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JP2009275792A - Friction bearing - Google Patents

Friction bearing Download PDF

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Publication number
JP2009275792A
JP2009275792A JP2008126839A JP2008126839A JP2009275792A JP 2009275792 A JP2009275792 A JP 2009275792A JP 2008126839 A JP2008126839 A JP 2008126839A JP 2008126839 A JP2008126839 A JP 2008126839A JP 2009275792 A JP2009275792 A JP 2009275792A
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Japan
Prior art keywords
raceway
inner ring
ring
fitting portion
ball
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Pending
Application number
JP2008126839A
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Japanese (ja)
Inventor
Hiroshi Morishita
比呂志 森下
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NTN Corp
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NTN Corp
NTN Toyo Bearing Co Ltd
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Application filed by NTN Corp, NTN Toyo Bearing Co Ltd filed Critical NTN Corp
Priority to JP2008126839A priority Critical patent/JP2009275792A/en
Publication of JP2009275792A publication Critical patent/JP2009275792A/en
Pending legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/60—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
    • F16C25/06—Ball or roller bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
    • F16C19/163—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls with angular contact
    • F16C19/166—Four-point-contact ball bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
    • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
    • F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
    • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
    • F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
    • F16C19/184—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2226/00—Joining parts; Fastening; Assembling or mounting parts
    • F16C2226/50—Positive connections
    • F16C2226/60—Positive connections with threaded parts, e.g. bolt and nut connections

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Support Of The Bearing (AREA)
  • Mounting Of Bearings Or Others (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To improve assemblability and handleability of a friction bearing in the case of having one of race rings structuring inner and outer rings is a divided race ring, for example, a four-point contact ball bearing. <P>SOLUTION: The inner ring 11 structuring the divided race ring is composed by combined surfaces of inner ring members 11a, 11b. Faucet fitting parts of the inner ring members 11a, 11b are provided with male and female screw parts 22a, 22b respectively. An adjustment shim 23 is intervened between axial butt surfaces of these inner ring members 11a, 11b and the inner ring members 11a, 11b are integrated by mutual screw connection by fastening the screw parts 22a, 22b. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

この発明は、４点接触玉軸受に見られるような内外輪を構成する軌道輪のうち、いずれか一方の軌道輪が分割軌道輪によって構成された転がり軸受に関するものである。   The present invention relates to a rolling bearing in which any one of the race rings constituting the inner and outer rings as seen in a four-point contact ball bearing is constituted by a split race ring.

内外輪を構成するいずれか一方の軌道輪が軸方向に二分割された分割軌道輪を用いた転がり軸受として、従来から４点接触又は３点接触のアンギュラ玉軸受が知られている（特許文献１、特許文献２）。また、分割軌道輪を用いた複列アンギュラ玉軸受も知られている（特許文献３）。   Conventionally, a four-point contact or three-point contact angular ball bearing is known as a rolling bearing using a split race ring in which any one of the race rings constituting the inner and outer rings is divided into two in the axial direction (Patent Literature). 1, Patent Document 2). A double-row angular contact ball bearing using a split raceway is also known (Patent Document 3).

前記の分割軌道輪を有する転がり軸受は、所要のアンギュラーコンタクトを得るためのゴシックアーチ形の軌道溝を加工する場合に便利である。即ち、分割軌道輪を構成する一対の軌道輪部材の相互間に適宜厚さのシムを介在させ、通常の砥石によって円弧面をもった軌道を研削加工したのち、前記シムを外して軌道輪部材相互を軸方向に突き合わせると所要のゴシックアーチ形の軌道が得られる。シムの厚さを変えることにより、ゴシックアーチの形状を変えることができる。   The rolling bearing having the above-described divided raceway is convenient when machining a gothic arch-shaped raceway groove for obtaining a required angular contact. That is, a shim having an appropriate thickness is interposed between a pair of raceway members constituting the split raceway, and after grinding the raceway having an arc surface with a normal grindstone, the shim is removed and the raceway ring member The desired Gothic arched trajectory is obtained when they are abutted against each other in the axial direction. The shape of the Gothic arch can be changed by changing the thickness of the shim.

また、前記のように加工された一対の軌道輪部材相互間の突き合わせ面に研削加工を施すことにより、軸受すきまや予圧の大きさを調整することができる。   In addition, the bearing clearance and the preload can be adjusted by grinding the abutting surfaces between the pair of bearing ring members processed as described above.

特開平１１−６２９９０号公報（図１）Japanese Patent Laid-Open No. 11-62990 (FIG. 1) 特開２００３−１３９１４５号公報（図２）Japanese Patent Laying-Open No. 2003-139145 (FIG. 2) 特開２００６−１０５３８４号公報（図１）JP 2006-105384 A (FIG. 1)

分割軌道輪を有する転がり軸受として、従来構造をもった４点接触玉軸受を図６に示す。図示の場合、内輪１が分割軌道輪であり外輪２が通常の一体の軌道輪によって構成され、その内外輪１、２の軌道溝３、４間に、保持器５によって一定間隔に保持された複数個の玉６が介在される。各軌道溝３、４の形状はゴシックアーチ形であり、玉６は４点で接触している。内輪１は軸方向に分割された一対の内輪部材１ａ、１ｂの組み合わせによって構成され、両者が軸方向の突き合せ面７において突き合わされる。   As a rolling bearing having a split ring, a four-point contact ball bearing having a conventional structure is shown in FIG. In the case of illustration, the inner ring 1 is a divided raceway ring and the outer ring 2 is constituted by a normal integral raceway, and is held at regular intervals between the raceway grooves 3 and 4 of the inner and outer races 1 and 2 by a cage 5. A plurality of balls 6 are interposed. Each track groove 3, 4 has a Gothic arch shape, and the ball 6 is in contact at four points. The inner ring 1 is constituted by a combination of a pair of inner ring members 1a and 1b divided in the axial direction, and both are abutted on an abutting surface 7 in the axial direction.

前記の玉軸受を横置きの軸に組み付ける場合、軸の周りに嵌めた外輪２の内径面に保持器５と玉６の組立体及び一方の内輪部材１ａを組み合わせ、その後、他方の内輪部材１ｂを組み付ける方法がとられる。   When the ball bearing is assembled to a horizontal shaft, the inner ring surface of the outer ring 2 fitted around the shaft is combined with the assembly of the cage 5 and the ball 6 and one inner ring member 1a, and then the other inner ring member 1b. The method of assembling is taken.

先に組み付けた保持器５と玉６は不安定な状態にあるため、他方の内輪部材１ｂを後から組み付ける際に、保持器５から外れた玉６が外輪２の軌道溝４の肩エッジ８と、前記他方の内輪部材１ｂの合わせ面エッジ９によって挟まれた状態になることがある。その状態で内輪部材１ｂが強く押し込まれると、玉６に対し両方のエッジ８、９による圧痕が生じることがある。   Since the cage 5 and the ball 6 assembled earlier are in an unstable state, when the other inner ring member 1b is assembled later, the ball 6 detached from the cage 5 is the shoulder edge 8 of the raceway groove 4 of the outer ring 2. And may be sandwiched by the mating surface edge 9 of the other inner ring member 1b. If the inner ring member 1b is strongly pushed in this state, the ball 6 may be indented by both edges 8 and 9.

また、前記の分割軌道輪は、搬送時や取り扱い時において内輪部材１ａ、１ｂが外れ易い不具合もあった。   In addition, the above-described split races have a problem that the inner ring members 1a and 1b are easily detached during transport and handling.

以上は４点接触玉軸受について説明したが、３点接触玉軸受、複列玉軸受等分割軌道輪を用いた転がり軸受一般に言えることである。   Although the above has described the four-point contact ball bearing, it can be generally applied to rolling bearings using split races such as a three-point contact ball bearing and a double row ball bearing.

そこで、この発明は、分割軌道輪を用いた転がり軸受における前記の問題を解消し、組立性、取り扱い性が良好な転がり軸受を提供することを課題とする。   Accordingly, an object of the present invention is to solve the above-mentioned problems in a rolling bearing using a split race and provide a rolling bearing with good assembling and handling properties.

前記の課題を解決するために、この発明においては、軌道輪を構成する内輪と外輪、前記内輪と外輪の間に介在された複数個の転動体、これらの転動体を保持する保持器からなり、前記内輪又は外輪のいずれか一方が軸方向に分割された一対の軌道輪部材を組み合わせた分割軌道輪からなる転がり軸受において、
前記分割軌道輪を構成する一対の軌道輪部材の組み合わせ面にそれぞれ雌雄のネジ部が設けられ、これらのネジ部の締結により前記軌道輪部材が相互に結合一体化された構成を採用した。 In order to solve the above-mentioned problems, the present invention comprises an inner ring and an outer ring constituting a raceway ring, a plurality of rolling elements interposed between the inner ring and the outer ring, and a cage for holding these rolling elements. In the rolling bearing consisting of a split raceway ring that combines a pair of raceway members in which either the inner ring or the outer ring is split in the axial direction,
A male and female threaded portion is provided on each of the combination surfaces of the pair of raceway members constituting the split raceway, and the raceway members are coupled and integrated with each other by fastening these threaded portions.

この発明は以上の構成であり、分割軌道輪を構成する一対の軌道輪部材が相互にネジ結合により一体化されているので、内外輪ともに一体の通常の軸受と同様の手法により組立てることができる。これにより、組立時に玉が外れることがなく、従って玉に圧痕を生じさせることもなく、組立性に優れる効果がある。また搬送時、取り扱い時等において軌道輪部材が分離することもないので、取り扱い性に優れる効果がある。
また、一対の軌道輪部材の軸方向の対向面間に調整用シムを介在した構成を採用すると、調整用シムの厚さに応じた軸受すきま又は予圧の設定を行うことができる。 The present invention has the above-described configuration, and since the pair of race ring members constituting the split race ring are integrated with each other by screw coupling, both the inner and outer races can be assembled by the same technique as that of an ordinary bearing integrated. . Thereby, the ball does not come off at the time of assembling, and therefore, there is no indentation on the ball, and there is an effect that the assembling property is excellent. Further, since the bearing ring member is not separated during transportation, handling, etc., there is an effect of excellent handling.
Further, when a configuration in which an adjustment shim is interposed between the axial facing surfaces of the pair of bearing ring members is adopted, it is possible to set a bearing clearance or a preload according to the thickness of the adjustment shim.

以下、この発明に係る転がり軸受の実施例を添付図面に基づいて説明する。   Embodiments of the rolling bearing according to the present invention will be described below with reference to the accompanying drawings.

図１及び図２に示した実施例１の転がり軸受は、内外に対向した軌道輪を構成する内輪１１と外輪１２、内輪１１の軌道溝１３と外輪１２の軌道溝１４の間に介在された複数個の玉１５、これらの玉１５を保持する保持器１６によって構成される。前記の各軌道溝１３、１４の断面形状は、図示のように、ゴシックアーチ形をなし、玉１５は２個所ずつ全部で４箇所に接点を有する４点接触玉軸受である。これらの軌道溝１３、１４の底面にグリース溜り１７、１８が形成される。   The rolling bearing of the first embodiment shown in FIGS. 1 and 2 is interposed between an inner ring 11 and an outer ring 12 constituting raceways facing the inside and outside, and between a raceway groove 13 of the inner ring 11 and a raceway groove 14 of the outer ring 12. A plurality of balls 15 and a cage 16 that holds these balls 15 are configured. As shown in the drawing, the cross-sectional shape of each of the raceway grooves 13 and 14 is a Gothic arch shape, and the ball 15 is a four-point contact ball bearing having contacts at four locations in total at two locations. Grease reservoirs 17 and 18 are formed on the bottom surfaces of these raceway grooves 13 and 14.

前記内輪１１は、軸方向に分割された一対の内輪部材（特許請求の範囲においては「軌道輪部材」と称している。）１１ａ、１１ｂの組み合わせによって形成された分割軌道輪である。内輪部材１１ａ、１１ｂは軌道溝１３を構成する円弧面１３ａ、１３ｂを有する。これらの円弧面１３ａ、１３ｂは、玉１５より大きい曲率半径をもつように形成され、それぞれ１点において玉１５と接触する。   The inner ring 11 is a divided race ring formed by a combination of a pair of inner ring members (referred to as “track ring members” in the claims) 11a and 11b divided in the axial direction. The inner ring members 11 a and 11 b have arcuate surfaces 13 a and 13 b that constitute the raceway grooves 13. These circular arc surfaces 13a and 13b are formed so as to have a radius of curvature larger than that of the ball 15, and each contact with the ball 15 at one point.

両方の内輪部材１１ａ、１１ｂはインロー嵌合によって組み合わされる。即ち、一方の内輪部材１１ｂの突き合わせ端面において、グリース溜り１７の一方の溝側面から他方の内輪部材１１ａ側に突き出した凸形嵌合部２１ｂが、該内輪部材１１ｂの内径面の周りに環状に形成される（図２参照）。   Both inner ring members 11a and 11b are combined by inlay fitting. That is, at the abutting end surface of one inner ring member 11b, the convex fitting portion 21b protruding from one groove side surface of the grease reservoir 17 toward the other inner ring member 11a is annularly formed around the inner diameter surface of the inner ring member 11b. Formed (see FIG. 2).

他方の内輪部材１１ａの内径面の周りにおいて、前記の凸形嵌合部２１ｂに軸方向に対向した凹形嵌合部２１ａが環状に形成される。凸形嵌合部２１ｂの外径面に雄ネジ部２２ｂが形成され、凹形嵌合部２１ａの内径面に雌ネジ部２２ａが形成される。   Around the inner diameter surface of the other inner ring member 11a, a concave fitting portion 21a is formed annularly facing the convex fitting portion 21b in the axial direction. A male screw portion 22b is formed on the outer diameter surface of the convex fitting portion 21b, and a female screw portion 22a is formed on the inner diameter surface of the concave fitting portion 21a.

前記の凸形嵌合部２１ｂと凹形嵌合部２１ａは、その凹形嵌合部２１ａの軸方向の突き合わせ面に環状の調整シム２３を介在した状態で、雄ネジ部２２ｂ及び雌ネジ部２２ａをねじ結合させることにより、調整シム２３を介在した状態で相互にインロー嵌合される。そのインロー嵌合によって各内輪部材１１ａ、１１ｂの円弧面１３ａ、１３ｂがゴシックアーチ形の軌道溝１３を形成する。   The convex fitting portion 21b and the concave fitting portion 21a have a male screw portion 22b and a female screw portion in a state where an annular adjustment shim 23 is interposed between the axial fitting surfaces of the concave fitting portion 21a. By screwing 22a, inlay fitting is performed with the adjustment shim 23 interposed therebetween. The arcuate surfaces 13a and 13b of the inner ring members 11a and 11b form a gothic arch-shaped raceway groove 13 by the inlay fitting.

調整シム２３として、厚さの異なったものを所要数用意しておき、適宜選択することにより、前記ゴシックアーチ形軌道溝１３の幅を変えて玉１５と軌道溝１３、１４とのすきまを調整することができる。また、そのすき間をマイナスの範囲に調整することにより、玉１５に対し所要の予圧を加えることができる。   As the adjustment shim 23, a required number of different thicknesses are prepared, and the gap between the ball 15 and the raceway grooves 13 and 14 is adjusted by changing the width of the gothic arch raceway groove 13 by selecting as appropriate. can do. Moreover, a required preload can be applied to the ball 15 by adjusting the clearance to a negative range.

以上の構成の４点接触玉軸受の組み立てに際しては、内輪部材１１ａ、１１ｂ相互間に調整シム２３を挟み、両部材１１ａ、１１ｂをネジ結合によって一体化しておくことにより、通常の非分割型の内外輪をもった玉軸受の組み立てと同様の手法によって組み立てることができる。   When assembling the four-point contact ball bearing having the above-described configuration, an adjustment shim 23 is sandwiched between the inner ring members 11a and 11b, and both the members 11a and 11b are integrated by screw coupling. It can be assembled by the same method as the assembly of ball bearings with inner and outer rings.

このため、玉１５が抜け出すことがなく、したがって、玉１５に圧痕を生じさせるような不具合を避けることができる。また、組立完了状態において搬送する場合、取り扱う場合等において、内輪部材１１ａ、１１ｂが分離するおそれがない。   For this reason, the ball 15 does not come out, and therefore it is possible to avoid a problem that causes the ball 15 to be indented. In addition, there is no possibility that the inner ring members 11a and 11b are separated when transported in the assembled state, handled, or the like.

なお、この実施例１と同様に内輪１１を内輪部材１１ａ、１１ｂの組み合わせによって構成し、これをネジ結合によって一体化した分割軌道輪とする一方、外輪１２が玉１５と１点で接触するように軌道溝１４の曲率半径を大きく設定した円弧形に形成することにより、３点接触玉軸受を構成することができる。   As in the first embodiment, the inner ring 11 is constituted by a combination of inner ring members 11a and 11b, and this is a split raceway ring integrated by screw connection, while the outer ring 12 contacts the ball 15 at one point. In addition, a three-point contact ball bearing can be formed by forming the raceway groove 14 in an arc shape with a large curvature radius.

図３（ａ）（ｂ）に示した実施例２は、前記の実施例１の場合と同様の４点接触玉軸受であるが、この場合は、外輪１２が分割軌道輪となっている。即ち、外輪１２は、外輪部材１２ａと１２ｂの組み合わせによって構成される。一方の外輪部材１２ａの外径面に凹形嵌合部２５ａ、内径面に円弧面１４ａが形成される。また、他方の外輪部材１２ｂの外径面に凸形嵌合部２５ｂ、内径面に円弧面１４ｂがそれぞれ設けられ、凹形嵌合部２５ａと凸形嵌合部２５ｂが相互にインロー嵌合により組み合わされる。   The second embodiment shown in FIGS. 3 (a) and 3 (b) is a four-point contact ball bearing similar to the first embodiment, but in this case, the outer ring 12 is a split raceway ring. That is, the outer ring 12 is configured by a combination of outer ring members 12a and 12b. A concave fitting portion 25a is formed on the outer diameter surface of one outer ring member 12a, and an arcuate surface 14a is formed on the inner diameter surface. Further, a convex fitting portion 25b is provided on the outer diameter surface of the other outer ring member 12b, and an arcuate surface 14b is provided on the inner diameter surface thereof, and the concave fitting portion 25a and the convex fitting portion 25b are mutually fitted by inlay fitting. Combined.

また、これらの嵌合部２５ａ、２５ｂにそれぞれ雄ネジ部２６ａ、雌ネジ部２６ｂが設けられ、また、両嵌合部２５ａ、２５ｂの突き合わせ面間に所要厚さの環状の調整シム２８が介在される。前記のネジ部２６ａ、２６ｂを相互にネジ結合することにより、インロー嵌合された凹形嵌合部２５ａと凸形嵌合部２５ｂが結合され外輪部材１２ａ、１２ｂが一体化される。その一体化によりゴシックアーチ形の軌道溝１４が形成される。玉１５は４点で接触し、４点接触玉軸受となる。   The fitting portions 25a and 25b are respectively provided with a male screw portion 26a and a female screw portion 26b, and an annular adjustment shim 28 having a required thickness is interposed between the butted surfaces of the fitting portions 25a and 25b. Is done. By screwing the screw portions 26a and 26b to each other, the concave fitting portion 25a and the convex fitting portion 25b that are fitted in place are joined, and the outer ring members 12a and 12b are integrated. The integration forms a gothic arch-shaped track groove 14. The ball 15 contacts at four points and becomes a four-point contact ball bearing.

前記の調整シム２８の厚さを変えることにより、軸受すきまや予圧を調整できることは、前記実施例１の場合と同様である。   The bearing clearance and the preload can be adjusted by changing the thickness of the adjusting shim 28 as in the case of the first embodiment.

なお、この場合も、外輪１２を外輪部材１２ａ、１２ｂの組み合わせによる分割軌道輪とする一方、内輪１１が玉１５と１点で接触するように軌道溝１３の曲率半径を大きく設定した円弧形に形成することにより、３点接触玉軸受を構成することができる。   In this case as well, the outer ring 12 is a divided raceway ring formed by a combination of the outer ring members 12a and 12b, while the arcuate shape in which the curvature radius of the raceway groove 13 is set large so that the inner ring 11 contacts the ball 15 at one point. By forming the three-point contact ball bearing, a three-point contact ball bearing can be configured.

図４（ａ）（ｂ）に示した実施例３は、複列アンギュラ玉軸受の場合である。この玉軸受は、内輪１１が内輪部材１１ａ、１１ｂからなる分割軌道輪であり、各内輪部材１１ａ、１１ｂに軌道溝１９ａ、１９ｂが形成され、外輪１２にもこれらに対向した軌道溝２０ａ、２０ｂが形成される。径方向に対向した軌道溝１９ａ、２０ａと１９ｂ、２０ｂの間にそれぞれ複数の玉１５が介在され、複列型となっている。   Example 3 shown in FIGS. 4A and 4B is a case of a double-row angular contact ball bearing. This ball bearing is a split race ring in which the inner ring 11 is composed of inner ring members 11a and 11b, raceway grooves 19a and 19b are formed in the inner ring members 11a and 11b, and raceway grooves 20a and 20b facing the outer ring 12 are also provided. Is formed. A plurality of balls 15 are interposed between the raceway grooves 19a, 20a and 19b, 20b opposed to each other in the radial direction to form a double row type.

一方の内輪部材１１ｂの突き合わせ端面には、他方の内輪部材１１ａ側に突き出した凸形嵌合部２１ｂが該内輪部材１１ｂの内径面の周りに環状に形成される。これに軸方向に対向した凹形嵌合部２１ａが他方の内輪部材１１ａの内径面の周りに環状に形成される。凸形嵌合部２１ｂの外径面に雄ネジ部２２ｂ（図４（ｂ）参照）が形成され、また凹形嵌合部２１ａの内径面に雌ネジ部２２ａが形成される。   A convex fitting portion 21b protruding toward the other inner ring member 11a is formed in an annular shape around the inner diameter surface of the inner ring member 11b on the abutting end surface of one inner ring member 11b. A concave fitting portion 21a facing this in the axial direction is formed in an annular shape around the inner diameter surface of the other inner ring member 11a. A male screw portion 22b (see FIG. 4B) is formed on the outer diameter surface of the convex fitting portion 21b, and a female screw portion 22a is formed on the inner diameter surface of the concave fitting portion 21a.

前記の凸形嵌合部２１ｂと凹形嵌合部２１ａは、その凹形嵌合部２１ａの軸方向の突き合わせ面に環状の調整シム２３を介在した状態でインロー嵌合させ、雄ネジ部２２ｂ及び雌ネジ部２２ａをネジ結合させることにより、調整シム２３を介在した状態で一体化される。   The convex fitting portion 21b and the concave fitting portion 21a are fitted with an inlay with an annular adjusting shim 23 interposed between the axial fitting surfaces of the concave fitting portion 21a and the male screw portion 22b. And by integrating the female screw portion 22a with screws, it is integrated with the adjustment shim 23 interposed.

図５（ａ）（ｂ）に示した実施例４は、実施例３の場合と同様の複列アンギュラ玉軸受であるが、この場合は、外輪１２が外輪部材１２ａ、１２ｂからなる分割軌道輪の場合である。一方の外輪部材１２ｂに凸形嵌合部２５ｂ及び軌道溝２０ｂ、他方の外輪部材１２ａに凹形嵌合部２５ａと軌道溝２０ａがそれぞれ設けられ、またこれらの嵌合部２５ａ、２５ｂにそれぞれ雄ネジ部２６ａ、雌ネジ部２６ｂが設けられる。   The fourth embodiment shown in FIGS. 5A and 5B is a double row angular contact ball bearing similar to that of the third embodiment. In this case, however, the split raceway ring in which the outer ring 12 is composed of the outer ring members 12a and 12b. This is the case. One outer ring member 12b is provided with a convex fitting portion 25b and a raceway groove 20b, and the other outer ring member 12a is provided with a concave fitting portion 25a and a raceway groove 20a, respectively, and each of these fitting portions 25a and 25b is male. A screw portion 26a and a female screw portion 26b are provided.

前記凸形嵌合部２５ｂと凹形嵌合部２５ａとの突き合わせ面間に所要厚さの調整シム２８が介在される。その他の構成は、実施例３（図４参照）の場合と同様である。   An adjustment shim 28 having a required thickness is interposed between the butted surfaces of the convex fitting portion 25b and the concave fitting portion 25a. Other configurations are the same as those of the third embodiment (see FIG. 4).

実施例３、４は複列玉軸受等について説明したが、複列円錐ころ軸受等にも同様に適用することができる。   Examples 3 and 4 have been described for double row ball bearings and the like, but can be similarly applied to double row tapered roller bearings and the like.

実施例１の一部省略断面図Partially omitted sectional view of Example 1 同上の一部省略分解断面図Partially omitted exploded sectional view （ａ）実施例２の一部省略断面図、（ｂ）同上の一部省略分解断面図(A) Partially omitted sectional view of Example 2, (b) Partially omitted sectional view of the above. （ａ）実施例３の一部省略断面図、（ｂ）同上の一部省略分解断面図(A) Partially omitted sectional view of Example 3, (b) Partially omitted sectional view of the above. （ａ）実施例４の一部省略断面図、（ｂ）同上の一部省略分解断面図(A) Partially omitted sectional view of Example 4, (b) Partially omitted exploded sectional view of the above. 従来例の断面図Cross section of conventional example

符号の説明Explanation of symbols

１１ 内輪
１１ａ、１１ｂ 内輪部材
１２ 外輪
１２ａ、１２ｂ 外輪部材
１３ 軌道溝
１３ａ、１３ｂ 円弧面
１４ 軌道溝
１４ａ、１４ｂ 円弧面
１５ 玉
１６ 保持器
１７ グリース溜り
１８ グリース溜り
１９ａ、１９ｂ 軌道溝
２０ａ、２０ｂ 軌道溝
２１ａ 凹形嵌合部
２１ｂ 凸形嵌合部
２２ａ 雌ネジ部
２２ｂ 雄ネジ部
２３ 調整シム
２５ａ 凹形嵌合部
２５ｂ 凸形嵌合部
２６ａ 雄ネジ部
２６ｂ 雌ネジ部
２８ 調整シム DESCRIPTION OF SYMBOLS 11 Inner ring 11a, 11b Inner ring member 12 Outer ring 12a, 12b Outer ring member 13 Track groove 13a, 13b Arc surface 14 Track groove 14a, 14b Arc surface 15 Ball 16 Cage 17 Grease reservoir 18 Grease reservoir 19a, 19b Track groove 20a, 20b Track Groove 21a Concave fitting portion 21b Convex fitting portion 22a Female screw portion 22b Male screw portion 23 Adjustment shim 25a Concave fitting portion 25b Convex fitting portion 26a Male screw portion 26b Female screw portion 28 Adjustment shim

Claims (6)

軌道輪を構成する内輪と外輪、前記内輪と外輪の間に介在された複数個の転動体、これらの転動体を保持する保持器からなり、前記内輪又は外輪のいずれか一方が軸方向に分割された一対の軌道輪部材を組み合わせた分割軌道輪からなる転がり軸受において、
前記分割軌道輪を構成する一対の軌道輪部材の組み合わせ面にそれぞれ雌雄のネジ部が設けられ、これらのネジ部の締結により前記軌道輪部材が相互に結合一体化されたことを特徴とする転がり軸受。 An inner ring and an outer ring constituting the raceway ring, a plurality of rolling elements interposed between the inner ring and the outer ring, and a cage for holding these rolling elements, and either the inner ring or the outer ring is divided in the axial direction. In a rolling bearing consisting of a split race ring that is a combination of a pair of race ring members,
A rolling device characterized in that male and female screw portions are respectively provided on a combination surface of a pair of race ring members constituting the split race ring, and the race ring members are coupled and integrated with each other by fastening these screw portions. bearing. 前記一対の軌道輪部材の軸方向の対向面間に調整用シムを介在したことを特徴とする請求項１に記載の転がり軸受。   The rolling bearing according to claim 1, wherein an adjustment shim is interposed between axially opposed surfaces of the pair of bearing ring members. 前記調整用シムとして、軸方向の厚さの異なるものを複数枚用意し、いずれか１枚を選択的に使用するようにした請求項２に記載の転がり軸受。   The rolling bearing according to claim 2, wherein a plurality of sheets having different axial thicknesses are prepared as the adjusting shims, and any one of them is selectively used. 前記一対の軌道輪部材がそれぞれ軸方向の端面に設けられた凸形嵌合部と凹形嵌合部のインロー嵌合によって組み合わされ、これらの凸形嵌合部及び凹形嵌合部の嵌合面に前記の雄ネジ部及び雌ネジ部がそれぞれ設けられたことを特徴とする請求項１から３のいずれかに記載の転がり軸受。   The pair of bearing ring members are combined by inlay fitting of a convex fitting portion and a concave fitting portion provided on the end surface in the axial direction, respectively, and fitting of these convex fitting portion and concave fitting portion is performed. The rolling bearing according to any one of claims 1 to 3, wherein the male screw portion and the female screw portion are provided on a mating surface. 前記転動体が玉であり、前記分割軌道輪と他方の軌道輪との間に介在された前記玉が、これらの軌道輪との間で３箇所又は４箇所の接触点を有する３点接触型又は４点接触型であることを特徴とする請求項１から４のいずれかに記載の転がり軸受。   The rolling element is a ball, and the ball interposed between the divided raceway and the other raceway has three or four contact points with the raceway. Or the rolling bearing in any one of Claim 1 to 4 characterized by the above-mentioned. 前記転動体が玉であり、前記玉が前記分割軌道輪と他方の軌道輪との間に複列状態に介在された複列型であることを特徴とする請求項１から４のいずれかに記載の転がり軸受。   The rolling element is a ball, and the ball is a double-row type interposed in a double-row state between the divided raceway and the other raceway. The rolling bearing described.
JP2008126839A 2008-05-14 2008-05-14 Friction bearing Pending JP2009275792A (en)

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DE102010028421A1 (en) * 2010-04-30 2011-11-03 Von Ardenne Anlagentechnik Gmbh Ceramic roller bearing for use in end block of e.g. pipe magnetron arrangement utilized in vacuum coating system for coating substrate, has roller bodies arranged in body cage between inner and outer rings, where rings have partial rings
DE102011014079A1 (en) * 2011-03-16 2012-09-20 Wzl Aachen Gmbh Multipoint radial bearing, has rolling elements constructed such that contact region with cylindrical mold is provided in middle of rolling elements, where elements are guided on ring by line contact and on another ring over point contacts
CN104653623A (en) * 2015-02-16 2015-05-27 上海斐赛轴承科技有限公司 Full rolling body inner integral ball bearing and manufacturing method thereof
CN104675850A (en) * 2015-03-13 2015-06-03 叶雪峰 Multiple-ball bearing
DE102015217651A1 (en) * 2015-09-15 2017-03-16 Zf Friedrichshafen Ag Bearing unit comprising two angular contact ball bearings
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JP2018048692A (en) * 2016-09-21 2018-03-29 株式会社Ｔｏｋ Double-row type ball bearing
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Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010028421A1 (en) * 2010-04-30 2011-11-03 Von Ardenne Anlagentechnik Gmbh Ceramic roller bearing for use in end block of e.g. pipe magnetron arrangement utilized in vacuum coating system for coating substrate, has roller bodies arranged in body cage between inner and outer rings, where rings have partial rings
DE102010028421B4 (en) * 2010-04-30 2012-02-23 Von Ardenne Anlagentechnik Gmbh Ceramic rolling bearing and end block for a rotating magnetron
DE102011014079A1 (en) * 2011-03-16 2012-09-20 Wzl Aachen Gmbh Multipoint radial bearing, has rolling elements constructed such that contact region with cylindrical mold is provided in middle of rolling elements, where elements are guided on ring by line contact and on another ring over point contacts
CN104653623A (en) * 2015-02-16 2015-05-27 上海斐赛轴承科技有限公司 Full rolling body inner integral ball bearing and manufacturing method thereof
CN104675850A (en) * 2015-03-13 2015-06-03 叶雪峰 Multiple-ball bearing
DE102015217651A1 (en) * 2015-09-15 2017-03-16 Zf Friedrichshafen Ag Bearing unit comprising two angular contact ball bearings
WO2018055991A1 (en) * 2016-09-21 2018-03-29 株式会社Ｔｏｋ Double-row ball bearing
JP2018048692A (en) * 2016-09-21 2018-03-29 株式会社Ｔｏｋ Double-row type ball bearing
DE102016121393A1 (en) * 2016-11-09 2018-05-09 Robert Bosch Gmbh Ball bearing and method for its manufacture, fixed bearing, steering gear and steering system
CN107061503A (en) * 2017-03-22 2017-08-18 沈阳艾克申机器人技术开发有限责任公司 A kind of novel bearing of 8 points of contacts
DE102019101055A1 (en) * 2019-01-16 2020-07-16 Burkard Hefter Roller bearing slewing ring, method for producing such a roller bearing slewing ring and component arrangement with such a roller bearing slewing ring
DE102019101055B4 (en) 2019-01-16 2023-02-09 Burkard Hefter Roller bearing slewing ring, method for producing such a roller bearing slewing ring and component arrangement with such a roller bearing slewing ring
JP2020190274A (en) * 2019-05-21 2020-11-26 大阪富士工業株式会社 Ball bearing and manufacturing method thereof
WO2020235248A1 (en) * 2019-05-21 2020-11-26 大阪富士工業株式会社 Ball bearing and method for manufacturing same
US11773904B2 (en) 2019-05-21 2023-10-03 Osaka Fuji Corporation Ball bearing and method for manufacturing same
EP3742010A1 (en) * 2019-05-22 2020-11-25 General Electric Company System and method for assembling a slewing ring bearing with a predetermined preload
IT202000017509A1 (en) * 2020-07-20 2022-01-20 Skf Ab BEARING UNIT FOR MARBLE CUTTING MACHINES

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