TW201031831A - Cross roller bearing, angular roller bearing, and method of manufacturing cross roller bearing and angular roller - Google Patents

Cross roller bearing, angular roller bearing, and method of manufacturing cross roller bearing and angular roller Download PDF

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TW201031831A
TW201031831A TW99104745A TW99104745A TW201031831A TW 201031831 A TW201031831 A TW 201031831A TW 99104745 A TW99104745 A TW 99104745A TW 99104745 A TW99104745 A TW 99104745A TW 201031831 A TW201031831 A TW 201031831A
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Taiwan
Prior art keywords
roller bearing
outer ring
ring
inner ring
rings
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TW99104745A
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Chinese (zh)
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TWI390123B (en
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Akira Yamamoto
Mitsuhiro Tamura
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Sumitomo Heavy Industries
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H1/00Toothed gearings for conveying rotary motion
    • F16H1/28Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H1/32Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/36Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers
    • F16C19/361Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers with cylindrical rollers
    • F16C19/362Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers with cylindrical rollers the rollers being crossed within the single row
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00Bearings with rolling contact, for exclusively rotary movement
    • F16C19/54Systems consisting of a plurality of bearings with rolling friction
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2361/00Apparatus or articles in engineering in general
    • F16C2361/61Toothed gear systems, e.g. support of pinion shafts

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

The problem to be solved by the this invention is to provide a cross roller bearing and an angular roller bearing having structures assembled with less components and capable of being separately used according to the required rigidity and installation space. The solution of this invention is to provide a cross roller bearing (14) in which a rolling member (25) being installed between an inner ring (14Ir) and an outer ring (14Or), said bearing is composed by a first outer ring (21), a second outer ring (22), a first inner ring (23) and a second inner ring (24) defined by separately dividing the mentioned inner ring (14Ir) and the outer ring (14Or) through passing a center (26A) of a space (26) surrounded by rolling surfaces (21A-24A) of the inner ring (14Ir) and the outer ring (14Or) and along a plane (P) perpendicular to the axial direction of a member to be supported, and the rolling member (25). Accordingly, a pair of angular roller bearings (16, 18) can be assembled by utilizing the inner rings and the outer rings (21-24) and the rolling member (25).

Description

201031831 六、發明說明: 【發明所屬之技術領域】 本發明是關於交叉滾子軸承、角接觸滾子軸承、以及 交叉滾子軸承與角接觸滾子軸承之製造方法。 【先前技術】 於專利文獻1的第1圖中,揭示有裝入交叉滾子軸承 φ 的減速機。 而且,於同專利文獻的第4圖中,揭示有裝入角接觸 滾子軸承的減速機。 〔專利文獻1〕:日本特開2003-74646號公報(第1 圖、第4圖) 【發明內容】 〔發明欲解決的課題〕 φ 由於上述交叉滾子軸承與角接觸滾子軸承於功能上、 構造上是不同的軸承,内外圏的形狀也不同,故分別個別 地設計或製造。因此,生產成本變高。 本發明要解決的課題在於,減少製造交叉滾子軸承及 角接觸滾子軸承時的零件數量,低成本地提供交叉滾子軸 承及角接觸滾子軸承。 〔用以解決課題的手段〕 本發明藉由如下技術解決上述課題,是在內圈與外圈 -5- 201031831 之間具有滾動體的交叉滾子軸承,使用:上述內圏與外圈 雙方由通過以該內圈與外圈之滾動面圍繞的空間之中心並 沿著與被支承體之軸向垂直的面分別分割的第1、第2內 圈及外圈構成的軸承。 有關交叉滾子軸承,設爲內圈與外圏雙方由通過以該 內圈與外圈之滾動面圍繞的空間之中心,並沿著與被支承 體之軸向垂直的面分別分割的第1、第2內圈及外圈構成 。其結果,使用該交叉滾子軸承所相對的內圈及外圈與滾 @ 動體,可以製造角接觸滾子軸承,故可以減少該軸承的製 造成本。而且,該交叉滾子軸承需要縮短被支承體之尺寸 時,作爲交叉滾子軸承可以使用內圈/外圈及滾動體之零 件,有必要使被支承體之剛性或容量提高時,可以藉由上 述的零件作爲角接觸滾子軸承而使用。 也就是,根據本發明,將交叉滾子軸承之內圈及外圈 及滾動體轉用到角接觸滾子軸承,以共同性較少的零件結 構’配合上述被支承體之剛性、裝入間隔等要求方式的規 ◎ 格,可以低成本地分開使用上述兩軸承。 〔發明效果〕 根據本發明可以減少製造交叉滾子軸承及角接觸滾子 軸承時的零件數量而低成本地提供交叉滾子軸承及角接觸 滾子軸承。 【實施方式】 -6- 201031831 . 以下,基於第1圖說明本發明之一實施例。 首先,對本發明之一實施例之交叉滾子軸承14進行 說明。第1圖(a)表示交叉滾子軸承14之縱剖面圖。 交叉滾子軸承14具有:外圈140r、內圈14 Ir、配置 於該外圈l4〇r與內圈Mir之間的滾子(滾動體)25。 於外圈140r之內周之軸向中央,形成有朝向該外圈 140r本身的內側互相正交的滾動面21A、22A。於內圏 φ 14Ir之外周之軸向中央,形成有:朝向該內圈Mil本身 的內側互相正交的滾動面23 A、24 A。 外圈140r通過以外圈140r與內圏14Ir之滾動面21A 〜24A圍繞的空間26之中心26A,並沿著與插入於該交 叉滾子軸承14之內周側而被支承的被支承體(省略圖示 )之軸向X垂直的面P,分割成2個外圈,也就是第1外 圈21、第2外圈22。第1外圈21、第2外圈22,在與其 軸向X平行的剖面(第1圖所示的剖面),具有:將正方 φ 形之1個頂點以45度切斷的面設爲上述滾動面21A、22A 的形狀。 內圈14Ir,通過以外圈140r與內圈14Ir之滾動面 21 A〜24A圍繞的空間26之中心26A,並沿著與被支承體 (省略圖示)之軸向X垂直的面P分割成2個內圈,也就 是第1內圈23、第2內圏24。第1內圈23、第2內圈24 ,也在與其軸向X平行的剖面(第1圖所示的剖面)’具 有:將正方形之1個頂點以45度切斷的面設爲上述滾動 面23A、24A的形狀。 201031831 也就是說,第1外圈21、第2外圈22及第1內圈23 、第2內圈24的與各軸向X平行的剖面’爲以滾動面 21A〜24A圍繞的空間26的中心26A爲中心設爲點對稱的 形狀。 滾子(滾動體)25’由直徑與高度(滾動體25的軸 向長度)相同(嚴格來說’直徑僅稍微小於高度)的圓筒 狀構成,並每隔1個改變90度方向而裝入。 其次,利用第1圖(b) ’對將該交叉滾子軸承14作 ❹ 爲一對角接觸滾子軸承16、18而有效地利用的情況進行 說明。另外,於第1圖(b)中’對於與第1圖(a)之交 叉滾子軸承14之零件對應的零件(相同的零件)附加相 同的圖號。 其中一方的角接觸滾子軸承16,在第1圖(a)之交 叉滾子軸承14之第1、第2內圈及外圏21〜24中,由上 述滾動面21A、24A所相對的第1外圈21及第2內圈24 、滾子25所構成。滾子25的與構成交叉滾子軸承14的 ❹ 滾子25相同的滾子全部向相同的方向(與傾斜軸向Z1成 爲直角的方向)裝入。 另一方的角接觸滾子軸承18,在第1圖(a)之交叉 滾子軸承14之第1、第2內圈及外圈21〜24中,由上述 滾動面22 A、23A所相對的第2外圈22及第1內圈23、 滾子25所構成。滾子25的與構成交叉滾子軸承14的滾 子25相同的滾子全部向相同的方向(與傾斜軸向z2成爲 直角的方向)裝入。 -8- 201031831 , 藉由上述的交叉滾子軸承14與一對角接觸滾子軸承 16、18之零件之共同使用,可以減少兩軸承14、(16、 18)之零件數量,並且低成本地提供交叉滾子軸承14及 角接觸滾子軸承丨6、18。而且,可以確定交叉滾子軸承 14與角接觸滾子軸承16' 18之製造方法,其特徵爲,由 通過以內圈23、24與外圈21、22之滾動面21A〜24A圍 繞的空間26之中心26A,並沿著與被支承體之軸向X垂 Φ 直的面P分別分割的第1、第2內圈及外圈21〜24與滾 動體25而製造交叉滾子軸承14,並且藉在第1、第2內 圈及外圈21〜24中,由滾動面21A〜24A所相對的一對 內圈24、23、外圈21、22、滾動體25而製造角接觸滾子 軸承1 6、1 8。 另外,於第1圖中,上述交叉滾子軸承14及角接觸 滾子軸承16、18之內圈及外圏21〜24之剖面形狀爲點對 稱,但是該交叉滾子軸承14之內圈及外圈21〜24之剖面 # 形狀不是點對稱也可以。 以下,對於構成交叉滾子軸承14的第1、第2內圈及 外圈21〜24之形狀之組合進行說明。 於第2圖表示交叉滾子軸承14之第1、第2內圈及外 圈21〜24之組合例的簡要剖面圖。 對第2圖所示之實施方式(a)〜(g)進行說明。 於實施方式(a)中,第1、第2內圈及外圈21a〜 24a之剖面形狀的半徑方向之長度12,成爲較軸向之長度 11更長的形狀。而且,其特徵爲,第1外圈21a、第2外 -9 - 201031831 圈22a之外側角部帶有圓度(R)(圓角)。 於實施方式(b)中,內圈及外圈2 lb〜24b之剖面形 狀的軸向之長度13成爲較半徑方向之長度14更長的形狀 。而且,其特徵爲,第1外圈21b、第2外圈22b之外側 角部帶有圓度。 於實施方式(c)中,與實施方式(b)同樣地第2內 圏及外圈22c、24c的軸向之長度13成爲較半徑方向之長 度Μ更長的形狀。而且’其特徵爲,第1外圈21c、第2 φ 外圈22c之外側角部帶有圓度。但是,第1內圈及外圈 21c、23c之軸向之長度15較第2內圈及外圏22c、24c之 軸向之長度13更長,故與實施方式(b)不同。 於實施方式(d)中,交叉滾子軸承14之軸向之長度 爲(第1外圈21d之軸向之長度17) <(第2內圈及外圈 22d、24d之軸向之長度16) <(第1內圈23d之軸向之長 度15)的關係。而且,其特徵爲,第1外圈21d、第2外 圈22d之外側角部帶有圓度。 ❹ 於實施方式(e)中,交叉滾子軸承14之軸向之長度 爲(第1內圈23e之軸向之長度17) <(第2內圏及外圈 22e、24e之軸向之長度16) <(第1外圈21e之軸向之長 度15)的關係。而且,其特徵爲,第1外圈21e、第2外 圈22e之外側角部帶有圓度。 於實施方式(f)中,第1內圈23f的半徑方向之長度 18,較軸向之長度17更長。其他的內圈及外圈21f、22f、 24f的半徑方向之長度17與軸向之長度17均相同。而且 -10- 201031831 .,其特徵爲,第1外圈21f、第2外圈22f之外側角部帶 有圓度。 於實施方式(g)中,第1外圈21g的半徑方向之長 度18,較軸向之長度17更長。第2外圈22g、第1內圈 23g、第2內圈24g之半徑方向之長度17與軸向之長度17 均相同。而且,其特徵爲,第1外圈21g、第2外圈22g 之外側角部帶有圓度。 φ 如此,交叉滾子軸承14a〜14g之各第1、第2內圈及 外圈21a〜24a、第1、第2內圈及外圈21b〜2 4b.....第 1、第2內圈及外圈21g〜2 4g的大小或形狀,由交叉滾子 軸承14a〜14g (或者使用該交叉滾子軸承之零件而構成的 角接觸滾子軸承)裝入於減速機等時的與周邊的構件的關 係,可以適當地進行變更。但是,爲了可將這些交叉滾子 軸承14a〜Mg作爲一對角接觸滾子軸承(省略圖示)而 轉用,各第1、第2內圈及外圈21a〜24a、21b〜24b、… 9 、21g〜24g均有必要通過以各內圈與外圈之滾動面圍繞的 空間26a〜26g之中心26Aa〜26Ag,並沿著與被支承體之 軸向X垂直的面Pa〜Pg被分割。 由此,雖然未圖示,但是各交叉滾子軸承14a〜14g 可以作爲包括滾動面所相對的第1外圈21a〜21g及第2 內圈24a〜24g的角接觸滾子軸承轉用。而且,作爲包括 滾動面所相對的另外一方的第2外圈22a〜22g及第1內 圈23 a〜23g的角接觸滾子軸承可以轉用相同的交叉滾子 軸承14a〜14g。 -11 - 201031831 其次,對將第1圖中所示之交叉滾子軸承14或角接 觸滾子軸承16、18裝入於減速機G1、G2的實施方式之 一實施例進行說明。 於第3圖表示裝入交叉滾子軸承14的減速機G1之縱 剖面圖。 於減速機G1之曲軸(輸入軸)41,一體形成有相位 差120°的3個偏心體42 (42A、42B、42C)。曲軸41透 過一對軸承55、56旋轉自如地支承於輪架48及外殼50。 參 在各偏心體42,隔介著滾子43 ( 43 A、43 B、43 C ) 安裝有3個行星齒輪40 (40A、40B、40C)。該行星齒輪 40分別內接嚙合於內齒輪44。 另外,內齒輪44設爲一體裝入於外殼50之內周側的 結構。 於行星齒輪40向軸向形成多個內滾子孔45 ( 45A、 45B、45C),並且插入內滾子46及內銷47。該內銷47 於其軸向的一端側與輪架48連結。藉由交叉滾子軸承14 Q ’相對於外殼50旋轉支承有輪架48 (以下,利用第5圖 進行詳述)。 根據上述的結構,各行星齒輪40之擺動成分可以藉 由各行星齒輪4〇之內滾子孔45與內滾子46之鬆動嵌合 被吸收’並且可以從輪架48排出相當於固定內齒輪44時 的行星齒輪40之自轉成分之旋轉。而且,將限制行星齒 輪40之自轉時的內齒輪44之旋轉作爲輸出而排出也可以 -12- 201031831 其次,將裝入第1圖中所示的角接觸滾子軸承16、18 的減速機G2顯示於第4圖。 與曲軸24 1連結的行星齒輪240之邊端具備有第1、 第 2 輪架 248 ( 248A、248B )。 該曲軸241藉由一對軸承255、256,相對於輪架248 旋轉自如地被支承。而且,該輪架248藉由一對角接觸滾 子軸承16、18,相對於外殼250旋轉自如地被支承(以下 φ ,利用第6圖進行詳述)。 對於其他的結構,基本上與使用上述交叉滾子軸承I4 的減速機G1之構造(第3圖)相同,故留下於與第3圖 對應的部分(功能上相同的部分)附加後2位數相同的標 圖號,省略重複說明。 在此,利用放大圖(第5圖、第6圖),對裝入於上 述減速機G1、G2的交叉滾子軸承14、角接觸滾子軸承 1 6、1 8進一步詳細地進行說明。 # 於第5圖表示以第3圖的V圍繞的部分的放大圖,於 第6圖表示以第4圖的VI圍繞的部分的放大圖。 另外,於第5圖、第6圖中,以相同之圖號表示與第 1圖(A) 、(B)所示的交叉滾子軸承14、角接觸滾子軸 承16、18之零件對應的相同的零件。 第5圖所示的支承輪架(被支承體)48的交叉滾子軸 承14在第1內圈23、第2內圈24與第1外圈21、第2 外圈22之間具有滾子25。 第1內圈23、第2內圈24與第1外圈21、第2外圈 -13- 201031831 22雙方,由通過以該內圈/外圈之滾動面21 A〜24A圍繞 的空間26之中心,並沿著與輪架(被支承體)48之軸向 X垂直的面P分別分割的第1、第2內圈及外圈21〜24構 成。 該第1、第2內圈及外圈21〜24以由滾動面21A〜 24八圍繞的空間26之中心爲中心爲點對稱的剖面形狀。 第6圖所示的角接觸滾子軸承16之內圈及外圈在上 述的交叉滾子軸承14之第1、第2內圈及外圈21〜24中 _ ,由在於輪架(被支承體)248A、248B之軸向剖面,滾 動面21a、24a所相對的第1外圈21與第2內圈24彼此 而構成。 角接觸滾子軸承18之內圈及外圈也同樣地,在交叉 滾子軸承14之第1、第2內圈及外圈21〜24中,由與滾 動面22a、23a相對的第1內圈23與第2外圈22彼此而 構成。.201031831 VI. Description of the Invention: [Technical Field] The present invention relates to a cross roller bearing, an angular contact roller bearing, and a method of manufacturing a crossed roller bearing and an angular contact roller bearing. [Prior Art] In Fig. 1 of Patent Document 1, a reduction gear incorporating a crossed roller bearing φ is disclosed. Further, in Fig. 4 of the same patent document, a reduction gear incorporating an angular contact roller bearing is disclosed. [Patent Document 1] Japanese Laid-Open Patent Publication No. 2003-74646 (Fig. 1 and Fig. 4) [Explanation] [Problems to be solved by the invention] φ Since the above-described crossed roller bearing and angular contact roller bearing are functionally The bearings are different in construction, and the shapes of the inner and outer turns are also different, so they are individually designed or manufactured. Therefore, the production cost becomes high. The object of the present invention is to reduce the number of parts for manufacturing a crossed roller bearing and an angular contact roller bearing, and to provide a cross roller bearing and an angular contact roller bearing at low cost. [Means for Solving the Problem] The present invention solves the above problems by the following technique: a cross roller bearing having a rolling element between the inner ring and the outer ring -5 - 201031831, using: both the inner and outer rings are A bearing formed by the first and second inner rings and the outer ring which are respectively divided by the center of the space surrounded by the rolling surfaces of the inner ring and the outer ring and along the surface perpendicular to the axial direction of the supported body. In the case of the crossed roller bearing, the inner ring and the outer ring are each divided by the center of the space surrounded by the rolling faces of the inner ring and the outer ring, and are respectively divided along the plane perpendicular to the axial direction of the supported body. The second inner ring and the outer ring are formed. As a result, the angular contact roller bearing can be manufactured by using the inner ring and the outer ring and the rotating body opposed to the crossed roller bearing, so that the manufacturing cost of the bearing can be reduced. Further, when the crossed roller bearing needs to be shortened in size, the inner ring/outer ring and the rolling element can be used as the crossed roller bearing, and it is necessary to improve the rigidity or capacity of the supported body by The above parts are used as angular contact roller bearings. That is, according to the present invention, the inner and outer rings of the crossed roller bearing and the rolling elements are transferred to the angular contact roller bearing, and the rigidity of the supported body is matched with the part structure having less commonality. The above two bearings can be used separately at low cost, etc. [Effect of the Invention] According to the present invention, it is possible to reduce the number of parts in manufacturing a crossed roller bearing and an angular contact roller bearing, and to provide a cross roller bearing and an angular contact roller bearing at low cost. [Embodiment] -6- 201031831. Hereinafter, an embodiment of the present invention will be described based on Fig. 1 . First, the cross roller bearing 14 of one embodiment of the present invention will be described. Fig. 1(a) is a longitudinal sectional view showing the crossed roller bearing 14. The crossed roller bearing 14 has an outer ring 140r, an inner ring 14 Ir, and a roller (rolling body) 25 disposed between the outer ring l4〇r and the inner ring Mir. At the center in the axial direction of the inner circumference of the outer ring 140r, rolling surfaces 21A and 22A which are orthogonal to each other inside the outer ring 140r itself are formed. In the axial center of the outer circumference of the inner circumference φ 14Ir, rolling surfaces 23 A and 24 A which are orthogonal to each other inside the inner circumference Mil itself are formed. The outer ring 140r passes through the center 26A of the space 26 surrounded by the outer ring 140r and the rolling faces 21A to 24A of the inner bore 14Ir, and is supported along the inner peripheral side inserted into the inner peripheral side of the crossed roller bearing 14 (omitted The plane X perpendicular to the plane P is shown divided into two outer rings, that is, the first outer ring 21 and the second outer ring 22. The first outer ring 21 and the second outer ring 22 have a cross section (the cross section shown in Fig. 1) parallel to the axial direction X, and have a surface in which one vertex of the square φ shape is cut at 45 degrees. The shape of the rolling surfaces 21A, 22A. The inner ring 14Ir is divided into a center 26A of the space 26 surrounded by the outer ring 140r and the rolling surfaces 21A to 24A of the inner ring 14Ir, and is divided into 2 along a plane P perpendicular to the axial direction X of the supported body (not shown). The inner ring, that is, the first inner ring 23 and the second inner ring 24. The first inner ring 23 and the second inner ring 24 also have a cross section (a cross section shown in FIG. 1) parallel to the axial direction X thereof: a surface in which one vertex of the square is cut at 45 degrees is set as the above-described rolling The shape of the faces 23A, 24A. 201031831 In other words, the cross section 'parallel to the respective axial directions X of the first outer ring 21, the second outer ring 22, the first inner ring 23, and the second inner ring 24 is the space 26 surrounded by the rolling surfaces 21A to 24A. The center 26A has a shape in which the center is point-symmetric. The roller (rolling element) 25' is composed of a cylindrical shape having the same diameter and height (the axial length of the rolling element 25) (strictly speaking, the diameter is only slightly smaller than the height), and is mounted every other 90 degrees. In. Next, a case where the crossed roller bearing 14 is used as a pair of angular contact roller bearings 16 and 18 can be effectively utilized by the first figure (b)'. Further, in Fig. 1(b), the same reference numerals are attached to the parts (the same parts) corresponding to the parts of the cross roller bearing 14 of Fig. 1(a). One of the angular contact roller bearings 16 is opposed to the first and second inner rings and the outer turns 21 to 24 of the crossed roller bearing 14 of Fig. 1(a) by the rolling surfaces 21A and 24A. The outer ring 21, the second inner ring 24, and the roller 25 are formed. The rollers of the roller 25 which are identical to the ❹ roller 25 constituting the crossed roller bearing 14 are all loaded in the same direction (direction which is at right angles to the slanting axis Z1). The other angular contact roller bearing 18 is opposed to the first and second inner rings and the outer rings 21 to 24 of the crossed roller bearing 14 of Fig. 1(a) by the rolling surfaces 22 A and 23A. The second outer ring 22, the first inner ring 23, and the roller 25 are formed. The rollers of the roller 25 which are the same as the rollers 25 constituting the crossed roller bearing 14 are all loaded in the same direction (the direction in which the oblique axial direction z2 is a right angle). -8- 201031831 , by using the above-mentioned cross roller bearing 14 and the parts of the pair of angular contact roller bearings 16, 18, the number of parts of the two bearings 14, (16, 18) can be reduced, and the cost is low. A cross roller bearing 14 and an angular contact roller bearing 丨 6, 18 are provided. Moreover, a method of manufacturing the crossed roller bearing 14 and the angular contact roller bearing 16' 18 can be determined, characterized in that the space 26 is surrounded by the rolling faces 21A to 24A of the inner rings 23, 24 and the outer rings 21, 22. The center 26A and the first and second inner rings and the outer rings 21 to 24, which are respectively divided by the surface P perpendicular to the axial direction of the supported body, and the rolling elements 25, and the cross roller bearing 14 are manufactured, and In the first and second inner rings and the outer rings 21 to 24, the angular contact roller bearing 1 is manufactured by the pair of inner rings 24, 23, the outer rings 21, 22, and the rolling elements 25 opposed to the rolling surfaces 21A to 24A. 6, 18. In addition, in FIG. 1, the cross-sectional shapes of the inner ring and the outer turns 21 to 24 of the crossed roller bearing 14 and the angular contact roller bearings 16 and 18 are point symmetrical, but the inner ring of the crossed roller bearing 14 and The profile of the outer ring 21 to 24 may not be point symmetrical. Hereinafter, a combination of the shapes of the first and second inner rings and the outer rings 21 to 24 constituting the crossed roller bearing 14 will be described. Fig. 2 is a schematic cross-sectional view showing a combination of the first and second inner rings of the crossed roller bearing 14 and the outer rings 21 to 24. Embodiments (a) to (g) shown in Fig. 2 will be described. In the embodiment (a), the length 12 of the cross-sectional shape of the first and second inner rings and the outer rings 21a to 24a in the radial direction is longer than the length 11 of the axial direction. Further, it is characterized in that the outer corners of the first outer ring 21a and the second outer -9 - 201031831 ring 22a have roundness (R) (rounded corners). In the embodiment (b), the axial length 13 of the cross-sectional shape of the inner ring and the outer ring 2 lb to 24b is longer than the length 14 in the radial direction. Further, it is characterized in that the outer corner portions of the first outer ring 21b and the second outer ring 22b have roundness. In the embodiment (c), as in the embodiment (b), the axial length 13 of the second inner and outer rings 22c and 24c is longer than the length Μ in the radial direction. Further, it is characterized in that the outer corner portions of the first outer ring 21c and the second φ outer ring 22c have roundness. However, since the length 15 of the axial direction of the first inner ring and the outer rings 21c and 23c is longer than the length 13 of the axial directions of the second inner ring and the outer rings 22c and 24c, it is different from the embodiment (b). In the embodiment (d), the axial length of the crossed roller bearing 14 is (the length 17 of the axial direction of the first outer ring 21d) < (the axial length of the second inner ring and the outer rings 22d, 24d) 16) The relationship of < (the length 15 of the axial direction of the first inner ring 23d). Further, it is characterized in that the outer corners of the first outer ring 21d and the second outer ring 22d have roundness. In the embodiment (e), the axial length of the crossed roller bearing 14 is (the length 17 of the axial direction of the first inner ring 23e) < (the axial direction of the second inner and outer rings 22e, 24e) Length 16) < (the length of the axial direction 15 of the first outer ring 21e). Further, it is characterized in that the outer corners of the first outer ring 21e and the second outer ring 22e have roundness. In the embodiment (f), the length 18 of the first inner ring 23f in the radial direction is longer than the length 17 of the axial direction. The lengths 17 of the other inner and outer rings 21f, 22f, 24f in the radial direction are the same as the length 17 of the axial direction. Further, -10-201031831 is characterized in that the outer corners of the first outer ring 21f and the second outer ring 22f are rounded. In the embodiment (g), the length 18 of the first outer ring 21g in the radial direction is longer than the length 17 of the axial direction. The length 17 of the second outer ring 22g, the first inner ring 23g, and the second inner ring 24g in the radial direction is the same as the length 17 in the axial direction. Further, it is characterized in that the outer corner portions of the first outer ring 21g and the second outer ring 22g are rounded. φ Thus, the first and second inner and outer rings 21a to 24a, the first and second inner rings, and the outer rings 21b to 2bb of the crossed roller bearings 14a to 14g are first and second. The size and shape of the inner ring and the outer ring 21g to 2 4g are incorporated in the reducer or the like by the crossed roller bearings 14a to 14g (or the angular contact roller bearing formed using the components of the crossed roller bearing) The relationship between the surrounding members can be changed as appropriate. However, in order to convert the crossed roller bearings 14a to 14g as a pair of angular contact roller bearings (not shown), the first and second inner and outer rings 21a to 24a, 21b to 24b, ... 9 and 21g to 24g are necessarily divided by the centers 26Aa to 26Ag of the spaces 26a to 26g surrounded by the rolling faces of the inner and outer rings, and are divided along the faces Pa to Pg perpendicular to the axial direction X of the supported body. . Therefore, although not shown, each of the crossed roller bearings 14a to 14g can be used as an angular contact roller bearing including the first outer rings 21a to 21g and the second inner rings 24a to 24g with respect to the rolling surface. Further, the angular contact roller bearings including the second outer rings 22a to 22g and the first inner rings 23a to 23g which are opposed to each other in the rolling surface can be transferred to the same crossed roller bearings 14a to 14g. -11 - 201031831 Next, an embodiment in which the crossed roller bearing 14 or the angular contact roller bearings 16 and 18 shown in Fig. 1 are incorporated in the speed reducers G1 and G2 will be described. Fig. 3 is a longitudinal sectional view showing the reduction gear G1 incorporated in the crossed roller bearing 14. Three eccentric bodies 42 (42A, 42B, 42C) having a phase difference of 120° are integrally formed on the crankshaft (input shaft) 41 of the reduction gear G1. The crankshaft 41 is rotatably supported by the carrier 48 and the casing 50 via a pair of bearings 55 and 56. In each of the eccentric bodies 42, three planetary gears 40 (40A, 40B, 40C) are mounted via the rollers 43 (43 A, 43 B, 43 C ). The planetary gears 40 are internally in meshed with the internal gear 44. Further, the internal gear 44 is integrally attached to the inner peripheral side of the outer casing 50. A plurality of inner roller holes 45 (45A, 45B, 45C) are formed in the planetary gear 40 in the axial direction, and the inner roller 46 and the inner pin 47 are inserted. The inner pin 47 is coupled to the carrier 48 at one end side in the axial direction. The carrier 48 is rotatably supported by the crossed roller bearing 14 Q ' with respect to the outer casing 50 (hereinafter, it will be described in detail with reference to Fig. 5). According to the above configuration, the swing component of each of the planetary gears 40 can be absorbed by the loose fitting of the inner roller hole 45 and the inner roller 46 of each of the planetary gears 4, and can be discharged from the carrier 48 as a fixed internal gear. The rotation of the rotation component of the planetary gear 40 at 440 hours. Further, it is also possible to discharge the rotation of the internal gear 44 when the rotation of the planetary gear 40 is restricted as an output. -12- 201031831 Next, the reduction gear G2 of the angular contact roller bearing 16, 18 shown in Fig. 1 is incorporated. Shown in Figure 4. The first end of the planetary gear 240 coupled to the crankshaft 24 1 is provided with first and second wheel carriers 248 (248A, 248B). The crankshaft 241 is rotatably supported relative to the wheel carrier 248 by a pair of bearings 255 and 256. Further, the wheel carrier 248 is rotatably supported by the outer casing 250 by a pair of angular contact roller bearings 16, 18 (hereinafter, φ, which will be described in detail with reference to Fig. 6). The other structure is basically the same as the structure (Fig. 3) of the speed reducer G1 using the above-described crossed roller bearing I4, so that the portion (functionally identical portion) corresponding to the third figure is attached to the second position. The same number of the same drawing number is omitted, and the repeated description is omitted. Here, the cross-roller bearing 14 and the angular contact roller bearing 16 and 18 incorporated in the above-described reduction gears G1 and G2 will be described in further detail using an enlarged view (Fig. 5 and Fig. 6). # Fig. 5 is an enlarged view of a portion surrounded by V in Fig. 3, and Fig. 6 is an enlarged view showing a portion surrounded by VI of Fig. 4. In addition, in the fifth drawing and the sixth drawing, the parts corresponding to the crossed roller bearing 14 and the angular contact roller bearing 16 and 18 shown in Figs. 1(A) and (B) are shown by the same reference numerals. The same parts. The crossed roller bearing 14 of the support carrier (supported body) 48 shown in Fig. 5 has a roller between the first inner ring 23, the second inner ring 24, the first outer ring 21, and the second outer ring 22. 25. Both the first inner ring 23, the second inner ring 24, the first outer ring 21, and the second outer ring-13-201031831 22 pass through the space 26 surrounded by the rolling surfaces 21 A to 24A of the inner ring/outer ring. The center is formed by the first and second inner rings and the outer rings 21 to 24 which are respectively divided along the surface P perpendicular to the axial direction X of the wheel carrier (supported body) 48. The first and second inner rings and the outer rings 21 to 24 have a point-symmetric cross-sectional shape centering on the center of the space 26 surrounded by the rolling surfaces 21A to 248. The inner ring and the outer ring of the angular contact roller bearing 16 shown in Fig. 6 are in the first and second inner rings and the outer rings 21 to 24 of the above-mentioned crossed roller bearing 14, and are supported by the wheel carrier. The axial cross-sections of the bodies 248A and 248B are formed by the first outer ring 21 and the second inner ring 24 facing each other by the rolling surfaces 21a and 24a. Similarly, in the inner ring and the outer ring of the angular contact roller bearing 18, in the first and second inner rings and the outer rings 21 to 24 of the crossed roller bearing 14, the first inner surface facing the rolling surfaces 22a and 23a The ring 23 and the second outer ring 22 are configured to each other. .

與使用交叉滾子軸承14的滾子25相同形狀之滾子25 Q ,是介於各內圈及外圈21〜24之滾動面21A〜24A之間 〇 根據以上情況’可以將交叉滾子軸承14之內圈及外 圈21〜24及滾子25轉用到角接觸滚子軸承16、18。 也就是說’可以減少製造交叉滚子軸承14及角接觸 滾子軸承16、18時的零件數量,而低成本提供交叉滾子 軸承14及角接觸滾子軸承16、18。而且,也可以確定兼 用兩軸承14、(16、18)之零件之製造方法。 -14- 201031831 藉此,當需要縮短減速機G1之尺寸時,可以作爲交 叉滾子軸承14而使用。而且,於需要提高減速機G2之剛 性或容量時,可以作爲一對角接觸滾子軸承16、18而組 合使用。 【圖式簡單說明】 第1圖是本發明所涉及的交叉滾子軸承之縱剖面圖。 φ 第2圖是表示本發明所涉及的交叉滾子軸承之內圈及 外圈之插入 的簡要剖面圖。 第3圖是插入有本發明之交叉滾子軸承的減速機之縱 剖面圖。 第4圖是將本發明之交叉滾子軸承作爲角接觸滾子軸 承而插入的減速機之縱剖面圖。 第5圖是第4圖所示之減速機G1之A部放大圖。 Φ 第6圖是第5圖所示之減速機G2之B部放大圖。 【主要元件符號說明】 14 :交叉滾子軸承 140r:外圈 14Ir :內圈 16、18:角接觸滾子軸承 21、22:第1外圈、第2外圈 23、24:第1內圈、第2內圈 -15- 201031831 21A〜24A:滾動面 25 :滾子(滾動體) 26 :空間 26A :空間之中心 X :軸向 P:與軸向垂直的面The roller 25 Q having the same shape as the roller 25 using the cross roller bearing 14 is interposed between the rolling surfaces 21A to 24A of the inner and outer rings 21 to 24, and the cross roller bearing can be used according to the above situation. The inner and outer rings 21 to 24 and the rollers 25 of 14 are transferred to the angular contact roller bearings 16, 18. That is to say, the number of parts when manufacturing the crossed roller bearing 14 and the angular contact roller bearing 16, 18 can be reduced, and the cross roller bearing 14 and the angular contact roller bearing 16, 18 are provided at low cost. Further, it is also possible to determine the manufacturing method of the parts that use the two bearings 14 and (16, 18). -14- 201031831 Thereby, when it is necessary to shorten the size of the speed reducer G1, it can be used as the cross roller bearing 14. Further, when it is necessary to increase the rigidity or capacity of the reduction gear G2, it can be used in combination as a pair of angular contact roller bearings 16, 18. BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a longitudinal sectional view of a crossed roller bearing according to the present invention. φ Fig. 2 is a schematic cross-sectional view showing the insertion of the inner ring and the outer ring of the crossed roller bearing according to the present invention. Fig. 3 is a longitudinal sectional view of a reduction gear incorporating the crossed roller bearing of the present invention. Fig. 4 is a longitudinal sectional view showing a reduction gear in which the crossed roller bearing of the present invention is inserted as an angular contact roller bearing. Fig. 5 is an enlarged view of a portion A of the speed reducer G1 shown in Fig. 4. Φ Fig. 6 is an enlarged view of a portion B of the speed reducer G2 shown in Fig. 5. [Description of main component symbols] 14: Crossed roller bearing 140r: Outer ring 14Ir: Inner ring 16, 18: Angular contact roller bearing 21, 22: First outer ring, second outer ring 23, 24: First inner ring 2nd inner ring -15- 201031831 21A~24A: rolling surface 25: roller (rolling body) 26: space 26A: center of space X: axial direction P: plane perpendicular to the axial direction

-16--16-

Claims (1)

201031831 七、申請專利範圍: 1· 一種交叉滾子軸承,在內圈與外圈之間具有滾動 體,其特徵爲: 上述內圈與外圈雙方,是分別由沿著通過以該內圈與 外圈之滾動面圍繞的空間之中心且與被支承體之軸向垂直 的面而分割的第1、第2內圈及外圈所構成。 2. 如申請專利範圍第1項的交叉滾子軸承,其中, φ 上述第丨、第2內圈及外圈,具有以由上述滾動面圍 繞的空間之中心爲中心呈點對稱的剖面形狀。 3. —種角接觸滾子軸承,其特徵爲: 藉由申請專利範圍第1項的交叉滾子軸承之上述第1 、第2內圈及外圈當中上述滾動面相對向的一對內圈與外 圈而構成內圈與外圈,並且,具備與上述滾動體相同的形 狀的滾動體。 4. 一種交叉滾子軸承與角接觸滾子軸承之製造方法 • ,其特徵爲: 藉由第1、第2內圈及外圈與滾動体而製造交叉滾子 軸承,該第1、第2內圈及外圈是分別沿著通過以內圈與 外圈之滾動面圍繞的空間之中心且與被支承體之軸向垂直 的面而被分割;藉由上述第1、第2內圈及外圈當中上述 滾動面相對向的一對內圈、外圈以及上述滾動體,而製造 角接觸滾子軸承。 -17-201031831 VII. Patent application scope: 1. A cross roller bearing having a rolling body between the inner ring and the outer ring, characterized in that: the inner ring and the outer ring are respectively passed along the inner ring and The first and second inner rings and the outer ring which are divided by the center of the space surrounded by the rolling surface of the outer ring and which are perpendicular to the axial direction of the support body. 2. The cross-roller bearing according to claim 1, wherein the φ, the second inner ring, and the outer ring have a cross-sectional shape that is point-symmetric about a center of a space surrounded by the rolling surface. 3. An angular contact roller bearing, characterized in that: a pair of inner rings of the first and second inner rings and the outer ring of the crossed roller bearing of claim 1 of the first aspect of the invention, wherein the rolling surfaces face each other The inner ring and the outer ring are formed separately from the outer ring, and a rolling element having the same shape as the rolling element is provided. A method of manufacturing a crossed roller bearing and an angular contact roller bearing, characterized in that a cross roller bearing is manufactured by a first and a second inner ring and an outer ring and a rolling element, the first and second The inner ring and the outer ring are respectively divided along a surface perpendicular to the axial direction of the supported body through the center of the space surrounded by the rolling surfaces of the inner ring and the outer ring; by the first and second inner rings and the outer An angular contact roller bearing is manufactured by a pair of inner rings, outer rings, and the above-described rolling elements in which the rolling surfaces are opposed to each other. -17-
TW99104745A 2009-02-20 2010-02-12 Angular roller bearing, and method of manufacturing cross roller bearing and angular roller TWI390123B (en)

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