201000786 六、發明說明： 【發明所屬之技術領域】 本發明係關於將減速機連結在對象機械（被驅動機械 )用之減速機的輸出部構造。 【先前技術】 減速機係將電動機等驅動源的旋轉予以減速，且傳達 到對象機械的被驅動軸。因此，在減速機的輸出側，必須 將減速機的本體外殼（固定系統）連結在對象機械的連結 外殼。又，必須連結減速機的輸出構件（旋轉系統）和對 象機械的被驅動軸。 第3圖係顯示專利文獻1所揭示之減速機2。 在減速機2的本體外殼4的内周4A配置一對之軸承 6、8’透過該一對之軸承6、8，將輸出構件10旋轉自如 地支撐在本體外殼4。 於此基本構成之下，利用形成在減速機2的本體外殼 4的外周4B之收納部（印盒部）E1，將該減速機2的本 體外殼（固定系統）4連結在對象機械12的連結外殻14 。此外’該明細書中，所謂「收納部」係提供2個構件抵 接時各構件安裝位置的基準用之嵌合部之意。即，藉由形 成在減速機2的本體外殼4的外周4B之收納部e 1和對象 機械12的連結外殼14的内周14A嵌合之方式，進行減速 機2的本體外殼4和對象機械12的連結外殼14之軸心對 準及軸方向對位。 -5- 201000786 又，透過軸承6、8支撐在本體外殼4的輸出 旋轉系統）1 〇 ’在此專利文獻1相關之例中’係作 之輸出軸之構成’透過無圖示之鍵連結對象機械1 驅動軸（省略圖示）。 〔專利文獻1〕日本特開2006-2263 47號公報 【發明內容】 但是，在這種輸出部構造’例如減速機的本體 外周爲了作爲收納部之功能’必須有正確加工。又 外殼的内周也構成軸承之承受面’因此終究須有精 。支撐輸出構件之軸承可使用泛用品、内製品，包 (鬆動）之尺寸管理’必須針對其内輪、外輪、轉 部有相符之尺寸管理。再者’輸出構件的外周當然 有精密加工。 換言之，若不適當地管理減速機的本體外殼之 内周、軸承的外輪之外周及内周、轉動體之徑、軸 輪之外周及内周、及輸出構件的外周，亦即全部的 向尺寸，則減速機的本體外殼的軸心和對象機械的 殼的軸心，或減速機的輸出構件的軸心和對象機械 動軸的軸心，將因誤差累積而無法正確地一致。因 於上述各部製造時的尺寸管理要求嚴密之管理，且 多，而容易提高製造成本。 本發明係爲了解決這種以往之問題而發明者， 在於減少零件數並緩和製造時的尺寸管理，而得以 構件（ 爲中實 2的被 外殼的 —Jr- ，本體 密加工 含游隙 動體全 必須也 外周及 承的内 半徑方 連結外 的被驅 此，對 零件數 其課題 低成本 -6- 201000786 且正確之尺寸精確度連結減速機和對象機械。 本發明係於使減速機可安裝在被驅動機械所構成之減 速機的輸出部構造，具備：構成軸承的内輪之内輪構件、 構成前述軸承的轉動體之轉動構件、及構成前述軸承的外 輪之外輪構件，前述内輪構件係作爲前述減速機的輸出構 件而連結前述對象機械的被驅動軸側，前述外輪構件係作 爲提供當減速機的本體外殼的内周及前述對象機械的連結 外殼的内周嵌合安裝時的基準用之收納部的功能，前述軸 承係藉由前述内輪構件、轉動構件、及外輪構件，承受前 述内輪構件及連結該内輪構件的前述被驅動軸之兩方向之 軸向荷重，藉此方式解決上述課題。 根據本發明，輸出側全體構成巨大的軸承，該軸承的 内輪係作爲輸出構件之功能，且外輪的外周係直接作爲減 速機的本體外殼及對象機械的連結外殼雙方之收納部之功 能°因此’可降低零件數且降低被要求精密的尺寸管理之 部位數’而可維持低成本且正確之尺寸精確度。 根據本發明，可緩和製造時的尺寸管理及零件管理， 以低成本且正確的尺寸精確度連結減速機和對象機械。 【實施方式】 以>下一邊參照圖面，一邊詳細地說明關於本發明之實 施形態之一例。 H 1 Η係顯示本發明之實施形態之一例所相關之減速 機的輸出部構造之剖視圖。此例中，顯示與電動機2〇 一 201000786 體化之減速機22被連結在對象機械（被驅震 樣子。 電動機20係於電動機外殻26的凸緣部 栓（省略圖示：僅圖示中心線）連結減速機 體外殻28。電動機20的電動機軸32係連結 機構3 4之連接軸3 6。連接軸3 6係透過球朝 減速機22的第1本體外殼28。在連接軸36 ’壓入相當於減速機22的輸入軸之恆星齒輪 減速機22具備單純遊星齒輪機構之減另 部30具備：前述恆星齒輪38、在該恆星齒輯 自轉一邊公轉之複數的遊星齒輪42、及該遊 接嚙合之内齒齒輪44。遊星齒輪42係透過金[Technical Field] The present invention relates to an output portion structure of a speed reducer for connecting a speed reducer to a target machine (driven machine). [Prior Art] The speed reducer decelerates the rotation of a drive source such as a motor and transmits it to the driven shaft of the target machine. Therefore, on the output side of the reducer, the main body casing (fixed system) of the reducer must be connected to the joint casing of the target machine. Further, it is necessary to connect the output member (rotation system) of the reducer and the driven shaft of the object machine. Fig. 3 shows a speed reducer 2 disclosed in Patent Document 1. A pair of bearings 6 and 8' are disposed on the inner circumference 4A of the main body casing 4 of the reduction gear 2, and the output members 10 are rotatably supported by the main body casing 4 through the pair of bearings 6 and 8. With this basic configuration, the main body casing (fixing system) 4 of the reduction gear 2 is coupled to the connection of the target machine 12 by the accommodating portion (printing box portion) E1 formed on the outer periphery 4B of the main body casing 4 of the reduction gear 2 . Housing 14. In addition, in the detailed description, the "storage unit" is intended to provide a fitting portion for the reference of the mounting position of each member when the two members are in contact with each other. In other words, the main body casing 4 of the reduction gear 2 and the target machine 12 are formed such that the accommodating portion e 1 formed on the outer periphery 4B of the main body casing 4 of the reduction gear 2 and the inner periphery 14A of the connection casing 14 of the target machine 12 are fitted. The axis of the joint housing 14 is aligned and aligned in the axial direction. -5- 201000786 Further, the output rotation system of the main body casing 4 is supported by the bearings 6 and 8). In the example related to Patent Document 1, the "configuration of the output shaft" is transmitted through a key connection object (not shown). Machine 1 drive shaft (not shown). [Patent Document 1] Japanese Laid-Open Patent Publication No. 2006-2263 47. SUMMARY OF THE INVENTION However, in such an output unit structure, for example, the outer periphery of the main body of the reduction gear must be correctly processed in order to function as a storage portion. Moreover, the inner circumference of the outer casing also constitutes the bearing surface of the bearing, so it must be refined after all. Bearings that support the output member can use pan-products and internal products, and the size management of the package (loose) must be consistent with the size management of the inner, outer, and rotating parts. Furthermore, the outer periphery of the output member is of course precision machined. In other words, if the inner circumference of the main body casing of the reducer, the outer circumference and the inner circumference of the outer ring of the bearing, the diameter of the rotating body, the outer circumference and the inner circumference of the shaft wheel, and the outer circumference of the output member, that is, the entire dimension, are improperly managed Then, the axis of the body casing of the reducer and the axis of the casing of the target machine, or the axis of the output member of the reducer and the axis of the target mechanical axis, may not be correctly aligned due to the accumulation of errors. Since the dimensional management of the above-mentioned various parts is required to be strictly managed, there are many, and it is easy to increase the manufacturing cost. The present invention has been made in order to solve such a conventional problem, and is to reduce the number of parts and to alleviate the dimensional management during manufacture, and to obtain a member (the Jr- of the outer casing of the middle solid 2) It is necessary to drive the outside of the outer circumference and the inner radius of the bearing. The number of parts is low cost -6- 201000786 and the correct dimensional accuracy is used to connect the reducer and the target machine. The present invention is capable of installing the reducer. The output portion of the reduction gear that is configured by the driven machine includes an inner ring member that constitutes an inner ring of the bearing, a rotating member that constitutes a rotating body of the bearing, and an outer wheel outer ring member that constitutes the bearing, and the inner ring member is the aforementioned The output member of the reduction gear is connected to the driven shaft side of the target machine, and the outer wheel member serves as a reference for providing the inner circumference of the main body casing of the reduction gear and the inner circumference of the connection casing of the target machine. The function of the part, the bearing is received by the inner wheel member, the rotating member, and the outer wheel member The above problem is solved by the axial load of the two directions of the driven shaft that connects the inner ring member. According to the present invention, the entire output side constitutes a huge bearing, and the inner wheel of the bearing functions as an output member, and The outer circumference of the outer ring directly functions as a housing portion of both the main body casing of the reducer and the connecting casing of the target machine. Therefore, the number of parts can be reduced and the number of parts required for precise dimensional management can be reduced, and the cost can be maintained at a low cost. According to the present invention, the size control and the parts management at the time of manufacture can be alleviated, and the speed reducer and the target machine can be coupled at a low cost and with accurate dimensional accuracy. [Embodiment] The following is detailed with reference to the drawing side. An example of an embodiment of the present invention is described. The H 1 Η system shows a cross-sectional view of the structure of the output unit of the speed reducer according to an embodiment of the present invention. In this example, the display is decelerated with the motor 2〇201000786. The machine 22 is coupled to the target machine (the shock is applied. The motor 20 is attached to the flange of the motor casing 26). The pin (not shown in the figure: only the center line is shown) is connected to the reduction body casing 28. The motor shaft 32 of the motor 20 is the connection shaft 36 of the connection mechanism 34. The connection shaft 36 is the first through the ball toward the reduction gear 22. The main body casing 28. The sun gear reducer 22 that presses the input shaft corresponding to the input shaft of the reduction gear 22 to the connecting shaft 36' includes a simple planetary gear mechanism. The reduction unit 30 includes the sun gear 38 and revolves while the star gear rotates. The plurality of star gears 42 and the meshing internal gear 44. The star gear 42 is transmitted through the gold
支搏在遊星銷45。遊星銷45被支撐在運載J 運載具48係與遊星齒輪42之公轉同步地自 運載具48係由運載板48八和運載銷48B所 栓60而被締結、固定在後述内輪構件54。 22係以蓮載具48及内輪構件54構成輸出構 54取出運載具48之旋轉作爲該減速機 轉。此外，内齒齒輪44係與減速機22的第 一體化。 减速機22係於連結著電動機20之狀態 體外殼46的螺栓***孔49***螺栓（省略 締結 '阖定在對象機械24的連結外殼5〇。 以下詳細地說明關於該減速機2 2的輸出 iil機械）2 4的 2 6 A，透過螺 2 2的第1本 具備摩擦締結 j承40支撐在 的中空部3 6 A 38 ° g部3 0。減速 | 38周圍一邊 星齒輪42内 f軸承43而被 _ 48。因此， 轉。此例中， 構成，透過螺 即，該減速機 件，且從内輪 ;22之輸出旋 2本體外殼46 下，在第2本 圖示），而被 部構造。 -8- 201000786 該輸出部構造係具備大軸承5 2作爲其主要構成要素 。該大軸承52具備：構成該大軸承52内輪之内輪構件54 、構成該大軸承52轉動體之轉動構件56、及構成該大軸 承5 2外輪之外輪構件5 8。 大軸承5 2的内輪構件5 4係大致圓柱狀之塊體，如前 述地透過螺栓60連結減速部30的前述運載具48，與該運 載具4 8 —起作爲減速機2 2的「輸出構件」之功能。本實 施形態中，藉由透過螺栓6 4從圖式之左側將輸出軸塊6 2 附設在該内輪構件54，且透過鍵（僅圖示鍵溝62A)連結 在對象機械24之無圖示之被驅動軸側的方式，構成傳達 動力。此外，取代附設有輸出軸塊6 2之動力傳達，例如 亦可利用螺栓64的螺栓孔66，作爲將對象機械24的被驅 動軸連結直接内輪構件54之構成。在内輪構件54形成有 組入轉動構件56用的打開度90度之V型溝54A，在後述 外輪構件58亦形成有對應之打開度90度之V型溝58 A。 大軸承5 2的轉動構件5 6係由直徑和軸長相等的輥（ 省略圖示）所構成，將該輥交互地改變90度方向組入前 述内輪構件54的V型溝54A和外輪構件58的V型溝 58A之間之構成。藉此，大軸承52全體構成所謂的十字 輥軸承。在十字輥軸承，轉動構件5 6的軌道平面（與包 含轉動構件56的重心之軸ΟΙ垂直的平面）T1爲僅存在 有1面，且在構造上，可承受徑向荷重和兩方向之軸向荷 重全部。此外，該轉動構件56係透過朝半徑方向貫通形 成在一部分之外輪構件5 8的組入孔7 1，各組入1個。 -9- 201000786 大軸承52的外輪構件5 8係兼用爲減速機22的端部 外殼之功能。外輪構件5 8的外周5 8B係設計成無階差之 單純圓筒形狀。本實施形態中，利用將該外輪構件5 8的 外周5 8 B設計成無階差之單純圓筒形狀，藉由所謂的無心 硏削盤（無心磨床：Centerless grinder )硏削加工該外輪 構件5 8的外周5 8 B。作爲無心硏削盤，眾知有利用工件 支架（省略圖示）支撐工件（本例中爲外輪構件5 8 )，用 2個磨石進行硏削者，可加工至極爲正圓。 外輪構件58的外周58B係作爲嵌合減速機22的第2 本體外殼46的内周46A (之一部分）之減速機側收納部 E2及嵌合對象機械24的連結外殼50的内周50A (之一部 分）之對象機械側收納部E3之功能。即，藉由該減速機 側收納部E2及對象機械側收納部E3之功能，使第2本體 外殼46及大軸承52之各軸心01 —致。又，藉由對象機 械24的連結外殼50的端面50C抵接第2本體外殻46的 凸緣部46B的端面46C，使連結外殻50的外輪構件58的 外周58B上之軸方向定位得以形成。此外，第2本體外殼 46的凸緣部46B並未形成在該第2本體外殼46的圓周方 向全體，而是於所謂的「耳部」之態樣下，在圓周方向的 4個部位，朝軸方向若干延伸並朝半徑方向突出形成。 從第1圖得知，本實施形態中，外輪構件5 8的外周 5 8B大半係嵌合對象機械24的連結外殼50。即，外輪構 件58的外周58B大半係作爲對象機械24的連結外殼5〇 之收納部之功能。 -10- 201000786 從其與轉動構件5 6之關係來看，在外輪構件5 8的外 周5 8B，減速機側收納部E2和對象機械側收納部E3之中 ’對象機械側收納部E3被設定成較長。又，形成爲前述 轉動構件5 6的軌道平面T 1被收納在該設定成較長之對象 機械側收納部E3的半徑方向内側。 此外，本實施形態係輸出部構成爲全體形成大軸承者 ’内輪構件5 4及外輪構件5 8並非以所謂「軸承鋼」形成 。因而，轉動構件56的轉送面（内輪構件54之V型溝 54A、外輪構件58之V型溝58A )必須有另外的硬化處理 。因此’該V型溝54A、58A附近由於素材變硬，因此遊 星銷45的銷孔47或螺栓孔66等各孔類必須避免在此變 硬的附近進行加工’注意不要形成「貫通孔」，結果爲在 軟的部分容易地且高精確度地形成各孔類。形狀方面，其 結果爲在内輪構件54存在有完全未形成孔的（完全中實 的）軸和直角的剖面P 1。 此外，第1圖的符號70係爲了密封減速機2 2内外而 配置在内輪構件54和外輪構件58之間的油封。 接著’說明具有上述輸出部構造之齒輪傳動電動機之 作用。 電動機20的輸出軸32旋轉時，透過連接軸36，減速 機22的輸入軸亦即恆星齒輪38旋轉。在該減速機22，由 於減速部3 0的内齒齒輪4 4處於固定狀態，因此遊星齒輪 42的公轉成分從運載具48被取出。運載具48係透過螺栓 60而與大軸承52的内輪構件54 —體化，内輪構件54係 -11 - 201000786 透過螺栓64而和輸出軸塊62連結，因此結果爲輸出軸塊 62旋轉，且透過無圖示之鍵，對象機械的被驅動軸旋轉。 其中，内輪構件54係透過十字輥型之轉動構件56而 被支撐在外輪構件5 8，因此可承受徑向荷重和兩方向之軸 向荷重全部，結果爲可對應内輪構件5 4的軸振擺（轉矩 成分）。 又，運載具48(運載板48A及運載銷48B)係與此被 安定支撐的内輪構件54 —體化，因此也可省略運載板 48A外周的軸承。 再者，十字輥型之轉動構件56係藉由互相錯開90度 地組入之「輥」所構成，因此大致沒有鬆動（内輪構件5 4 及外輪構件5 8之間的游隙），可以高組裝精確度組入内 輪構件54及外輪構件58。又，轉動構件56的軌道平面 T1只有1面，因此必要時可將大軸承52軸方向厚度設計 成更薄。 外輪構件58係其外周58B活用被設計成無階差之單 純圓筒形狀，而利用無心硏削盤硏削加工，因此可進行極 爲接近正圓之加工。又，外輪構件5 8係以該接近正圓之 外周58B嵌合在減速機22的第2本體外殼46的凸緣部 46B及對象機械24的連結外殼50。其中，減速機22的第 2本體外殻46被嵌合的減速機側收納部E2、及對象機械 24的連結外殼5 0被嵌合的對象機械側收納部E 3之中， 對象機械側收納部E3被設定成較長（實際上是在外周 5 8 B的大致全面）。因此，結果是外輪構件5 8通過其接 -12- 201000786 近正圓之外周5 8B的大致全面被嵌合支撐。特別是本實 形態中，不是「減速機22」被嵌合的減速機側收納部 ，而是將「對象機械24」被嵌合的對象機械側收納部 設定成較長，因此是藉由所謂對象機械之質量大的構件 被嵌合支撐。因此，可直接利用對象機械的連結外殼的 性作爲支撐基礎，而可確保更高的剛性。 再者，如此地在以高剛性被安定支撐著的外輪構件 的對象機械側收納部E3半徑方向内側，配置有轉動構 5 6的轉動面T 1，因此（例如相較於收納部軸方向尺寸 而在偏離該收納部軸方向位置之位置的半徑方向内側具 轉動構件5 6的轉動面之構造）可極爲安定地承接從轉 構件5 6側傳達來的徑向負荷或推力負荷、或搖動等力 負荷。 不須與前述習知例詳細比較，本實施形態中可將被 求嚴格管理尺寸的加工面數抑制在最小限度，如此則誤 累積少，可確保高尺寸精確度之組裝。The beat is sold at 45. The star-shaped pin 45 is supported by the carrier J, and the carrier 48 is engaged with the carrier 48 by the carrier plate 48 and the carrier pin 48B, and is fixed to an inner wheel member 54 which will be described later. In the 22 series, the rotation of the speed reducer is performed by the lotus carrier 48 and the inner wheel member 54 constituting the output structure 54. Further, the internally toothed gear 44 is integrated with the first of the speed reducer 22. The reduction gear 22 is inserted into the bolt insertion hole 49 of the state outer casing 46 to which the electric motor 20 is coupled. (The connection is not made to the connection housing 5 of the target machine 24. The output iil of the reduction gear 2 2 will be described in detail below. Mechanically) 2 4 of 2 6 A, the first part of the snail 2 2 is provided with a frictional junction j-bearing 40 supported by the hollow portion 3 6 A 38 ° g portion 30. Deceleration | 38 around the star gear 42 inside the f bearing 43 and _ 48. Therefore, turn. In this example, the structure is transmitted through the screw, that is, the reduction gear member is rotated from the output of the inner wheel 22 to the main body casing 46, and is shown in the second embodiment. -8- 201000786 This output unit structure has a large bearing 52 as its main component. The large bearing 52 includes an inner ring member 54 that constitutes the inner ring of the large bearing 52, a rotating member 56 that constitutes the rotating body of the large bearing 52, and an outer wheel member 58 that constitutes the outer bearing 52. The inner ring member 504 of the large bearing 52 is a substantially cylindrical block, and the carrier 48 that is coupled to the speed reducing portion 30 via the bolt 60 as described above is used as the "output member" of the speed reducer 2 2 together with the carrier 48. The function. In the present embodiment, the output shaft block 6 2 is attached to the inner ring member 54 from the left side of the drawing through the through-bolt 64, and the transmission key (only the key groove 62A is shown) is coupled to the target machine 24 (not shown). The way to be driven on the side of the shaft constitutes the transmission of power. Further, instead of the power transmission in which the output shaft block 62 is attached, for example, the bolt hole 66 of the bolt 64 may be used as the configuration in which the driven shaft of the target machine 24 is coupled to the direct inner ring member 54. A V-shaped groove 54A having an opening degree of 90 degrees for assembling the rotating member 56 is formed in the inner ring member 54, and a V-shaped groove 58A having a corresponding opening degree of 90 degrees is formed in the outer ring member 58 which will be described later. The rotating member 56 of the large bearing 52 is composed of a roller (not shown) having the same diameter and axial length, and the roller is alternately changed into the V-shaped groove 54A and the outer ring member 58 of the inner ring member 54 in the 90-degree direction. The configuration between the V-shaped grooves 58A. Thereby, the entire large bearing 52 constitutes a so-called cross roller bearing. In the cross roller bearing, the orbital plane of the rotating member 56 (the plane perpendicular to the axis 包含 including the center of gravity of the rotating member 56) T1 has only one side, and is structurally capable of withstanding the radial load and the axes of both directions. The load is all. Further, the rotating member 56 is formed to pass through one of the grouping holes 711 formed in a part of the outer wheel member 58 in the radial direction. -9- 201000786 The outer ring member 58 of the large bearing 52 also functions as the end casing of the reducer 22. The outer circumference 5 8B of the outer ring member 58 is designed to have a simple cylindrical shape without step. In the present embodiment, the outer circumference member 5 8 B of the outer ring member 58 is designed to have a simple cylindrical shape without step, and the outer wheel member 5 is honed by a so-called centerless grinder (Centerless grinder). The outer circumference of 8 is 5 8 B. As a centerless boring disc, it is known that a workpiece holder (not shown) supports a workpiece (in this example, an outer wheel member 58), and if it is smashed with two grindstones, it can be processed to a very perfect circle. The outer circumference 58B of the outer ring member 58 serves as the reduction gear side housing portion E2 of the inner circumference 46A (one part) of the second main body casing 46 of the fitting reduction gear 22, and the inner circumference 50A of the coupling housing 50 of the fitting target machine 24 ( Part of the function of the object machine side housing portion E3. In other words, the respective axial centers 01 of the second main body casing 46 and the large bearing 52 are aligned by the functions of the reduction gear side accommodating portion E2 and the target machine side accommodating portion E3. Further, the end surface 50C of the connecting casing 50 of the target machine 24 abuts against the end surface 46C of the flange portion 46B of the second main body casing 46, so that the axial direction of the outer circumference 58B of the outer casing member 58 of the coupling casing 50 is positioned. . Further, the flange portion 46B of the second main body casing 46 is not formed in the entire circumferential direction of the second main body casing 46, but in the so-called "ear portion", in the four portions in the circumferential direction, The axial direction extends somewhat and protrudes in a radial direction. As is apparent from Fig. 1, in the present embodiment, the outer circumference of the outer ring member 58 is mostly connected to the outer casing 50 of the fitting machine 24 . In other words, most of the outer circumference 58B of the outer ring member 58 functions as a housing portion of the target casing 24 that connects the outer casing 5'. -10-201000786 From the relationship with the rotating member 56, the target mechanical side housing portion E3 is set in the outer circumference 58 8B of the outer ring member 58 and the reduction gear side housing portion E2 and the target machine side housing portion E3. It is longer. Further, the track plane T 1 formed as the above-described rotating member 56 is accommodated in the radial direction inner side of the target mechanical side housing portion E3 which is set to be long. Further, in the present embodiment, the output portion is configured to form a large bearing as a whole. The inner ring member 514 and the outer ring member 58 are not formed of so-called "bearing steel". Therefore, the transfer surface of the rotating member 56 (the V-shaped groove 54A of the inner ring member 54 and the V-shaped groove 58A of the outer ring member 58) must be additionally hardened. Therefore, since the material is hardened in the vicinity of the V-shaped grooves 54A and 58A, the holes such as the pin holes 47 or the bolt holes 66 of the star-shaped pin 45 must be prevented from being processed in the vicinity of the hardened portion. As a result, each of the pores is easily and highly accurately formed in the soft portion. In terms of shape, as a result, there is a (completely medium-solid) shaft and a right-angled cross section P 1 in which the inner ring member 54 is completely unformed. Further, reference numeral 70 in Fig. 1 is an oil seal disposed between the inner ring member 54 and the outer ring member 58 in order to seal the inside and outside of the reduction gear 2 2 . Next, the function of the geared motor having the above-described output portion configuration will be described. When the output shaft 32 of the motor 20 rotates, the input shaft of the speed reducer 22, that is, the sun gear 38, is rotated through the connecting shaft 36. In the speed reducer 22, since the internal gear 44 of the speed reducing portion 30 is in a fixed state, the revolution component of the planetary gear 42 is taken out from the carrier 48. The carrier 48 is integrally formed with the inner ring member 54 of the large bearing 52 via the bolt 60, and the inner ring member 54 is connected to the output shaft block 62 through the bolt 64, so that the output shaft block 62 rotates and transmits The button of the target machine is rotated by the button without a symbol. Among them, the inner ring member 54 is supported by the outer roller member 5 8 through the cross roller type rotating member 56, so that the radial load and the axial load in both directions can be received, and as a result, the shaft wobble of the inner ring member 54 can be corresponding. (torque component). Further, the carrier 48 (the carrier plate 48A and the carrier pin 48B) is integrated with the internally supported inner wheel member 54. Therefore, the bearing on the outer periphery of the carrier plate 48A can be omitted. Further, since the cross roll type rotating member 56 is constituted by "rollers" which are arranged to be shifted by 90 degrees from each other, there is substantially no looseness (the play between the inner ring member 54 and the outer ring member 58), which can be high. The assembly accuracy is incorporated into the inner wheel member 54 and the outer wheel member 58. Further, since the orbital plane T1 of the rotating member 56 has only one surface, the thickness of the large bearing 52 in the axial direction can be designed to be thinner if necessary. The outer ring member 58 has a single-cylindrical shape in which the outer circumference 58B is designed to have no step difference, and is boring by a centerless boring disc, so that processing which is extremely close to a perfect circle can be performed. Further, the outer ring member 58 is fitted to the flange portion 46B of the second main body casing 46 of the reduction gear 22 and the connecting casing 50 of the target machine 24 by the outer circumference 58B close to the perfect circle. The second main body casing 46 of the reduction gear 22 is fitted to the reduction gear side storage portion E2 and the target machine side storage portion E 3 to which the connection housing 50 of the target machine 24 is fitted. Part E3 is set to be longer (actually at approximately 5 8 B in the periphery). Therefore, as a result, the outer ring member 58 is fitted and supported substantially by the outer circumference of the outer circumference of the outer circumference of the outer circumference of the outer ring member 58 8B. In particular, in the present embodiment, the target machine side housing portion to which the "target machine 24" is fitted is set to be longer than the speed reducer side housing portion in which the "reducer 22" is fitted. The member of the object machine having a large mass is fitted and supported. Therefore, the nature of the joint casing of the target machine can be directly utilized as a support base, and higher rigidity can be ensured. In this way, the rotating surface T1 of the rotating structure 56 is disposed on the inner side in the radial direction of the target machine-side housing portion E3 of the outer ring member that is stably supported by the high rigidity (for example, compared with the axial direction of the housing portion) On the other hand, in the radial direction inward of the position in the axial direction of the accommodating portion, the rotation surface of the rotating member 56 is configured to receive the radial load or the thrust load or the rocking force transmitted from the side of the rotating member 56. Force load. In the present embodiment, it is not necessary to be inferior to the above-described conventional example. In the present embodiment, the number of processing faces that are strictly managed by the size can be minimized, and thus the accumulation of errors is small, and assembly with high dimensional accuracy can be ensured.
此外，上述實施形態中，前述大軸承5 2係全體構 十字輥軸承，但本發明中，不必須是全體構成十字輥軸 。例如如第2圖所示，在内輪構件1 54和外輪構件1 5 8 間，作爲「轉動構件」，配置有：可承接軸方向一方側 軸向荷重之第1轉動構件156A、及與該第1轉動構 15 6A朝軸方向偏離配置且可承接軸方向另一方側的軸 荷重之第2轉動構件156B，大軸承152亦可構成（第1 第2轉動構件156A、156B的軌道平面T101A、T101B 施 E2 E3 而 剛 58 件 短 有 動 矩 要 差 成 承 之 的 件 向 、 存 -13- 201000786 在有2面之）角軸承。於該情形下，大軸承1 5 2係藉由内 輪構件154、第1、第2轉動構件156 A、15 6B、及外輪構 件158，承受全體内輪構件154及與該内輪構件154連結 的對象機械124的被驅動軸（省略圖示）兩方向之軸向荷 重，而獲得與上述同樣的作用效果。 此外，如此地具有 2面轉動構件1 5 6的軌道平面 T 1 0 1 A、T 1 0 1 B之軸承構造的情形下，該雙方之軌道平面 T 1 0 1 A、T 1 0 1 B —起存在被設定成較長的收納部（本實施 形態中爲對象構件側收納部E 1 0 3 )的半徑方向内側即可 。藉此，相輔於各軌道平面T101A、T101B偏離軸方向， 特別是關於内輪構件1 54的軸搖動可獲得良好的支撐特性 〇 關於其他構成，係與先前的實施形態大致同樣，因此 圖中在與第1圖顯示之構成相同或功能相同的部分，在第 2圖中僅只附加下2位爲相同符號，省略重複說明。 此外，上述實施形態中，外輪構件的外周爲無階差之 單純圓筒形狀，（活用此單純形狀）藉由利用無心硏削盤 加以硏削加工，將構成收納部的外輪構件之外周予以高精 確度地加工。但是，本發明中，外輪構件的外周形狀不必 須是無階差之單純圓筒形狀，例如在外輪構件的軸方向途 中中止對象機械的連結外殼之嵌合的情形下形成階差亦可 。即，本發明中，關於對象機械的連結外殼或減速機的本 體外殻對外輪構件的外周之嵌合程度，並無特別限定。即 使在無階差之圓筒形狀的情形下，也不必須將外周全部作 -14- 201000786 爲收納部。 内輪構件的形狀也非受限於上述形狀者，各孔之形成 也（例如在半徑方向有餘裕時等）可以是貫通孔。於該情 形下’可將内輪構件的軸方向長更縮短。 又’減速機之具體的減速部構造也不限定於上述構成 0 本發明可作爲各種減速機之輸出部構造而廣泛利用。 【圖式簡單說明】 第1圖係顯示本發明實施形態之一例的減速機之剖視 圖。 第2圖係顯示本發明另一實施形態之一例的減速機之 剖視圖。 第3圖係顯示以往的減速機之輸出部構造之一例的減 速機之剖視圖。 【主要元件符號說明】 20 :電動機 22 :減速機 24 :對象機械 26 :電動機外殻 28 :第1本體外殼 3 〇 :減速部 32 :電動機軸 -15- 201000786 36 : 38 : 42 : 44 : 46 : 48 : 50 : 52 : 54 : 54 A 56 : 58 : 5 8 A 60、 62 : T1 : E2 ： E3 ： 連接軸 太陽齒車 行星齒車 内齒齒車 第2本體外殼 載體 連結外殻 大軸承 内輪構件 :V型溝 轉動構件 外輪構件 :V型溝 6 4 :螺桿 輸出軸塊 軌道平面 減速機側收納部 對象機械側收納部 -16 -Further, in the above-described embodiment, the large bearing 52 is a cross roller bearing as a whole, but in the present invention, it is not necessary to constitute the cross roller shaft as a whole. For example, as shown in FIG. 2, between the inner ring member 154 and the outer ring member 158, a first rotating member 156A capable of receiving one axial load in the axial direction is disposed as a "rotating member", and 1A rotation mechanism 15 6A is a second rotation member 156B that is disposed to be offset from the axial direction and can receive the axle load on the other side in the axial direction, and the large bearing 152 can also be configured (the orbital planes T101A, T101B of the first and second rotation members 156A and 156B) Apply E2 E3 and just 58 pieces of short and dynamic moments are inferior to the bearing direction, save -13- 201000786 in two sides of the angular bearing. In this case, the large bearing 158 receives the entire inner ring member 154 and the target machine coupled to the inner ring member 154 by the inner ring member 154, the first and second rotating members 156 A and 156B, and the outer ring member 158. The axial load of both directions of the driven shaft (not shown) of 124 is obtained, and the same effects as described above are obtained. Further, in the case of the bearing structure of the track planes T 1 0 1 A, T 1 0 1 B of the two-sided rotating member 156, the orbital planes T 1 0 1 A, T 1 0 1 B — It is sufficient that the storage portion that is set to be long (in the present embodiment, the target member side storage portion E 1 0 3 ) is radially inward. Thereby, the orbital planes T101A and T101B are offset from the axial direction, and in particular, the axial oscillation of the inner ring member 154 can obtain good supporting characteristics. The other configurations are substantially the same as those of the previous embodiment. In the second embodiment, only the lower two bits are denoted by the same reference numerals, and the description thereof will not be repeated. Further, in the above-described embodiment, the outer circumference of the outer ring member is a simple cylindrical shape having no step difference, and (using the simple shape) is boring by the centerless boring disk, and the outer circumference of the outer wheel member constituting the accommodating portion is made high. Processed with precision. However, in the present invention, the outer circumferential shape of the outer ring member does not have to be a simple cylindrical shape having no step difference, and for example, a step may be formed in the case where the fitting of the connecting casing of the target machine is suspended in the axial direction of the outer ring member. In other words, in the present invention, the degree of fitting of the outer casing of the outer casing of the connecting casing of the target machine or the outer casing of the reduction gear is not particularly limited. Even in the case of a cylindrical shape having no step, it is not necessary to make the outer circumference -14-201000786 as the storage portion. The shape of the inner ring member is not limited to the above shape, and the formation of each hole (for example, when there is a margin in the radial direction) may be a through hole. In this case, the axial length of the inner ring member can be shortened. Further, the specific speed reduction portion structure of the reduction gear is not limited to the above configuration. 0 The present invention can be widely used as an output portion structure of various reduction gears. BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a cross-sectional view showing a reduction gear according to an embodiment of the present invention. Fig. 2 is a cross-sectional view showing a reduction gear according to an embodiment of the present invention. Fig. 3 is a cross-sectional view showing a speed reducer which is an example of a structure of an output portion of a conventional reducer. [Description of main component symbols] 20: Motor 22: Reducer 24: Target machine 26: Motor case 28: First body case 3 〇: Reducer 32: Motor shaft -15- 201000786 36 : 38 : 42 : 44 : 46 : 48 : 50 : 52 : 54 : 54 A 56 : 58 : 5 8 A 60 , 62 : T1 : E2 : E3 : Connecting shaft sun gear planetary gear car internal gear 2nd body casing carrier coupling shell large bearing inner wheel Member: V-groove rotating member Outer wheel member: V-groove 6 4 : Screw output shaft block Orbital plane reducer side storage part Object mechanical side storage part -16 -