JP7057485B2 - Separate double row angular contact ball bearings, outer ring assembly and inner ring assembly - Google Patents

Separate double row angular contact ball bearings, outer ring assembly and inner ring assembly Download PDF

Info

Publication number
JP7057485B2
JP7057485B2 JP2016238511A JP2016238511A JP7057485B2 JP 7057485 B2 JP7057485 B2 JP 7057485B2 JP 2016238511 A JP2016238511 A JP 2016238511A JP 2016238511 A JP2016238511 A JP 2016238511A JP 7057485 B2 JP7057485 B2 JP 7057485B2
Authority
JP
Japan
Prior art keywords
outer ring
inner ring
ring assembly
assembly
ball
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
JP2016238511A
Other languages
Japanese (ja)
Other versions
JP2018096395A (en
Inventor
孝一 渡辺
敏宏 河合
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Nachi Fujikoshi Corp
Original Assignee
Nachi Fujikoshi Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Nachi Fujikoshi Corp filed Critical Nachi Fujikoshi Corp
Priority to JP2016238511A priority Critical patent/JP7057485B2/en
Priority to KR1020170130375A priority patent/KR20180065873A/en
Publication of JP2018096395A publication Critical patent/JP2018096395A/en
Application granted granted Critical
Publication of JP7057485B2 publication Critical patent/JP7057485B2/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • 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
    • 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
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • F16C19/546—Systems with spaced apart rolling bearings including at least one angular contact bearing
    • F16C19/547—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling 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
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/38—Constructional details

Landscapes

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

Description

本発明は、分離型複列アンギュラ玉軸受とその外輪アッシィおよび内輪アッシィに関するものである。 The present invention relates to a separate double row angular contact ball bearing and its outer ring assembly and inner ring assembly.

アンギュラ玉軸受はラジアル荷重とアキシアル荷重とを同時に支持することができるが、特に複列のものは負荷能力が大きく剛性も高い。そのため複列アンギュラ玉軸受は、例えば自動車のデファレンシャルギヤ（最終減速機）のピニオン軸など、車両や機械等のなかでも比較的大きな荷重のかかる場所に多く使用されている。 Angular contact ball bearings can support both radial and axial loads at the same time, but double-row bearings have a large load capacity and high rigidity. Therefore, double-row angular contact ball bearings are often used in places where a relatively large load is applied, such as pinion shafts of differential gears (final reducers) of automobiles, among vehicles and machines.

特許文献１には、自動車用トランスファーに使用されている複列アンギュラ玉軸受が開示されている。特許文献１の複列アンギュラ形玉軸受１６は、図２に示されているように、外輪側がケーシング１に固定されていて、内輪側が傘ピニオン軸５に固定されている。 Patent Document 1 discloses a double-row angular contact ball bearing used in an automobile transfer. As shown in FIG. 2, in the double row angular contact ball bearing 16 of Patent Document 1, the outer ring side is fixed to the casing 1 and the inner ring side is fixed to the umbrella pinion shaft 5.

自動車部品に使用される複列アンギュラ玉軸受は、ハウジング側に固定された外輪と、軸側に固定された内輪とで、分離可能になっているものも多い。分離型複列アンギュラ玉軸受であれば、あらかじめ外輪をハウジングに固定し、内輪を軸に固定しておくことで、ハウジングに軸を挿入する作業に並行して軸受の組付け作業も完了できる。そのため、強固に組み付けられた非分離型の軸受が存在する状態でハウジングに軸を挿入する場合に比べて、作業の労力を減らすことができる。 In many cases, double-row angular contact ball bearings used for automobile parts are separable between an outer ring fixed to the housing side and an inner ring fixed to the shaft side. In the case of separate double-row angular contact ball bearings, by fixing the outer ring to the housing and fixing the inner ring to the shaft in advance, the bearing assembly work can be completed in parallel with the work of inserting the shaft into the housing. Therefore, the labor of work can be reduced as compared with the case where the shaft is inserted into the housing in the presence of a firmly assembled non-separable type bearing.

特許第４０５８２４１号公報Japanese Patent No. 4058241

しかしながら、自動車部品等に使用される軸受の外輪や内輪、および玉（鋼球）は、金属製品として厳格な品質管理の元で加工されているものの、同じ称呼寸法（基準値）で製造された同じロットの物同士であってもわずかながら寸法差が生じる。そのため、従来の分離型複列アンギュラ玉軸受にあっては、軸受として完成した状態における寸法精度を保つために、外輪と内輪のペアを解消することなく管理する必要があった。例えば、自動車部品等の組立工程において、ある軸受の内輪と外輪のペアを分離させて、内輪に軸をはめ込み、外輪をハウジングにはめ込んだ後には、内輪と外輪が再び同じペアに戻るように軸とハウジングを組み合わせていた。換言すれば、同じ型番の軸受であっても、ある軸受の外輪（または内輪）は他の軸受の内輪（または外輪）と互換性がなかった。 However, although the outer and inner rings and balls (steel balls) of bearings used for automobile parts are processed under strict quality control as metal products, they are manufactured with the same nominal dimensions (standard values). Even if the products are in the same lot, there will be a slight dimensional difference. Therefore, in the conventional separate type double row angular contact ball bearing, it is necessary to manage the pair of the outer ring and the inner ring without eliminating the pair in order to maintain the dimensional accuracy in the completed state as the bearing. For example, in the assembly process of automobile parts, etc., the pair of inner ring and outer ring of a certain bearing is separated, the shaft is fitted to the inner ring, and after the outer ring is fitted to the housing, the shaft so that the inner ring and the outer ring return to the same pair again. And the housing were combined. In other words, the outer ring (or inner ring) of one bearing was not compatible with the inner ring (or outer ring) of another bearing, even for bearings of the same model number.

上記のように軸受の内輪と外輪を管理するためには、必然的にある工場のひとつのラインで軸受の分離から再組立てまで行うことになる。しかしながら、近年の生産工程の細分化と多様化によれば、内輪側の部品の組立てと外輪側の部品の組立てとを別々に行い得ることが望ましい。仮にある軸受の外輪（または内輪）が他の軸受の内輪（または外輪）と互換性があれば、内輪側の部品の組立てと外輪側の部品の組立てを他のライン、他の工場、さらには異なる国の生産拠点で製造することも可能となる。すると、例えば、軸に内輪をはめ込んだ上で軸に他の加工を施すことが可能になり、ハウジングに外輪をはめ込んだ上でさらに他の加工を施すことも可能になる。すなわち、軸は軸の工場、ハウジングはハウジングの工場で生産することが可能となり、軸受を設置することによる生産工程の制限がなくなるという大きな利点がある。 In order to manage the inner ring and outer ring of the bearing as described above, it is inevitable that one line of a certain factory will be used for bearing separation and reassembly. However, according to the subdivision and diversification of production processes in recent years, it is desirable that the parts on the inner ring side and the parts on the outer ring side can be assembled separately. If the outer ring (or inner ring) of one bearing is compatible with the inner ring (or outer ring) of another bearing, the parts on the inner ring side and the parts on the outer ring side can be assembled on other lines, other factories, and even. It will also be possible to manufacture at production bases in different countries. Then, for example, it becomes possible to fit the inner ring into the shaft and then perform other processing on the shaft, and it is also possible to fit the outer ring into the housing and then perform other processing. That is, the shaft can be produced at the shaft factory and the housing can be produced at the housing factory, and there is a great advantage that the production process is not restricted by installing the bearing.

本発明は、このような課題に鑑み、寸法精度が高く、さらには他の外輪アッシィおよび内輪アッシィとの互換性が確保された分離型複列アンギュラ玉軸受とその外輪アッシィおよび内輪アッシィを提供することを目的としている。 In view of these problems, the present invention provides a separate double-row angular contact ball bearing having high dimensional accuracy and ensuring compatibility with other outer ring assemblies and inner ring assemblies, and the outer ring assembly and inner ring assembly thereof. The purpose is.

上記課題を解決するために、本発明にかかる分離型複列アンギュラ玉軸受の代表的な構成は、外輪と内輪と２列の玉とを備えた分離型複列アンギュラ玉軸受において、外輪は２列の軌道溝のうち一方側の軌道溝が肩を落としたカウンタボア形状であり、内輪は２列の軌道溝のうち他方側の軌道溝が肩を落としたカウンタボア形状であり、外輪とカウンタボアの形成されていない軌道溝に保持された玉の列とを含む外輪アッシィが形成され、内輪とカウンタボアの形成されていない軌道溝に保持された玉の列とを含む内輪アッシィが形成されていて、外輪アッシィの玉は、称呼寸法からなる理想的な形状の内輪アッシィに対して所定の組幅精度になる寸法のものであることを特徴とする。 In order to solve the above problems, a typical configuration of the separate double-row angular contact ball bearing according to the present invention is a separate double-row angular contact ball bearing having an outer ring, an inner ring, and two rows of balls, in which the outer ring is two. The raceway groove on one side of the raceway grooves in the row has a counterbore shape with the shoulder dropped, and the inner ring has a counterbore shape in which the raceway groove on the other side of the raceway grooves in the two rows has the shoulder dropped. An outer ring assembly is formed that includes a row of balls held in the raceway groove without a bore, and an inner ring assembly is formed that includes an inner ring and a row of balls held in the raceway groove without a counterbore. The ball of the outer ring assembly is characterized in that the ball has a predetermined assembly width accuracy with respect to the inner ring assembly having an ideal shape having the nominal size.

上記構成によれば、玉のゲージ（ロットの平均直径と呼び直径との寸法差）を利用して、外輪の称呼寸法に対する誤差を吸収し、より称呼寸法に近い外輪アッシィが実現できる。したがって、軸受全体としても寸法精度を高め、２列の玉の同時接触性を確保し、品質を向上させることができる。 According to the above configuration, an error with respect to the nominal size of the outer ring can be absorbed by using the ball gauge (dimension difference between the average diameter of the lot and the nominal diameter), and an outer ring assembly closer to the nominal size can be realized. Therefore, the dimensional accuracy of the bearing as a whole can be improved, the simultaneous contact property of the two rows of balls can be ensured, and the quality can be improved.

上記課題を解決するために、本発明にかかる分離型複列アンギュラ玉軸受の他の代表的な構成は、外輪と内輪と２列の玉とを備えた分離型複列アンギュラ玉軸受において、外輪は２列の軌道溝のうち一方側の軌道溝が肩を落としたカウンタボア形状であり、内輪は２列の軌道溝のうち他方側の軌道溝が肩を落としたカウンタボア形状であり、外輪とカウンタボアの形成されていない軌道溝に保持された玉の列とを含む外輪アッシィが形成され、内輪とカウンタボアの形成されていない軌道溝に保持された玉の列とを含む内輪アッシィが形成されていて、内輪アッシィの玉は、称呼寸法からなる理想的な形状の外輪アッシィに対して所定の組幅精度になる寸法のものであることを特徴とする。 In order to solve the above problems, another typical configuration of the separated double-row angular contact ball bearing according to the present invention is an outer ring in a separate double-row angular contact ball bearing including an outer ring, an inner ring, and two rows of balls. Is a counterbore shape in which the raceway groove on one side of the two rows of raceway grooves has a shoulder dropped, and the inner ring has a counterbore shape in which the raceway groove on the other side of the raceway grooves in the two rows has a shoulder drop. And an outer ring assembly containing a row of balls held in a raceway groove without a counterbore is formed, and an inner ring assembly containing an inner ring and a row of balls held in a raceway groove without a counterbore is formed. The ball of the inner ring assembly, which is formed, is characterized in that the ball has a size having a predetermined assembly width accuracy with respect to the outer ring assembly having an ideal shape having a nominal size.

上記構成によれば、玉のゲージを利用して、内輪の称呼寸法に対する誤差を吸収し、より称呼寸法に近い内輪アッシィが実現できる。したがって、軸受全体としても寸法精度を高め、２列の玉の同時接触性を確保し、品質を向上させることができる。 According to the above configuration, the ball gauge can be used to absorb an error with respect to the nominal size of the inner ring, and an inner ring assembly closer to the nominal size can be realized. Therefore, the dimensional accuracy of the bearing as a whole can be improved, the simultaneous contact property of the two rows of balls can be ensured, and the quality can be improved.

上記課題を解決するために、本発明にかかる外輪アッシィの代表的な構成は、所定の内輪アッシィと分離可能に組み合されて分離型複列アンギュラ玉軸受となる外輪アッシィにおいて、外輪の２列の軌道溝のうち一方側の軌道溝が肩を落としたカウンタボア形状であり、外輪のカウンタボアの形成されていない軌道溝に玉の列が保持されていて、玉は、称呼寸法からなる理想的な形状の内輪アッシィに対して所定の組幅精度になる寸法のものであることを特徴とする。 In order to solve the above problems, a typical configuration of the outer ring assembly according to the present invention is a two-row outer ring in an outer ring assembly that is separably combined with a predetermined inner ring assembly to form a separable double-row angular contact ball bearing. The raceway groove on one side of the raceway groove has a counterbore shape with the shoulder dropped, and a row of balls is held in the raceway groove where the counterbore of the outer ring is not formed, and the ball is ideally composed of nominal dimensions. It is characterized by having a size having a predetermined assembly width accuracy with respect to an inner ring assembly having a specific shape.

上記構成によっても、玉のゲージを利用して、外輪の称呼寸法に対する誤差を吸収し、より称呼寸法に近い外輪アッシィが実現できる。したがって、軸受全体としても寸法精度を高め、品質を向上させることができる。 Even with the above configuration, an error with respect to the nominal size of the outer ring can be absorbed by using the ball gauge, and an outer ring assembly closer to the nominal size can be realized. Therefore, the dimensional accuracy of the bearing as a whole can be improved and the quality can be improved.

上記課題を解決するために、本発明にかかる内輪アッシィの代表的な構成は、所定の外輪アッシィと分離可能に組み合されて分離型複列アンギュラ玉軸受となる内輪アッシィにおいて、内輪の２列の軌道溝のうち一方側の軌道溝が肩を落としたカウンタボア形状であり、内輪のカウンタボアの形成されていない軌道溝に玉の列が保持されていて、玉は、称呼寸法からなる理想的な形状の外輪アッシィに対して所定の組幅精度になる寸法のものであることを特徴とする。 In order to solve the above problems, a typical configuration of the inner ring assembly according to the present invention is an inner ring assembly that is separably combined with a predetermined outer ring assembly to form a separable double-row angular contact ball bearing, in which two rows of inner rings are provided. The raceway groove on one side of the raceway groove has a counterbore shape with the shoulder dropped, and a row of balls is held in the raceway groove where the counterbore of the inner ring is not formed, and the ball is ideally composed of nominal dimensions. It is characterized in that it has a size that gives a predetermined assembly width accuracy with respect to an outer ring assembly having a specific shape.

上記構成によっても、玉のゲージを利用して、内輪の称呼寸法に対する誤差を吸収し、より称呼寸法に近い内輪アッシィが実現できる。したがって、軸受全体としても寸法精度を高め、品質を向上させることができる。 Even with the above configuration, an error with respect to the nominal size of the inner ring can be absorbed by using the ball gauge, and an inner ring assembly closer to the nominal size can be realized. Therefore, the dimensional accuracy of the bearing as a whole can be improved and the quality can be improved.

上記課題を解決するために、本発明にかかる分離型複列アンギュラ玉軸受の他の代表的な構成は、外輪と内輪と２列の玉とを備えた分離型複列アンギュラ玉軸受において、外輪は２列の軌道溝のうち一方側の軌道溝が肩を落としたカウンタボア形状であり、内輪は２列の軌道溝のうち他方側の軌道溝が肩を落としたカウンタボア形状であり、外輪とカウンタボアの形成されていない軌道溝に保持された玉の列とを含む外輪アッシィが形成され、内輪とカウンタボアの形成されていない軌道溝に保持された玉の列とを含む内輪アッシィが形成されていて、外輪アッシィの玉は、称呼寸法からなる理想的な形状の内輪アッシィに対して所定の組幅精度になる寸法のものであり、内輪アッシィの玉は、称呼寸法からなる理想的な形状の外輪アッシィに対して所定の組幅精度になる寸法のものであることを特徴とする。 In order to solve the above problems, another typical configuration of the separated double-row angular contact ball bearing according to the present invention is an outer ring in a separate double-row angular contact ball bearing including an outer ring, an inner ring and two rows of balls. Is a counterbore shape in which the raceway groove on one side of the two rows of raceway grooves has a shoulder dropped, and the inner ring has a counterbore shape in which the raceway groove on the other side of the raceway grooves in the two rows has a shoulder drop. And an outer ring assembly containing a row of balls held in a raceway groove without a counterbore is formed, and an inner ring assembly containing an inner ring and a row of balls held in a raceway groove without a counterbore is formed. The ball of the outer ring assembly that is formed has a size that has a predetermined assembly width accuracy with respect to the inner ring assembly having an ideal shape having the nominal size, and the ball of the inner ring assembly has an ideal shape having the nominal size. It is characterized in that it has a size that gives a predetermined assembly width accuracy to an outer ring assembly having a different shape.

上記構成によれば、玉のゲージを利用して、外輪および内輪のそれぞれの称呼寸法に対する誤差を吸収し、より称呼寸法に近い外輪アッシィおよび内輪アッシィが実現できる。これら称呼寸法に近い外輪アッシィおよび内輪アッシィであれば、分離後に他の外輪アッシィおよび内輪アッシィと再組立てした場合にも、軸受としての組幅精度および玉の同時接触を保証することができる。すなわち、上記構成であれば、寸法精度の高い軸受が実現できるだけでなく、分離後に他の外輪アッシィおよび内輪アッシィと組み替えても品質が維持できる、互換性の高い分離型複列アンギュラ玉軸受を提供することができる。 According to the above configuration, the ball gauge can be used to absorb errors in the nominal dimensions of the outer ring and the inner ring, and an outer ring assembly and an inner ring assembly closer to the nominal dimensions can be realized. If the outer ring assembly and the inner ring assembly are close to these nominal dimensions, the assembly width accuracy as a bearing and the simultaneous contact of the balls can be guaranteed even when the outer ring assembly and the inner ring assembly are reassembled after separation. That is, with the above configuration, not only can a bearing with high dimensional accuracy be realized, but also a highly compatible separate double-row angular contact ball bearing that can maintain quality even if it is recombined with other outer ring assemblies and inner ring assemblies after separation is provided. can do.

当該分離型複列アンギュラ玉軸受は、外輪および内輪が玉と多点接触可能になっていてもよい。当該分離型複列アンギュラ玉軸受は玉の同時接触が保証されているため、さらに３点や４点等の多点接触に設定することでより負荷能力が大きく剛性も高い軸受を提供することができる。 In the separate type double row angular contact ball bearing, the outer ring and the inner ring may be capable of multipoint contact with the ball. Since the separate type double row angular contact ball bearing guarantees simultaneous contact of balls, it is possible to provide a bearing with larger load capacity and higher rigidity by setting multi-point contact such as 3 points or 4 points. can.

本発明によれば、寸法精度が高く、さらには他の外輪アッシィおよび内輪アッシィとの互換性が確保された分離型複列アンギュラ玉軸受とその外輪アッシィおよび内輪アッシィを提供することが可能になる。 INDUSTRIAL APPLICABILITY According to the present invention, it becomes possible to provide a separate double-row angular contact ball bearing having high dimensional accuracy and ensuring compatibility with other outer ring assemblies and inner ring assemblies, and the outer ring assembly and inner ring assembly thereof. ..

本発明の実施形態にかかる分離型複列アンギュラ玉軸受を用いた差動装置の図である。It is a figure of the differential device which used the separated type double row angular contact ball bearing which concerns on embodiment of this invention. 図１の分離型複列アンギュラ玉軸受を拡大して示した図である。It is an enlarged view which showed the separated type double row angular contact ball bearing of FIG. 外輪アッシィの玉の選定を説明する図である。It is a figure explaining the selection of the ball of the outer ring assembly. 内輪アッシィの玉の選定を説明する図である。It is a figure explaining the selection of the ball of the inner ring assembly. 分離型複列アンギュラ玉軸受の変形例を示した図である。It is a figure which showed the deformation example of the separated type double row angular contact ball bearing.

以下に添付図面を参照しながら、本発明の好適な実施形態について詳細に説明する。かかる実施形態に示す寸法、材料、その他具体的な数値などは、発明の理解を容易とするための例示に過ぎず、特に断る場合を除き、本発明を限定するものではない。なお、本明細書及び図面において、実質的に同一の機能、構成を有する要素については、同一の符号を付することにより重複説明を省略し、また本発明に直接関係のない要素は図示または説明を省略する。 Preferred embodiments of the present invention will be described in detail below with reference to the accompanying drawings. The dimensions, materials, and other specific numerical values shown in the embodiment are merely examples for facilitating the understanding of the invention, and do not limit the present invention unless otherwise specified. In the present specification and the drawings, elements having substantially the same function and configuration are designated by the same reference numerals to omit duplicate description, and elements not directly related to the present invention are illustrated or described. Is omitted.

（分離型複列アンギュラ玉軸受１００）
図１は、本発明の実施形態にかかる分離型複列アンギュラ玉軸受１００を用いた差動装置１０２の図である。図１に示す差動装置１０２では、当該分離型複列アンギュラ玉軸受１００と他のアンギュラ玉軸受１０４を使用して、ピニオン軸１０６を回転可能に支えている。 (Separate type double row angular contact ball bearing 100)
FIG. 1 is a diagram of a differential device 102 using a separate double-row angular contact ball bearing 100 according to an embodiment of the present invention. In the differential device 102 shown in FIG. 1, the separate type double row angular contact ball bearing 100 and another angular contact ball bearing 104 are used to rotatably support the pinion shaft 106.

差動装置１０２では、リングギヤ１０８とピニオンギヤ１１０が噛合している。ピニオンギヤ１１０はピニオン軸１０６（ギヤ軸）の一端に備えられていて、ピニオン軸１０６の他端にはフランジ１１２（コンパニオンフランジ、または接続フランジともいう）が備えられている。フランジ１１２は不図示のプロペラシャフトに接続される部位である。ピニオン軸１０６やピニオンギヤ１１０の外側には、ハウジング１１４が設けられている。 In the differential device 102, the ring gear 108 and the pinion gear 110 are meshed with each other. The pinion gear 110 is provided at one end of the pinion shaft 106 (gear shaft), and a flange 112 (also referred to as a companion flange or a connecting flange) is provided at the other end of the pinion shaft 106. The flange 112 is a portion connected to a propeller shaft (not shown). A housing 114 is provided on the outside of the pinion shaft 106 and the pinion gear 110.

分離型複列アンギュラ玉軸受１００は、ピニオンギヤ１１０の近傍に設けられている。分離型複列アンギュラ玉軸受１００は、外輪１１６がハウジング１１４に固定されていて、内輪１１８がピニオン軸１０６に固定されている。アンギュラ玉軸受１０４は、フランジ１１２の近傍（ピニオン軸１０６のうちピニオンギヤ１１０とは反対側）に設けられている。 The separate double row angular contact ball bearing 100 is provided in the vicinity of the pinion gear 110. In the separate type double row angular contact ball bearing 100, the outer ring 116 is fixed to the housing 114, and the inner ring 118 is fixed to the pinion shaft 106. The angular contact ball bearing 104 is provided in the vicinity of the flange 112 (on the side of the pinion shaft 106 opposite to the pinion gear 110).

図２は、図１の分離型複列アンギュラ玉軸受１００を拡大して示した図である。図２（ａ）は、分離型複列アンギュラ玉軸受１００の全体の概要を示している。図２（ａ）に示すように、当該分離型複列アンギュラ玉軸受１００は、外輪１１６と、内輪１１８と、これら外輪１１６と内輪１１８との間に形成された２列の玉１２０、１２２を備えている。本実施形態では、玉１２０、１２２は、同じ呼び直径で、同じピッチ径に設定されている。 FIG. 2 is an enlarged view of the separate double row angular contact ball bearing 100 of FIG. 1. FIG. 2A shows an overall outline of the separate type double row angular contact ball bearing 100. As shown in FIG. 2A, the separate double-row angular contact ball bearing 100 has an outer ring 116, an inner ring 118, and two rows of balls 120, 122 formed between the outer ring 116 and the inner ring 118. I have. In the present embodiment, the balls 120 and 122 have the same nominal diameter and the same pitch diameter.

分離型複列アンギュラ玉軸受１００は、外輪１１６および玉１２０を含む外輪アッシィ１２４と、内輪１１８および玉１２２を含む内輪アッシィ１２６とに分離可能になっている。分離型複列アンギュラ玉軸受１００は、外輪アッシィ１２４をハウジング１１４（図１参照）に固定し、内輪アッシィ１２６をピニオン軸１０６に固定して、分離することができる。分離型複列アンギュラ玉軸受１００は、分離可能になっていることで、ハウジング１１４およびピニオン軸１０６の組立て作業を行いやすくするだけでなく、そのメンテナンスや再組立てなどの作業も行いやすくする。 The separate double row angular contact ball bearing 100 is separable into an outer ring assembly 124 including an outer ring 116 and a ball 120 and an inner ring assembly 126 including an inner ring 118 and a ball 122. The separate type double row angular contact ball bearing 100 can be separated by fixing the outer ring assembly 124 to the housing 114 (see FIG. 1) and fixing the inner ring assembly 126 to the pinion shaft 106. The separable double-row angular contact ball bearing 100 is separable, which not only facilitates the assembly work of the housing 114 and the pinion shaft 106, but also facilitates the maintenance and reassembly work thereof.

図２（ｂ）は、図２（ａ）の外輪アッシィ１２４を単独で示した図である。外輪アッシィ１２４は、外輪１１６と一列の玉１２０、および保持器１２８から構成されている。外輪１１６は、内輪アッシィ１２６（図２（ａ）参照）と分離可能に組み合わせるために、２列の軌道溝１３０、１３２のうち、一方側の軌道溝１３２の肩を落とし、カウンタボア形状１３４が設けられているになっている。玉１２０は、カウンタボアの形成されていない軌道溝１３０に保持されている。保持器１２８は、玉１２０の列を軌道溝１３０に保持したまま内輪アッシィ１２６との分離を可能にしている。 FIG. 2B is a diagram showing the outer ring assembly 124 of FIG. 2A alone. The outer ring assembly 124 is composed of an outer ring 116, a row of balls 120, and a cage 128. In order to separably combine the outer ring 116 with the inner ring assembly 126 (see FIG. 2A), the shoulder of the raceway groove 132 on one side of the two rows of raceway grooves 130 and 132 is dropped, and the counter bore shape 134 is formed. It is supposed to be provided. The ball 120 is held in the track groove 130 in which the counter bore is not formed. The cage 128 enables separation from the inner ring assembly 126 while holding the row of balls 120 in the raceway groove 130.

図２（ｃ）は、図２（ａ）の内輪アッシィ１２６を単独で示した図である。内輪アッシィ１２６は、内輪１１８と一列の玉１２２、および保持器１３６から構成されている。内輪１１８は、外輪アッシィ１２４（図２（ｂ）参照）と分離可能に組み合わせるために、２列の軌道溝１３８、１４０のうち、軌道溝１３２（図２（ｂ））に対して他方側となる軌道溝１３８の肩を落とし、カウンタボア形状１４２になっている。玉１２２は、カウンタボアの形成されていない軌道溝１４０に保持されている。保持器１３６は、玉１２２の列を軌道溝１４０に保持したまま外輪アッシィ１２４との分離を可能にしている。 FIG. 2 (c) is a diagram showing the inner ring assembly 126 of FIG. 2 (a) alone. The inner ring assembly 126 is composed of an inner ring 118, a row of balls 122, and a cage 136. The inner ring 118 is separably combined with the outer ring assembly 124 (see FIG. 2B), so that the inner ring 118 is on the other side of the two rows of raceway grooves 138 and 140 with respect to the raceway groove 132 (FIG. 2B). The shoulder of the track groove 138 is dropped to form a counter bore shape 142. The ball 122 is held in the track groove 140 in which the counter bore is not formed. The cage 136 enables separation from the outer ring assembly 124 while holding the row of balls 122 in the raceway groove 140.

図２（ａ）に示した本実施形態の分離型複列アンギュラ玉軸受１００は、外輪１１６および内輪１１８の製造誤差に合わせて、玉１２０、１２２のゲージ（ロットの平均直径と呼び直径との寸法差）を選定している。ここで重要なことは、外輪アッシィ１２４と内輪アッシィ１２６がそれぞれ玉の列を有していて、外輪アッシィ１２４においては後述する基準内輪に対して玉のゲージを選定し、内輪アッシィ１２６においては後述する基準外輪に対して玉のゲージを選定していることである。これにより、同一規格の他の軸受の外輪アッシィおよび内輪アッシィとの互換性を確保することができる。以下、外輪アッシィ１２４および内輪アッシィ１２６の構成について、さらに説明を行う。 In the separate double row angular contact ball bearing 100 of the present embodiment shown in FIG. 2A, the gauges of the balls 120 and 122 (the average diameter and the nominal diameter of the lot) are adjusted to match the manufacturing errors of the outer ring 116 and the inner ring 118. Dimensional difference) is selected. What is important here is that the outer ring assembly 124 and the inner ring assembly 126 each have a row of balls, and in the outer ring assembly 124, a ball gauge is selected for the reference inner ring described later, and in the inner ring assembly 126, the ball gauge is selected, which will be described later. It means that the gauge of the ball is selected for the standard outer ring. This makes it possible to ensure compatibility with the outer ring assembly and the inner ring assembly of other bearings of the same standard. Hereinafter, the configurations of the outer ring assembly 124 and the inner ring assembly 126 will be further described.

（外輪アッシィ）
図３は外輪アッシィ１２４の玉の選定を説明する図である。図３（ａ）は玉の選定前の状態を示している。本実施形態では、外輪アッシィ１２４に設ける玉１２０を選定するために、基準内輪１４４を利用している。 (Outer ring assembly)
FIG. 3 is a diagram illustrating selection of balls for the outer ring assembly 124. FIG. 3A shows a state before selection of balls. In this embodiment, the reference inner ring 144 is used to select the ball 120 provided in the outer ring assembly 124.

基準内輪１４４は、称呼寸法からなる理想的な形状の内輪アッシィである。例えば、基準内輪１４４は、内輪１４６の幅、軌道面１４８、１４９の径および曲率半径、玉１５０の直径がすべて、分離型複列アンギュラ玉軸受１００（図２（ａ）参照）の称呼寸法（きわめて小さい誤差）で形成されている。外輪アッシィ１２４は、基準内輪１４４を利用し、分離型複列アンギュラ玉軸受１００を組み上げたときの組幅精度および２列の玉の同時接触性が所定の値になるよう、玉の寸法（ゲージ）が選定される。 The reference inner ring 144 is an inner ring assembly having an ideal shape having nominal dimensions. For example, the reference inner ring 144 has the width of the inner ring 146, the diameter and radius of curvature of the raceway surface 148, 149, and the diameter of the ball 150, all of which are the nominal dimensions of the separate double row angular contact ball bearing 100 (see FIG. 2A). It is formed with a very small error). The outer ring assembly 124 uses the reference inner ring 144, and the ball dimensions (gauge) so that the assembly width accuracy and the simultaneous contact property of the two rows of balls when the separate double row angular contact ball bearing 100 is assembled become predetermined values. ) Is selected.

玉のゲージを選定するために、まず外輪アッシィ１２４を、外輪１１６と、任意の玉１５２とで組む。玉１５２は、分離型複列アンギュラ玉軸受１００の玉の称呼寸法から選んだ任意のゲージのものである。そして、外輪アッシィ１２４を基準内輪１４４とペアにし、軸受１５４を形成する。 In order to select the gauge of the ball, first, the outer ring assembly 124 is assembled with the outer ring 116 and an arbitrary ball 152. The ball 152 is of an arbitrary gauge selected from the nominal size of the ball of the separate type double row angular contact ball bearing 100. Then, the outer ring assembly 124 is paired with the reference inner ring 144 to form the bearing 154.

軸受１５４は、測定装置で寸法等の各種項目を測定する。測定した値の成績からは、基準内輪１４４がきわめて小さい誤差で形成されていることから、外輪１１６の製造誤差が判明する。特に、二列の軌道溝１３０、１３２に対して、軌道径ｄ１と軌道径ｄ２とに相互差が生じているか否か、軌道径の互いの距離（ピッチＰｅ）が称呼寸法から乖離しているか否かが判明する。 The bearing 154 measures various items such as dimensions with a measuring device. From the results of the measured values, the manufacturing error of the outer ring 116 can be found because the reference inner ring 144 is formed with an extremely small error. In particular, whether or not there is a mutual difference between the track diameters d1 and the track diameters d2 with respect to the two rows of track grooves 130 and 132, and whether the mutual distances (pitch Pe) of the track diameters deviate from the nominal dimensions. It turns out whether or not.

外輪１１６に軌道溝１３０を設けるとき、破線で示す理想的な形状と比べて、実線で示す実際の形状には誤差が生じていることがある。その結果、例えば、軌道径ｄ１と軌道径ｄ２とに相互差Δｄｏ（Δｄｏ＞０）が表れ、軌道径の互いの距離に称呼寸法に対する乖離値ΔＰｅ（ΔＰｅ＞０）が表れた場合、玉１５２が内輪１４６に接触していても、玉１５０が外輪１１６に接触しないことがある。この場合、外輪１１６と玉１５０とは、軸受１５４に外力が加わってその分の変位が生じたときに初めて接触し、接触点も当初の設定からずれてしまう。このときの外輪１１６と玉１５０との接触遅れ量が、相互差Δｄｏおよび乖離値ΔＰｅを得ることで計算可能になる。 When the raceway groove 130 is provided in the outer ring 116, an error may occur in the actual shape shown by the solid line as compared with the ideal shape shown by the broken line. As a result, for example, when the mutual difference Δdo (Δdo> 0) appears between the orbital diameter d1 and the orbital diameter d2, and the deviation value ΔPe (ΔPe> 0) with respect to the nominal dimension appears in the mutual distance of the orbital diameters, the ball 152. May not contact the outer ring 116 even if the ball 150 is in contact with the inner ring 146. In this case, the outer ring 116 and the ball 150 come into contact with each other only when an external force is applied to the bearing 154 and a displacement corresponding to the force is generated, and the contact point also deviates from the initial setting. The contact delay amount between the outer ring 116 and the ball 150 at this time can be calculated by obtaining the mutual difference Δdo and the deviation value ΔPe.

外輪アッシィ１２４と基準内輪１４４との同時接触は、相互差Δｄｏおよび乖離値ΔＰｅを吸収することで達成できる。基準内輪１４４の玉１５０は称呼寸法（きわめて小さい誤差）であるため、外輪アッシィ１２４の接触遅れ量は玉１５２を交換することで吸収できる。 Simultaneous contact between the outer ring assembly 124 and the reference inner ring 144 can be achieved by absorbing the mutual difference Δdo and the deviation value ΔPe. Since the ball 150 of the reference inner ring 144 has a nominal size (extremely small error), the contact delay amount of the outer ring assembly 124 can be absorbed by replacing the ball 152.

図３（ｂ）は玉の選定後の状態を示している。玉１５２（図３（ａ）参照）を設置した場合の接触遅れ量をもとにゲージを選定し、例えば小さいサイズの玉１２０を選定する。選定後の玉１２０によれば、選定前の玉１５２（図３（ａ）参照）に比べて、外輪１１６の軌道溝１３０側に軸方向のすきまが得られ、軌道溝１３２と玉１５０とも当初の設定に近い状態で接触する。これによって、外輪アッシィ１２４と基準内輪１４４の同時接触が可能になる。 FIG. 3B shows the state after the ball is selected. A gauge is selected based on the contact delay amount when the ball 152 (see FIG. 3A) is installed, and for example, a ball 120 having a small size is selected. According to the ball 120 after selection, an axial clearance is obtained on the raceway groove 130 side of the outer ring 116 as compared with the ball 152 before selection (see FIG. 3A), and both the raceway groove 132 and the ball 150 are initially. Contact in a state close to the setting of. This enables simultaneous contact between the outer ring assembly 124 and the reference inner ring 144.

上記のように、当該外輪アッシィ１２４は、外輪１１６の軌道径の相互差Δｄｏやピッチの乖離値ΔＰｅなどの誤差を、玉１２０のゲージを利用して吸収可能になっている。本実施形態であれば、より称呼寸法に近い外輪アッシィ１２４が実現できる。この外輪アッシィ１２４であれば、分離型複列アンギュラ玉軸受１００（図２（ａ）参照）の寸法精度を高め、２列の玉の同時接触性も確保してその品質を向上させることができる。また、外輪アッシィ１２４は寸法精度が高いため、他の外輪アッシィとも高い互換性を有し、特定の内輪アッシィ１２６（図２（ａ）参照）だけでなく、他の内輪アッシィと組み合わせた場合にも、寸法精度の高い分離型複列アンギュラ玉軸受１００を実現することができる。 As described above, the outer ring assembly 124 can absorb errors such as the mutual difference Δdo of the track diameters of the outer ring 116 and the deviation value ΔPe of the pitch by using the gauge of the ball 120. According to this embodiment, the outer ring assembly 124 that is closer to the nominal size can be realized. With this outer ring assembly 124, the dimensional accuracy of the separate double-row angular contact ball bearing 100 (see FIG. 2A) can be improved, and the simultaneous contact property of the two-row balls can be ensured to improve the quality. .. Further, since the outer ring assembly 124 has high dimensional accuracy, it has high compatibility with other outer ring assemblies, and when combined with not only a specific inner ring assembly 126 (see FIG. 2A) but also another inner ring assembly. Also, it is possible to realize a separate type double row angular contact ball bearing 100 with high dimensional accuracy.

なお、図３（ａ）の場合において、外輪１１６の製造誤差の程度によっては、基準内輪１４４の玉１５０が先に外輪アッシィ１２４に接触し、外輪アッシィ１２４側の玉が基準内輪１４４に接触しない場合もある。その場合は、玉１２０にゲージの大きい玉を選定することで、外輪アッシィ１２４と基準内輪１４４との同時接触が可能になる。このように、本実施形態の技術的思想であれば、外輪アッシィ１２４と基準内輪１４４との接触遅れ量に合わせて玉のゲージを選定することで、互換性のある外輪アッシィ１２４および分離型複列アンギュラ玉軸受１００が実現できる。 In the case of FIG. 3A, depending on the degree of manufacturing error of the outer ring 116, the ball 150 of the reference inner ring 144 first contacts the outer ring assembly 124, and the ball on the outer ring assembly 124 side does not contact the reference inner ring 144. In some cases. In that case, by selecting a ball having a large gauge for the ball 120, simultaneous contact between the outer ring assembly 124 and the reference inner ring 144 becomes possible. As described above, according to the technical idea of the present embodiment, by selecting the ball gauge according to the contact delay amount between the outer ring assembly 124 and the reference inner ring 144, the outer ring assembly 124 and the separate type double are compatible. A row angular contact ball bearing 100 can be realized.

（内輪アッシィ）
図４は内輪アッシィ１２６の玉の選定を説明する図である。図４（ａ）は玉の選定前の状態を示している。内輪アッシィ１２６も、上述した外輪アッシィ１２４と同様の手法で、称呼寸法からなる理想的な形状の外輪アッシィである基準外輪１６０を利用し、分離型複列アンギュラ玉軸受１００を組み上げたときの組幅精度および２列の玉の同時接触性が所定の値になるよう、玉の寸法（ゲージ）が選定されている。 (Inner ring assembly)
FIG. 4 is a diagram illustrating selection of balls for the inner ring assembly 126. FIG. 4A shows a state before selection of balls. The inner ring assembly 126 is also a set when the separate type double row angular contact ball bearing 100 is assembled by using the reference outer ring 160 which is an outer ring assembly having an ideal shape having nominal dimensions by the same method as the outer ring assembly 124 described above. The size (gauge) of the balls is selected so that the width accuracy and the simultaneous contact of the balls in two rows have predetermined values.

基準外輪１６０も、外輪１６２の幅、軌道面１６４、１６６の径および曲率半径、玉１６８の直径がすべて、分離型複列アンギュラ玉軸受１００（図２（ａ）参照）の称呼寸法（きわめて小さい誤差）で形成されている。 The reference outer ring 160 also has the nominal dimensions (extremely small) of the separate double row angular contact ball bearing 100 (see FIG. 2A) in that the width of the outer ring 162, the diameter and radius of curvature of the raceway surfaces 164 and 166, and the diameter of the ball 168 are all. It is formed by error).

内輪アッシィ１２６もまた、内輪１１８と、任意のゲージの玉１７０とで組む。玉１７０は、分離型複列アンギュラ玉軸受１００の玉の称呼寸法から選んだ任意のゲージのものである。そして、内輪アッシィ１２６と基準外輪１６０とをペアにし、軸受１７２を形成する。そして、測定装置で軸受１７２の寸法等を測定し、内輪１１８の製造誤差を判定する。 The inner ring assembly 126 is also assembled with the inner ring 118 and a ball 170 of an arbitrary gauge. The balls 170 are of any gauge selected from the nominal dimensions of the balls of the separate double row angular contact ball bearing 100. Then, the inner ring assembly 126 and the reference outer ring 160 are paired to form a bearing 172. Then, the dimensions and the like of the bearing 172 are measured by the measuring device, and the manufacturing error of the inner ring 118 is determined.

例えば、内輪１１８に軌道溝１４０を設けるときも、破線で示す理想的な形状と比べて、実線で示す実際の形状には誤差が生じていることがある。その場合、玉１７０が外輪１６２に接触していても、玉１６８が内輪１１８に接触しないことがある。すると、軸受１７２に外力が加わったときに玉１６８と内輪１１８とが初めて接触し、接触点も当初の設定からずれてしまう。このような内輪１１８の誤差が、二列の軌道溝１３８、１４０に対して、軌道径Ｄ１と軌道径Ｄ２とに相互差が生じているか否か、軌道径の互いの距離（ピッチＰｉ）が称呼寸法から乖離しているか否かによって判明する。 For example, even when the raceway groove 140 is provided in the inner ring 118, an error may occur in the actual shape shown by the solid line as compared with the ideal shape shown by the broken line. In that case, even if the ball 170 is in contact with the outer ring 162, the ball 168 may not be in contact with the inner ring 118. Then, when an external force is applied to the bearing 172, the ball 168 and the inner ring 118 come into contact with each other for the first time, and the contact point also deviates from the initial setting. Whether or not such an error of the inner ring 118 causes a mutual difference between the track diameter D1 and the track diameter D2 with respect to the two rows of raceway grooves 138 and 140, and the mutual distance (pitch Pi) of the raceway diameters. It is determined by whether or not it deviates from the nominal size.

内輪アッシィ１２６と基準外輪１６０との同時接触もまた、相互差ΔＤｏおよび乖離値ΔＰｉを吸収することで達成できる。基準外輪１６０の玉１６８は称呼寸法（きわめて小さい誤差）であるため、内輪アッシィ１２６の接触遅れ量は玉１７０を交換することで吸収できる。 Simultaneous contact between the inner ring assembly 126 and the reference outer ring 160 can also be achieved by absorbing the mutual difference ΔDo and the deviation value ΔPi. Since the ball 168 of the reference outer ring 160 has a nominal size (extremely small error), the contact delay amount of the inner ring assembly 126 can be absorbed by replacing the ball 170.

図４（ｂ）は玉の選定後の状態を示している。玉１７０（図４（ａ）参照）を設置した場合の接触遅れ量をもとに、例えば小さいゲージの玉１２２を選定する。選定後の玉１２２によれば、選定前の玉１７０（図４（ａ）参照）に比べて、内輪１１８の軌道溝１４０側に軸方向のすきまが得られ、軌道溝１３８と玉１６８とも当初の設定に近い状態で接触する。これによって、内輪アッシィ１２６と基準外輪１６０の同時接触が可能になる。また、基準外輪１６０の玉１６８が先に当たってしまう場合には、玉１２２にゲージの大きい玉を選定することで、内輪アッシィ１２６と基準外輪１６０との同時接触が可能になる。 FIG. 4B shows the state after the ball is selected. For example, a small gauge ball 122 is selected based on the contact delay amount when the ball 170 (see FIG. 4A) is installed. According to the ball 122 after selection, an axial clearance is obtained on the raceway groove 140 side of the inner ring 118 as compared with the ball 170 before selection (see FIG. 4A), and both the raceway groove 138 and the ball 168 are initially. Contact in a state close to the setting of. This enables simultaneous contact between the inner ring assembly 126 and the reference outer ring 160. Further, when the ball 168 of the reference outer ring 160 hits first, by selecting a ball having a large gauge for the ball 122, the inner ring assembly 126 and the reference outer ring 160 can be in contact with each other at the same time.

上記のように、当該内輪アッシィ１２６は、内輪１１８の軌道径の相互差ΔＤｏやピッチの乖離値ΔＰｉなどの誤差を、玉１２２のゲージを利用して吸収可能になっている。本実施形態であれば、より称呼寸法に近い内輪アッシィ１２６が実現できる。この内輪アッシィ１２６であれば、分離型複列アンギュラ玉軸受１００（図２（ａ）参照）の寸法精度を高め、２列の玉の同時接触性も確保してその品質を向上させることができる。また、内輪アッシィ１２６は寸法精度が高いため、他の内輪アッシィとも高い互換性を有し、特定の外輪アッシィ１２４（図２（ａ）参照）だけでなく、他の外輪アッシィと組み合わせた場合にも、寸法精度の高い分離型複列アンギュラ玉軸受１００を実現することができる。 As described above, the inner ring assembly 126 can absorb errors such as the mutual difference ΔDo of the track diameters of the inner ring 118 and the deviation value ΔPi of the pitch by using the gauge of the ball 122. According to this embodiment, the inner ring assembly 126 closer to the nominal size can be realized. With this inner ring assembly 126, the dimensional accuracy of the separate double-row angular contact ball bearing 100 (see FIG. 2A) can be improved, and the simultaneous contact property of the two-row balls can be ensured to improve the quality. .. Further, since the inner ring assembly 126 has high dimensional accuracy, it has high compatibility with other inner ring assemblies, and when combined with not only a specific outer ring assembly 124 (see FIG. 2A) but also another outer ring assembly. Also, it is possible to realize a separate type double row angular contact ball bearing 100 with high dimensional accuracy.

以上のように、図２（ａ）の分離型複列アンギュラ玉軸受１００は、玉１２０、１２２のゲージを利用して、外輪１１６および内輪１１８のそれぞれの称呼寸法に対する誤差を吸収し、より称呼寸法に近い外輪アッシィ１２４および内輪アッシィ１２６を実現している。これら称呼寸法に近い外輪アッシィ１２４および内輪アッシィ１２６であれば、分離後に他の外輪アッシィおよび内輪アッシィと再組立てした場合にも、軸受としての組幅精度および玉の同時接触を保証することができる。このように、当該分離型複列アンギュラ玉軸受１００は、高い寸法精度を実現しているだけでなく、分離後に他の外輪アッシィおよび内輪アッシィと組み替えても品質が維持できる、互換性の高い構造を実現している。 As described above, the separate double-row angular contact ball bearing 100 of FIG. 2A uses the gauges of the balls 120 and 122 to absorb errors in the nominal dimensions of the outer ring 116 and the inner ring 118, and is more named. The outer ring assembly 124 and the inner ring assembly 126, which are close to the dimensions, are realized. If the outer ring assembly 124 and the inner ring assembly 126 are close to these nominal dimensions, the assembly width accuracy as a bearing and the simultaneous contact of the balls can be guaranteed even when the outer ring assembly 124 and the inner ring assembly 126 are reassembled after separation. .. As described above, the separate type double row angular contact ball bearing 100 not only realizes high dimensional accuracy, but also has a highly compatible structure that can maintain the quality even if it is recombined with other outer ring assemblies and inner ring assemblies after separation. Has been realized.

（変形例）
図５は分離型複列アンギュラ玉軸受１００の変形例を示した図である。図５に示す各変形例は、玉の接触点の数において、図２（ａ）の分離型複列アンギュラ玉軸受１００と構成が異なっている。なお、以降の記載において、既に説明した構成要素については、同じ符号を付することによって、その説明を省略する。また、異なる符号が付された構成要素であっても、既に説明した構成要素と同じ名称のものは、同じ構成および機能を有するものとする。 (Modification example)
FIG. 5 is a diagram showing a modified example of the separate type double row angular contact ball bearing 100. Each modification shown in FIG. 5 has a different configuration from the separate double row angular contact ball bearing 100 shown in FIG. 2A in terms of the number of contact points of the balls. In the following description, the components already described will be designated by the same reference numerals, and the description thereof will be omitted. Further, even if the components have different reference numerals, those having the same name as the components already described shall have the same structure and function.

図５（ａ）に示す第１変形例の分離型複列アンギュラ玉軸受２００では、外輪２０２および内輪２０４が、玉１２０、１２２と３点接触する構成になっている。上述したように、外輪アッシィ１２４および内輪アッシィ１２６は、玉１２０、１２２の同時接触が保証されている。そのため、玉１２０、１２２と３点接触する外輪２０２および内輪２０４を採用することによって、より負荷能力が大きく剛性も高い分離型アンギュラ玉軸受２００を実現することができる。 In the separate double-row angular contact ball bearing 200 of the first modification shown in FIG. 5A, the outer ring 202 and the inner ring 204 are configured to make three-point contact with the balls 120 and 122. As described above, the outer ring assembly 124 and the inner ring assembly 126 are guaranteed to have the balls 120 and 122 in contact with each other at the same time. Therefore, by adopting the outer ring 202 and the inner ring 204 that come into contact with the balls 120 and 122 at three points, it is possible to realize a separate type angular contact ball bearing 200 having a larger load capacity and higher rigidity.

図５（ｂ）に示す第２変形例の分離型複列アンギュラ玉軸受２２０では、外輪２２２および内輪２２４が、玉１２０、１２２と４点接触する構成になっている。玉１２０、１２２と４点接触する外輪２２２および内輪２２４を採用することによっても、より負荷能力が大きく剛性も高い分離型アンギュラ玉軸受２２０を実現することができる。 In the separate double-row angular contact ball bearing 220 of the second modification shown in FIG. 5B, the outer ring 222 and the inner ring 224 are configured to come into contact with the balls 120 and 122 at four points. By adopting the outer ring 222 and the inner ring 224 that come into contact with the balls 120 and 122 at four points, it is possible to realize a separate angular contact ball bearing 220 having a larger load capacity and higher rigidity.

図５（ｃ）に示す第３変形例の分離型複列アンギュラ玉軸受２４０では、外輪２４２および内輪２４４は、玉１２０と２点で接触し、玉１２２と３点で接触する構成になっている。このように、玉１２０、１２２それぞれに応じて接触点の数が異なる外輪２４２および内輪２４４を採用することによっても、より負荷能力が大きく剛性も高い分離型アンギュラ玉軸受２４０を実現することができる。 In the separate double-row angular contact ball bearing 240 of the third modification shown in FIG. 5 (c), the outer ring 242 and the inner ring 244 are configured to contact the ball 120 at two points and contact the ball 122 at three points. There is. As described above, by adopting the outer ring 242 and the inner ring 244 having different numbers of contact points according to the balls 120 and 122, it is possible to realize a separate angular contact ball bearing 240 having a larger load capacity and higher rigidity. ..

以上のように、分離型複列アンギュラ玉軸受１００のもつ技術的思想は、多点接触の軸受としても実現可能である。これによって、負荷能力や剛性を向上させ、目的に応じた性能の軸受を提供することが可能になる。 As described above, the technical idea of the separate type double row angular contact ball bearing 100 can be realized as a multi-point contact bearing. This makes it possible to improve the load capacity and rigidity and provide bearings with performance according to the purpose.

以上、添付図面を参照しながら本発明の好適な実施例について説明したが、本発明は係る例に限定されないことは言うまでもない。当業者であれば、特許請求の範囲に記載された範疇内において、各種の変更例または修正例に想到し得ることは明らかであり、それらについても当然に本発明の技術的範囲に属するものと了解される。 Although preferred embodiments of the present invention have been described above with reference to the accompanying drawings, it goes without saying that the present invention is not limited to such examples. It is clear that a person skilled in the art can come up with various modifications or modifications within the scope of the claims, which naturally belong to the technical scope of the present invention. Understood.

本発明は、分離型複列アンギュラ玉軸受とその外輪アッシィおよび内輪アッシィに利用することができる。 The present invention can be applied to a separate type double row angular contact ball bearing and its outer ring assembly and inner ring assembly.

Ｄ１…内輪の左側の軌道径、Ｄ２…内輪の右側の軌道径、ｄ１…外輪輪の左側の軌道径、ｄ２…外輪の右側の軌道径、Ｐｅ…外輪の軌道径のピッチ、Ｐｉ…内輪の軌道径のピッチ、１００…分離型複列アンギュラ玉軸受、１０２…差動装置、１０４…アンギュラ玉軸受、１０６…ピニオン軸、１０８…リングギヤ、１１０…ピニオンギヤ、１１２…フランジ、１１４…ハウジング、１１６…外輪、１１８…内輪、１２０…外輪アッシィの玉、１２２…内輪アッシィの玉、１２４…外輪アッシィ、１２６…内輪アッシィ、１２８…外輪アッシィの保持器、１３０…外輪の左側の軌道溝、１３２…外輪の右側の軌道溝、１３４…外輪のカウンタボア形状、１３６…内輪アッシィの保持器、１３８…内輪の左側の軌道溝、１４０…内輪の右側の軌道溝、１４２…内輪のカウンタボア形状、１４４…基準内輪、１４６…内輪、１４８…左側の軌道面、１４９…右側の軌道面、１５０…基準内輪の玉、１５２…任意の玉、１５４…軸受、１６０…基準外輪、１６２…外輪、１６４…左側の軌道面、１６６…右側の軌道面、１６８…基準外輪の玉、１７０…任意の玉、１７２…軸受、２００…第１変形例の分離型複列アンギュラ玉軸受、２０２…外輪、２０４…内輪、２２０…第２変形例の分離型複列アンギュラ玉軸受、２２２…外輪、２２４…内輪、２４０…第２変形例の分離型複列アンギュラ玉軸受、２４２…外輪、２４４…内輪、Ｐｉ…ピッチ D1 ... the raceway diameter on the left side of the inner ring, D2 ... the raceway diameter on the right side of the inner ring, d1 ... the raceway diameter on the left side of the outer ring ring, d2 ... the raceway diameter on the right side of the outer ring, Pe ... the pitch of the raceway diameter of the outer ring, Pi ... Track diameter pitch, 100 ... Separable double row angular contact ball bearings, 102 ... Differential device, 104 ... Angular contact ball bearings, 106 ... Pinion shaft, 108 ... Ring gear, 110 ... Pinion gear, 112 ... Flange, 114 ... Housing, 116 ... Outer ring, 118 ... Inner ring, 120 ... Outer ring assy ball, 122 ... Inner ring assy ball, 124 ... Outer ring assy, 126 ... Inner ring assy, 128 ... Outer ring assy cage, 130 ... Outer ring left track groove, 132 ... Outer ring Right side bearing groove, 134 ... Outer ring counterbore shape, 136 ... Inner ring assembly cage, 138 ... Inner ring left side bearing groove, 140 ... Inner ring right side raceway groove, 142 ... Inner ring counterbore shape, 144 ... Reference inner ring, 146 ... Inner ring, 148 ... Left track surface, 149 ... Right track surface, 150 ... Reference inner ring ball, 152 ... Arbitrary ball, 154 ... Bearing, 160 ... Reference outer ring, 162 ... Outer ring, 164 ... Left side Raceway surface 166 ... Right side raceway surface 168 ... Reference outer ring ball, 170 ... Arbitrary ball, 172 ... Bearing, 200 ... Separated double row angular contact ball bearing of the first modification, 202 ... Outer ring, 204 ... Inner ring , 220 ... Separated double row angular contact ball bearings of the second modification, 222 ... Outer ring, 224 ... Inner ring, 240 ... Separated double row angular contact ball bearings of the second modification, 242 ... Outer ring, 244 ... Inner ring, Pi ... Pitch

Claims (3)

外輪と内輪と２列の玉とを備えた分離型複列アンギュラ玉軸受において、
前記外輪は２列の軌道溝のうち一方側の軌道溝が肩を落としたカウンタボア形状であり、
前記内輪は２列の軌道溝のうち他方側の軌道溝が肩を落としたカウンタボア形状であり、
前記外輪と前記カウンタボアの形成されていない軌道溝に保持された玉の列とを含む外輪アッシィが形成され、
前記内輪と前記カウンタボアの形成されていない軌道溝に保持された玉の列とを含む内輪アッシィが形成されていて、
前記外輪アッシィの玉は、称呼寸法からなる理想的な形状の内輪アッシィに対して所定の組幅精度になる寸法のものであり、
前記内輪アッシィの玉は、称呼寸法からなる理想的な形状の外輪アッシィに対して前記所定の組幅精度になる寸法のものであって、
前記外輪アッシィは特定の前記内輪アッシィだけでなく他の前記内輪アッシィとも互換性を有し、
前記内輪アッシィは特定の前記外輪アッシィだけでなく他の前記外輪アッシィとも互換性を有することを特徴とする分離型複列アンギュラ玉軸受。 In a separate double-row angular contact ball bearing with an outer ring, an inner ring and two rows of balls.
The outer ring has a counterbore shape in which the raceway groove on one side of the two rows of raceway grooves has a shoulder dropped.
The inner ring has a counterbore shape in which the raceway groove on the other side of the two rows of raceway grooves has a shoulder dropped.
An outer ring assembly is formed that includes the outer ring and a row of balls held in a raceway groove in which the counterbore is not formed.
An inner ring assembly is formed that includes the inner ring and a row of balls held in a raceway groove in which the counterbore is not formed.
The ball of the outer ring assembly has a size having a predetermined assembly width accuracy with respect to the inner ring assembly having an ideal shape having a nominal size.
The ball of the inner ring assembly has a size having the predetermined assembly width accuracy with respect to the outer ring assembly having an ideal shape having the nominal size.
The outer ring assembly is compatible not only with the specific inner ring assembly but also with other inner ring assemblies.
The inner ring assembly is a separate type double row angular contact ball bearing characterized in that it is compatible not only with the specific outer ring assembly but also with other outer ring assemblies. 所定の内輪アッシィと分離可能に組み合されて分離型複列アンギュラ玉軸受となる外輪アッシィにおいて、
外輪の２列の軌道溝のうち一方側の軌道溝が肩を落としたカウンタボア形状であり、
前記外輪の前記カウンタボアの形成されていない軌道溝に玉の列が保持されていて、
前記玉は、称呼寸法からなる理想的な形状の内輪アッシィに対して所定の組幅精度になる寸法のものであって、
前記内輪アッシィは、内輪の２列の軌道溝のうち他方側の軌道溝が肩を落としたカウンタボア形状であり、前記内輪の前記カウンタボアの形成されていない軌道溝に玉の列が保持されていて、前記玉は、称呼寸法からなる理想的な形状の外輪アッシィに対して所定の組幅精度になる寸法のものであって、
当該外輪アッシィは、特定の前記内輪アッシィだけでなく他の前記内輪アッシィとも互換性を有することを特徴とする外輪アッシィ。 In an outer ring assembly that is separably combined with a predetermined inner ring assembly to form a separate double-row angular contact ball bearing.
Of the two rows of raceway grooves on the outer ring, the raceway groove on one side has a counterbore shape with the shoulder dropped.
A row of balls is held in the raceway groove of the outer ring in which the counter bore is not formed.
The ball has a size having a predetermined assembly width accuracy with respect to an inner ring assembly having an ideal shape having a nominal size.
The inner ring assembly has a counterbore shape in which the raceway groove on the other side of the two rows of raceway grooves of the inner ring has a shoulder dropped, and a row of balls is held in the raceway groove in which the counterbore of the inner ring is not formed. The ball has a size having a predetermined assembly width accuracy with respect to an ideally shaped outer ring assembly having a nominal size.
The outer ring assembly is characterized in that it is compatible not only with the specific inner ring assembly but also with other inner ring assemblies. 所定の外輪アッシィと分離可能に組み合されて分離型複列アンギュラ玉軸受となる内輪アッシィにおいて、
内輪の２列の軌道溝のうち一方側の軌道溝が肩を落としたカウンタボア形状であり、
前記内輪の前記カウンタボアの形成されていない軌道溝に玉の列が保持されていて、
前記玉は、称呼寸法からなる理想的な形状の外輪アッシィに対して所定の組幅精度になる寸法のものであって、
前記外輪アッシィは、外輪の２列の軌道溝のうち他方側の軌道溝が肩を落としたカウンタボア形状であり、前記外輪の前記カウンタボアの形成されていない軌道溝に玉の列が保持されていて、前記玉は、称呼寸法からなる理想的な形状の内輪アッシィに対して所定の組幅精度になる寸法のものであって、
当該内輪アッシィは、特定の前記外輪アッシィだけでなく他の前記外輪アッシィとも互換性を有することを特徴とする内輪アッシィ。 In an inner ring assembly that is separably combined with a predetermined outer ring assembly to form a separate double-row angular contact ball bearing.
Of the two rows of raceway grooves on the inner ring, the raceway groove on one side has a counterbore shape with the shoulder dropped.
A row of balls is held in a raceway groove in which the counter bore is not formed in the inner ring.
The ball has a size having a predetermined assembly width accuracy with respect to an outer ring assembly having an ideal shape having a nominal size.
The outer ring assembly has a counterbore shape in which the raceway groove on the other side of the two rows of raceway grooves of the outer ring has a shoulder dropped, and a row of balls is held in the raceway groove in which the counterbore of the outer ring is not formed. The ball has a size having a predetermined assembly width accuracy with respect to an inner ring assembly having an ideal shape having a nominal size.
The inner ring assembly is characterized in that it is compatible not only with the specific outer ring assembly but also with other outer ring assemblies.
JP2016238511A 2016-12-08 2016-12-08 Separate double row angular contact ball bearings, outer ring assembly and inner ring assembly Active JP7057485B2 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP2016238511A JP7057485B2 (en) 2016-12-08 2016-12-08 Separate double row angular contact ball bearings, outer ring assembly and inner ring assembly
KR1020170130375A KR20180065873A (en) 2016-12-08 2017-10-11 Separable double row angular ball bearing, outer race assembly and inner race assembly

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2016238511A JP7057485B2 (en) 2016-12-08 2016-12-08 Separate double row angular contact ball bearings, outer ring assembly and inner ring assembly

Publications (2)

Publication Number Publication Date
JP2018096395A JP2018096395A (en) 2018-06-21
JP7057485B2 true JP7057485B2 (en) 2022-04-20

Family

ID=62633673

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2016238511A Active JP7057485B2 (en) 2016-12-08 2016-12-08 Separate double row angular contact ball bearings, outer ring assembly and inner ring assembly

Country Status (2)

Country Link
JP (1) JP7057485B2 (en)
KR (1) KR20180065873A (en)

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2005147372A (en) 2003-11-20 2005-06-09 Nachi Fujikoshi Corp Tandem duplex angular ball bearing and separation method thereof

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0566327U (en) * 1992-02-13 1993-09-03 株式会社不二越 Parallel combination type double row angular contact ball bearing
DE19839481C2 (en) 1998-08-29 2003-06-05 Ina Schaeffler Kg Transfer case for a motor vehicle

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2005147372A (en) 2003-11-20 2005-06-09 Nachi Fujikoshi Corp Tandem duplex angular ball bearing and separation method thereof

Also Published As

Publication number Publication date
KR20180065873A (en) 2018-06-18
JP2018096395A (en) 2018-06-21

Similar Documents

Publication Publication Date Title
JP5312514B2 (en) Crossed roller bearing
US9097333B2 (en) Wear compensation device for a gear set with temporary angular pre-indexing, and associated mounting method
JP2013015200A (en) Conical roller bearing
JP2019074214A (en) Angular ball bearing and its manufacturing method
US20130283940A1 (en) Wear compensation device for a gear set and associated mounting method
GB2528042A (en) Cage of a roller bearing and method for producing such a cage
JP7057485B2 (en) Separate double row angular contact ball bearings, outer ring assembly and inner ring assembly
JP6432338B2 (en) Ball bearing for wave reducer
WO2015053351A1 (en) Roller bearing cage, assembly and production method therefor, and roller bearing
JP2014088928A (en) Assembly method of conical roller bearing
KR20140024008A (en) Two-stage cross roller bearing
JP2014137097A (en) Rolling bearing, and bearing unit
JP2023072404A (en) roller bearing
JP2018194014A (en) Method of manufacturing cylindrical roller bearing and holder
WO2017168611A1 (en) Double-row cylindrical roller bearing
CN110566574A (en) separated type double-row angular contact ball bearing, outer ring assembly and inner ring assembly
JP2012149703A (en) Self-alignment roller bearing
KR20150146407A (en) Tool for assembling an axial rolling bearing
JP6379079B2 (en) Radial roller bearings
JP2007205455A (en) Rolling bearing
WO2018055991A1 (en) Double-row ball bearing
WO2017110907A1 (en) Roller bearing
WO2023145047A1 (en) Tapered roller bearing and retainer
JP2014231900A (en) Roller bearing
JP2013096473A (en) Double row bearing

Legal Events

Date Code Title Description
RD03 Notification of appointment of power of attorney

Free format text: JAPANESE INTERMEDIATE CODE: A7423

Effective date: 20180612

A621 Written request for application examination

Free format text: JAPANESE INTERMEDIATE CODE: A621

Effective date: 20190315

A977 Report on retrieval

Free format text: JAPANESE INTERMEDIATE CODE: A971007

Effective date: 20200110

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20200128

A521 Request for written amendment filed

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20200323

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20200818

A521 Request for written amendment filed

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20201019

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20210309

A521 Request for written amendment filed

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20210506

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20211005

A521 Request for written amendment filed

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20211206

TRDD Decision of grant or rejection written
A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

Effective date: 20220308

A61 First payment of annual fees (during grant procedure)

Free format text: JAPANESE INTERMEDIATE CODE: A61

Effective date: 20220321

R150 Certificate of patent or registration of utility model

Ref document number: 7057485

Country of ref document: JP

Free format text: JAPANESE INTERMEDIATE CODE: R150