態下直接利用。 此外，在本實施形態中，是採用具有自鎖性的偏心搖 動型内接嚙合行星齒輪減速機來作爲減速機102。如此一 來，無須特別設置制動機構等，僅以伺服馬達1 06之轉動 的ΟΝ/OFF，便能將工具承座172保持於特定的轉動位置 。當然也能額外設置制動機構等，以期能更確實。 此外，在本實施形態中，工具倉匣170具備：將該該 工具倉匣170的轉動軸（與軸心0〗一致）作爲中心，並 可在半徑方向上將工具保持於每個特定的間隔（節距）G 。不僅如此，伺服馬達1 〇6是可從該工具承座1 72之間（ 間隔G)裝卸（請參考第3圖）。藉由構成上述的說明， 能使伺服馬達1〇6的裝卸作業變得更容易。 此外，在本實施形態中，固定體104 (的固定體殼 117)是形成箱狀的外觀，且其中一面是形成與工作機械 之本體108連結的第1連結面104A，另一面則形成與伺 服馬達106連結的第2連結面104B，甚至另外一面是形 成與減速機1〇2連結的第3連結面104C。如此一來’使 固定體104和減速機102留置於工作機械的本體108側’ 而形成可單獨地僅裝卸伺服馬達1〇6。 此外，在本實施形態中，與減速機102連結的第3連 結面104C，是對與工作機械之本體108連結的第1連結 面104A構成傾斜。藉由採用上述的構造，可輕易地將工 -15- 200950924 具承座172配置於特定的方向（角度）。 此外，在本實施形態中，在減速機1〇2與固定體104 間的連結部分設有油封1 46，而將封入各個内部的潤滑劑 予以隔離。藉此，可確實地確保「應保持於減速機102内 部的量（最佳量）」的潤滑劑，此外，可確實地確保「應 保持於固定體1 04内部的量（最佳量）」的潤滑劑。譬如 ，在減速機102封入「可使軸承148與軸承150整體浸入 之程度」的潤滑劑，另外，在固定體104內形成僅供傘齒 輪118之下端浸入的程度，可降低攪拌的損失。 此時亦可構成：被封入減速機102内的潤滑劑、與被 封入固定體104内的潤滑劑不同。也就是說，可藉由已隔 離的狀態，而使用對應於各部特性的最佳潤滑劑。 此外，在本實施形態中，固定體104内的減速是由： 被配置於伺服馬達106側的小齒輪（第1傘齒輪）112P、 及被配置在減速機102側的傘齒輪（第2傘齒輪）所實現 ，而傘齒輪118是可裝卸地安裝於減速機102的輸入軸 122。藉由採用上述的構造，可使角度α (由軸心01與 〇2所形成的角度α )的設計變更變得容易。 此外，在本實施形態中，在減速機102的輸入軸122 上，傘齒輪118安裝位置之軸方向的相反側，形成有六角 扳手孔164 (轉動防止構件安裝部），該六角扳手孔164 (轉動防止構件安裝部）可防止將該傘齒輪118安裝於輸 入軸122時之輸入軸122的轉動。如此一來，在執行傘齒 輪118的裝卸（對輸入軸122的裝卸）之際，可輕易地防 -16- 200950924 止輸入軸122不經意的轉動，使裝卸作業變得確實且容易 [產業上的利用性] 以NC工作機械爲首’適用於可自動地更替複數種類 的工具以執行作業之工作機械的工具倉匣驅動。 0 【圖式簡單說明】 第1圖：是顯示本發明之實施形態的其中一例之齒輪 馬達的側剖面圖。 第2圖：是安裝有工具倉匣之狀態的齒輪馬達的側剖 面圖。 第3圖：爲工具倉匣的前視圖（第2圖中的箭號III 方向）。 第4圖：是顯示專利文獻1所記載之工作機械的局部 φ 的圖。 第5圖：是專利文獻1所記載之工作機械的整體想像 圖。 【主要元件符號說明】 100 :齒輪馬達 102 :減速機 104 :固定體 104A :第1連結面 -17- 200950924 104B :第2連結面 104C :第3連結面 106 :伺服馬達 108:工作機械本體 1 1 〇 :馬達軸 1 12 :連接軸 1 12A :凹部 1 12P ：小齒輪 114、 116、 148、 150、 156、 158：軸承 1 1 7 :固定體殼 1 1 7 A :内周面 1 1 8 :傘齒輪 120 、 154 、 160 、 162 :螺栓 122 :輸入軸 1 2 4 :偏心體 1 2 6 :偏心體用軸承 1 2 8 :外齒齒輪 1 2 8 A :中心孔 1 2 8 B :内銷孔 1 3 0 :外銷 1 3 2 :減速機殼 1 3 2 A :螺栓孔 134:第1突緣（非轉動構件） 136 :第2突緣 -18- 200950924 138 :内銷 140 :内滾子 142， 146 ：油封 1 5 2 :蓋 1 6 4 :六角扳手孔 1 70 :工具倉匣 1 72 :工具承座The invention is related to the technical field of a gear motor that "decelerates the rotation of a motor as a power source and outputs it". [Prior Art] In the fourth and fifth figures, the work that has been widely known to the public is shown. 0 (Please refer to Patent Document 1). In the machine tool 1, a tool magazine 3 having "a plurality of tools 4" is provided in the casing 2. The tool magazine 3 is formed in a disk shape, and different types of tools 4 are arranged at each specific interval to be radially formed. Further, the tool magazine 3 is constructed such that it can be rotated to a specific position at a specific time point by the motor 10 disposed in front of the magazine 3. Further, the work machine 1 is provided with a head 5 for transmitting power to the tool 4. Further, the head portion 5 is configured to advance and retreat in the up and down direction (up and down direction in Fig. 4) at a specific time point, and φ can receive the tool 4 from the tool magazine 3 in the middle of the advance and retreat. The head 5 selects a necessary tool 4 based on the processing contents of the object to be processed (not shown in the drawing), and performs machining (for example, drilling, cutting, etc.). The selection of the tool 4 can be achieved by moving the tool 4 of the desired type to the loading and unloading position relative to the head 5 by the rotation of the tool magazine 3. [Patent Document 1] Japanese Laid-Open Patent Publication No. SHO 61-50735-A SUMMARY OF INVENTION [Problem to be Solved by the Invention] In the machine tool 1, the motor 10 is disposed in front of the tool magazine 3, and In order to facilitate the maintenance and repair work (exchange, etc.) of the motor 10 itself. However, in the case where the motor 10 is disposed in front of the tool magazine 3 (front side), the motor 10 is partially formed to inevitably protrude from the front of the tool magazine 3 (that is, the front surface of the machine tool 1). , and the depth of the working machine 1 becomes larger. In addition, in the case of performing maintenance work (for example, exchange) on the tool 4 attached to the tool magazine 3, since the motor 10 is positioned near the head of the operator, the motor 10 is hindered and it is difficult to perform. Maintenance work. Further, in order to avoid the above problem, the motor is disposed in the inner direction of the tool magazine 3, and the exchange work of the tool 4 is facilitated, which makes maintenance of the motor 1 itself difficult. The present invention has been made to solve the above problems, and an object of the present invention is to provide a tool magazine for miniaturization of a depth and size while maintaining the maintainability of the motor itself and the maintainability of the tool. Gear motor. [Means for Solving the Problem] The present invention is a tool magazine gear motor for rotationally driving a tool magazine capable of holding a plurality of tools, comprising: a motor as a driving source; and a speed reducer which is available at an output portion Mounting the body of the tool magazine: and a fixed body having a first connecting surface, the first connecting surface is a part of the speed reducer or an independent individual, and is connected to the motor, and In a state in which the motor is coupled, the motor is coupled to the main body side of the machine tool, and the motor is detachably coupled to the main body side of the machine tool through the fixed body, so that the motor can pass along the first joint surface. The above problems can be solved by loading and unloading in the direction. By adopting the above configuration, it is possible to provide a gear motor for a tool magazine that does not protrude from the front side of the tool magazine. In other words, the motor can be attached to and detached from the first connecting surface with respect to the fixed body to which the machine body and the speed reducer are connected, so that the motor can be prevented from protruding in a direction orthogonal to the first connecting surface ( The amount of the front side of the tool magazine, the front side of the work machine, or the operator's side. In this way, the depth of the working machine can be reduced, and the maintenance of the motor itself and the maintenance of the tool can be achieved. [Effect of the Invention] By adopting the present invention, it is possible to provide a gear motor for a tool magazine that is compact in size and compact, while maintaining both the maintainability of the motor itself and the maintainability of the tool. [Embodiment] Hereinafter, a first embodiment of the present invention will be described in detail with reference to the drawings. FIG. 1 is a side cross-sectional view showing a gear motor as an example of an embodiment of the present invention. Fig. 2 is a side sectional view showing the teeth of the 200950924 wheel motor in a state in which the tool magazine is mounted. Figure 3 is the arrow ΠΙ direction in the front view of the tool magazine. <Structure of Gear Motor> The gear motor 100 is composed of a fixed body 104 to which the speed reducer 102 of the speed reducer 102 is coupled, and a fixed servo motor 106 connected thereto. The fixed body 104 is a center of a box-shaped fixed body case, and is fixedly connected to the first connecting surface 104A of the one side of the case, the mechanical body 1 8 (only the figure is displayed). However, in the above description, the first joint surface 104A is configured to be directly coupled to the work 108, but may be indirectly connected through another member such as an adapter. The upper side surface (second joining surface 104B) of the fixed casing 117 is connected to 106. Further, the configuration is inclined to the first joint surface i〇4A [the joint surface 104C, and the speed reducer 1〇2 is coupled. In the present embodiment, the fixed body 104 is a constituent member other than the speed reducer 102. However, the following structure 104 may be used as a component of the speed reducer 102 (for example, a partial extension of 102 is fixed. Structure of the function of the body casing 117 | <Structure of the fixed body> The motor shaft 11A as the output shaft of the servo motor 106 is connected by the Π2, and the connecting shaft 112 is supported by the bearing 114 and the bearing in the fixed body casing 117. The circumferential surface is 11 7A. The figure (2; and the body 17 of the body 104 is constituted, and the work is in the plane of the mechanical body plane, the third connection in the fixed servo horse is independent of the reduction: fixing the reducer I) 〇 and connecting shaft 1 1 6 and shaft -8- 200950924 The inner circumferential surface 117A, the bearings 114, 116 and the connecting shaft 112 described above are mutually restricted by bolting engagement (sPig〇tj oint) or buckle In the axial direction, the connecting shaft 112 is formed by directly cutting the pinion gear 12 12P at the front end thereof, and forming a concave portion 11 2A at the other end (opposite side of the front end side). The concave portion 11 2A is coupled by a key. There is a front end of the aforementioned motor shaft 110, not only that The key is formed by the small screw (not shown in the drawing) and does not fall off. Thus, the 'motor shaft 11' and the connecting shaft 112 are fixed in the rotational direction. Further, the front end of the connecting shaft 112 is directly The pinion gear 1 1 2P formed by the cutting is engaged with the bevel gear 118. Thus, the inside of the fixed body 104 (inside the fixed body casing 117) constitutes a speed reduction mechanism by the pinion gear 112P and the bevel gear 118. The bevel gear 118 is fixed at the center end (the end on the fixed body 104 side) of the input shaft 122 of the speed reducer 102, and is fixed by the bolt 120. Further, the meshing between the pinion gear 112P and the bevel gear 118 is The configuration is such that a specific angle α is formed between the axes of the respective axes (the axis 02 of the pinion gear 1 12P and the Φ axis of the bevel gear 1 18:). In the present embodiment, the angle α is 1 10°. The inside of the fixed body 104 is formed by the presence of the oil seal 146 and the 0-rings 144, 180, and 184. The structure of the reducer is reduced. The power (rotational force) of 122 is decelerated and output. This embodiment The reduction gear 1 0 2 is a so-called eccentric rocking type internal meshing planetary gear reducer. 200950924 An eccentric body 124 is integrally formed on the input shaft 122 that can rotate the shaft center 作为! In the embodiment, the eccentric body 124 is formed in three pieces and each has a phase difference of about 120. Further, although the eccentric body bearing 126 and the external gear wheel 128 are respectively formed into three groups according to the above configuration, The invention is not limited to this configuration. Even if the external gears 128 and the like are one set, two sets, or four or more sets depending on the transmission capacity required by the reducer or the like. The eccentric body 124 is fitted to the center hole 128 of the externally toothed gear 128 through the eccentric body bearing 126. The externally toothed gear 128 engages the center hole 12 8 本身 of the eccentric body bearing 126 and engages the internal teeth of the internal gear (in the present embodiment, corresponds to the outer pin 130). Further, in the externally toothed gear 128, a plurality of inner pin holes 128B are provided at different positions in the circumferential direction (only one is shown in the drawing). The inner pin 138 is loosely fitted to the inner pin hole 128B through the inner roller 140. The inner roller 140 is free to rotate relative to the inner pin 138. Further, the outer pin 130 engaged with the externally toothed gear 128 is provided in plural in the inner peripheral surface of the reduction gear casing 132. Although it does not appear in the drawing, the number of teeth of the external gear 128 and the number of the outer pins 130 are set to be small (about 1 to 3). The inner pin 138 in the present embodiment is formed integrally with the disk-shaped first flange 134. Further, the inner pin 138 is coupled and fixed to the disk-shaped second flange 136 by the bolt 162. That is, the inner pin 138 is integrated with the first and second flanges 134, 136. Further, a bearing-10-200950924 156 is disposed between the first flange 134 and the input shaft 122, and a bearing 158 is disposed between the second flange 136 and the input shaft 122, and the first flange 134 and the reduction case are disposed. A bearing 148' is disposed between 132, and a bearing 150 is disposed between the second flange 136 and the reduction housing 132, and the cover 152 is disposed to cover the second flange 136'. The cover 152 is fixed by the bolt 154. Reducer housing 132. Further, reference numeral 132A is a bolt hole for attaching a tool magazine to be described later to the reduction case 132. Further, the inside of the reduction gearbox 102 is formed by the presence of the oil seals 142, 146 and the 〇-type φ ring 182, thereby forming an independent sealed space. <Connection between Reducer and Fixing Body> The connection between the reducer 102 and the fixed body 104 is "connecting the first flange (non-rotating member) 134 and the fixed body casing 1 in the present embodiment" 17" bolts 160 are realized. As described above, since the first flange 134 is coupled and fixed to the second flange 136 through the integrally formed inner pin 138, the inner pin 138 or the second flange 136 is actually coupled and fixed to the fixed body case. 117. According to the above configuration, the rotation input to the input shaft 122 is transmitted through the eccentric body 124, the eccentric body bearing 126, and the external gear 128, and finally the reduction case 132 itself is opposed to the fixed inner pin 138. And the rotation (detailed effect will be explained later). That is, the speed reducer casing 132 itself functions as an output shaft (output portion) of the gear motor 1A. Further, the connecting portion between the speed reducer 102 and the fixed body 1〇4, that is, the connecting surface between the first flange 134 of the speed reducer 102 and the fixed body casing 117 of the fixed body 104 (third) The joint surface 104C) -11 - 200950924 is interposed with a 〇-shaped ring 144. Further, an oil seal 146 is provided between the inner circumferential surface of the first flange I34 and the outer circumferential surface of the input shaft 122. However, although not shown in the drawing, a lubricant (such as butter) is sealed inside the fixed body 104 and the speed reducer 102. <Relationship between Gear Motor and Tool Cassette> Next, the relationship between the gear motor 100 and the tool magazine 17 is shown in Fig. 2 . The tool magazine 170 is composed of a tool magazine body (rotating shaft) 171 and a tool holder 172 that can hold the tool. Further, the tool magazine 170 is connected and fixed to the reduction gear casing 132 by means of a bolt hole 13 2A provided in the reduction casing 132 (output portion) of the reduction gear 102. The tool magazine 170 is attached to the front side (the left side in Fig. 2) of the speed reducer 102 in such a manner as to further cover the cover 152 of the speed reducer 102. The tool magazine 170 is in the form of a disk in the case of a front view (arrow III direction: please refer to Fig. 3). In addition, a plurality of tool holders 172 are arranged at a predetermined interval to form a radial shape (radially in the radial direction centering on the axis 〇). In addition, various types of tool pockets 74 are held in each of the tool holders 172'. <Operation of Gear Motor> Next, the action of the gear motor 100 will be described. Once the rotational command is input to the servo motor 106, the motor shaft 110 will be caused to rotate only by the indicated amount (angle). The rotation of the motor shaft 110 is transmitted to the pinion gear 112P through the connecting shaft 112, and is transmitted to the meshed bevel gear 118. The input shaft 122 of the reduction gearbox 102 is coupled to the bevel gear 118 by -12-200950924, and the input shaft 122 is rotated. In the present embodiment, "the timing of the transmission from the pinion gear 112P to the bevel gear 118 (timing) is decelerated by the rotation of the motor shaft 11 (speed reduction mechanism). Once the input shaft 122 is rotated, the eccentric body 124 integrally formed on the input shaft 122 will be eccentrically rotated. The eccentric rotation ' of the eccentric body 124 is transmitted to the externally toothed gear 128 through the eccentric body bearing 126. As a result, the outer 0-tooth gear 128 starts to rotate in a state where the axis 0! is shaken. Further, since the externally toothed gear 128 is also engaged with the outer pin 130 to restrict the rotation, almost only the shaking is performed. Further, as described earlier, since only a small amount of difference (number of teeth difference) is provided between the number of teeth of the externally toothed gear 128 and the number of the outer pins 130, the externally toothed gear 128 is formed: once per rocking, only the The amount of the difference in the number of teeth is such that the outer pin 130 forms a rotation. The amount of rotation (relative rotation amount) of the external gear 130 to the outer pin 130 is taken out through the inner pin 138 and the inner roller 140 toward the first and second flanges 134 and 136. However, in the Φ embodiment, since the first flange 134 is fixed to the fixed body casing 117, the relative rotation amount is outputted as the rotation of the reduction gear casing 132. The amount of rocking of the externally toothed gear 128 is offset by the loose fitting between the externally toothed gear 128 and the inner pin 138 (and the inner roller 140). Therefore, only the amount of rotation (relative rotation amount) is taken out. As described above, in the present embodiment, since the first flange 134 is coupled and fixed to the fixed body casing 117, the relative amount of rotation is outputted in a state in which the reduction casing 132 rotates. That is, the tool magazine 170 fixed to the reduction housing 132 is caused to rotate. • 13- 200950924 In this way, in the gear motor 100, the direction of the joint surface 104A (in the first figure, the servo motor 6 is detachably attached to the fixed body 104 connected to the speed machine 102, and the servo magazine 170 is reduced. In the front surface (that is, the front side of the working machine and the operator side), the depth of the machine is reduced in size, and the workability of the maintenance and repair of the tool 174 can be taken into consideration. Moreover, the rotational position of the tool magazine 170 is not dependent. The cam mechanism or the like, that is, 170 is coupled to the output shaft speed housing 132) of the speed reducer 102, and further to the servo horse 102 to form a rotational position (stop position) of the rotary tool magazine 170 of the servo motor 106. Rather than the coarse positioning of the cam mechanism, the minimum unit of the rotation detection accuracy of the 1 06 can be performed by the deceleration of the machine 102 between the pinion 112P and the bevel gear 118. In the case where the cam mechanism is used for the position, the design of the cam mechanism is changed once the pitch of the adjacent tool holder 172 is changed due to a design change or the like. (譬 changing the pitch of the cam groove so that the added tool is formed by the machine body 1〇8 and the subtraction motor 106 from the Z-direction·up-and-down direction) protrudes from the tool, so that the work clothes motor can be made. The maintenance of the maintenance (stop position) is achieved by the tool magazine (which is used in the embodiment to reduce the accuracy of the deceleration maneuver detection by 106), that is, the servo can be formed. The positioning of the motor. Moreover, the deceleration portion and the rotation detecting tool holder 172 of the reduction motor 106 are more than the tool holder 172, so it must be matched as follows: Specific -1450924 location). However, according to the structure of the present embodiment, regardless of the change in the pitch of the adjacent tool holders 172, it can be directly used without changing the design of the gear motor 1 . Further, in the present embodiment, an eccentric rocking type internal meshing planetary gear reducer having self-locking property is employed as the speed reducer 102. In this way, the tool holder 172 can be held at a specific rotational position only by the ΟΝ/OFF of the rotation of the servo motor 106 without specifically providing a brake mechanism or the like. Of course, it is also possible to additionally set the brake mechanism, etc., in order to be more certain. Further, in the present embodiment, the tool magazine 170 is provided with the rotation axis (consistent with the axis 0) of the tool magazine 170 as a center, and the tool can be held at each specific interval in the radial direction. (pitch) G. Moreover, the servo motor 1 〇 6 is detachable from the tool holder 1 72 (interval G) (please refer to Fig. 3). By constituting the above description, the loading and unloading operation of the servo motor 1〇6 can be made easier. Further, in the present embodiment, the fixed body 104 (the fixed body case 117) has a box-like appearance, and one of the first connecting faces 104A is formed to be coupled to the main body 108 of the working machine, and the other side is formed with the servo. The second connecting surface 104B to which the motor 106 is connected has a third connecting surface 104C that is connected to the speed reducer 1〇2. Thus, the fixing body 104 and the speed reducer 102 are left on the side of the body 108 of the machine tool, so that only the servo motor 1〇6 can be attached and detached. Further, in the present embodiment, the third joint surface 104C connected to the speed reducer 102 is inclined to the first joint surface 104A that is coupled to the main body 108 of the machine tool. By adopting the above configuration, the yoke 172-200950924 can be easily placed in a specific direction (angle). Further, in the present embodiment, the oil seal 1 46 is provided at the joint portion between the speed reducer 1〇2 and the fixed body 104, and the lubricant sealed in each of the interiors is isolated. In this way, it is possible to securely secure the lubricant (the amount (the optimum amount) to be held inside the reducer 102), and to securely ensure the amount (the optimum amount to be held inside the fixed body 104). Lubricant. For example, the reducer 102 encloses a lubricant "to the extent that the bearing 148 and the bearing 150 as a whole are immersed", and is formed in the fixed body 104 only to the extent that the lower end of the bevel gear 118 is immersed, thereby reducing the loss of agitation. In this case, the lubricant enclosed in the reducer 102 may be different from the lubricant enclosed in the fixed body 104. That is to say, the optimum lubricant corresponding to the characteristics of each part can be used by the separated state. Further, in the present embodiment, the deceleration in the fixed body 104 is composed of a pinion (first bevel gear) 112P disposed on the servo motor 106 side and a bevel gear (second umbrella) disposed on the side of the reducer 102. The gear wheel is realized, and the bevel gear 118 is detachably mounted to the input shaft 122 of the speed reducer 102. By adopting the above configuration, the design change of the angle α (the angle α formed by the axes 01 and 〇2) can be easily made. Further, in the present embodiment, on the input shaft 122 of the speed reducer 102, a hexagonal wrench hole 164 (rotation preventing member mounting portion) is formed on the opposite side of the axial direction of the bevel gear 118 mounting position, and the hexagonal wrench hole 164 ( The rotation preventing member attaching portion can prevent the rotation of the input shaft 122 when the bevel gear 118 is attached to the input shaft 122. In this way, when the loading and unloading of the bevel gear 118 (loading and unloading of the input shaft 122) is performed, the input shaft 122 can be easily prevented from being inadvertently rotated, making the loading and unloading operation practical and easy [industrial Utilities] The NC work machine is the first tool for the tool magazine drive that can automatically replace a plurality of types of tools to perform work. BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a side cross-sectional view showing a gear motor as an example of an embodiment of the present invention. Fig. 2 is a side cross-sectional view showing a gear motor in a state in which a tool magazine is mounted. Figure 3: Front view of the tool magazine (arrow 3 in Figure 2). Fig. 4 is a view showing a partial φ of the machine tool described in Patent Document 1. Fig. 5 is an overall image of the working machine described in Patent Document 1. [Description of main component symbols] 100: Gear motor 102: Reducer 104: Fixed body 104A: First connecting surface -17- 200950924 104B: Second connecting surface 104C: Third connecting surface 106: Servo motor 108: Working machine body 1 1 〇: motor shaft 1 12 : connecting shaft 1 12A : recess 1 12P : pinion 114 , 116 , 148 , 150 , 156 , 158 : bearing 1 1 7 : fixed body housing 1 1 7 A : inner peripheral surface 1 1 8 : Bevel gears 120 , 154 , 160 , 162 : Bolts 122 : Input shaft 1 2 4 : Eccentric body 1 2 6 : Eccentric body bearing 1 2 8 : External gear 1 2 8 A : Center hole 1 2 8 B : Inside Pin hole 1 3 0 : Outer pin 1 3 2 : Reducer housing 1 3 2 A : Bolt hole 134: 1st flange (non-rotating member) 136 : 2nd flange -18- 200950924 138 : Domestic pin 140 : Internal roll Sub 142, 146: Oil seal 1 5 2 : Cover 1 6 4 : Hex wrench hole 1 70 : Tool magazine 匣 1 72 : Tool holder
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