JP2015105670A - Rolling bearing, and power transmission device equipped with the same - Google Patents

Rolling bearing, and power transmission device equipped with the same Download PDF

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JP2015105670A
JP2015105670A JP2013246476A JP2013246476A JP2015105670A JP 2015105670 A JP2015105670 A JP 2015105670A JP 2013246476 A JP2013246476 A JP 2013246476A JP 2013246476 A JP2013246476 A JP 2013246476A JP 2015105670 A JP2015105670 A JP 2015105670A
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rolling bearing
flange portion
housing
bolt insertion
power transmission
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Japanese (ja)
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健 岩脇
Takeshi Iwawaki
健 岩脇
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JTEKT Corp
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JTEKT Corp
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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
    • 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
    • F16C19/185—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 with two raceways provided integrally on a part other than a race ring, e.g. a shaft or housing
    • 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
    • F16C33/583—Details of specific parts of races
    • F16C33/586—Details of specific parts of races outside the space between the races, e.g. end faces or bore of inner ring
    • 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
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F16C2240/60—Thickness, e.g. thickness of coatings
    • 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
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F16C2240/70—Diameters; Radii

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

Abstract

PROBLEM TO BE SOLVED: To provide a rolling bearing capable of effectively improving the hardness of a flange portion while suppressing the weight increase of the rolling bearing.SOLUTION: A rolling bearing includes: a pair of bearing rings 21 opposite in a diametrical direction; a rolling body provided between the pair of the bearing rings so as to roll; and a flange portion 25 projecting outward in a diametrical direction from one bearing ring 21, formed with a plurality of bolt insertion holes at intervals in a circumferential direction, and fixed to a housing 11 by bolts 26 inserted in the bolt insertion holes. The flange portion 25 have a plurality of areas R1 and R2 whose thickness dimensions in an axial direction are different in the circumferential direction.

Description

本発明は、転がり軸受、及びこれを備えた動力伝達装置に関するものである。   The present invention relates to a rolling bearing and a power transmission device including the same.

自動車等の車両に設けられた動力伝達装置、例えばトランスミッションやトランスファーには、ハウジング内で動力伝達軸を支持するために転がり軸受が用いられている（例えば、下記特許文献１及び２参照）。この転がり軸受は、径方向に対向する外輪及び内輪と、これらの間に転動可能に配置された転動体とを備えている。外輪には、ボルト挿通孔が形成されたフランジ部が径方向外方へ突設され、このフランジ部が、ボルト挿通孔に挿通されたボルトによってハウジングに固定されている。   Rolling bearings are used for power transmission devices provided in vehicles such as automobiles, such as transmissions and transfers, to support a power transmission shaft within a housing (see, for example, Patent Documents 1 and 2 below). The rolling bearing includes an outer ring and an inner ring that are opposed to each other in the radial direction, and a rolling element that is arranged to be able to roll therebetween. A flange portion in which a bolt insertion hole is formed protrudes radially outward from the outer ring, and this flange portion is fixed to the housing by a bolt inserted into the bolt insertion hole.

特開２００９−１１５３２３号公報JP 2009-115323 A 特開２００７−１９２３０１号公報JP 2007-192301 A

上記のような転がり軸受において、外輪は、ハウジング内に形成された開口に遊嵌されており、実質的にフランジ部のみがハウジングに固定されている。したがって、動力伝達軸からの負荷は、主としてフランジ部が受けることになる。そのため、フランジ部は、動力伝達軸からの負荷に十分に耐えうる強度を備える必要がある。
しかし、フランジ部の強度を高めるために単にフランジ部を分厚くしたり大きくしたりするだけであると、転がり軸受の重量が増大する。近年、トランスミッション等の動力伝達装置は、ハウジング等の構成部品をアルミ合金で形成すること等によって軽量化を図っているが、前述のような転がり軸受の重量増は、動力伝達装置の軽量化を妨げる要因となるため、好ましくない。 In the rolling bearing as described above, the outer ring is loosely fitted in an opening formed in the housing, and substantially only the flange portion is fixed to the housing. Therefore, the load from the power transmission shaft is mainly received by the flange portion. Therefore, the flange portion needs to have a strength that can sufficiently withstand a load from the power transmission shaft.
However, if the flange portion is simply made thicker or larger in order to increase the strength of the flange portion, the weight of the rolling bearing increases. In recent years, power transmission devices such as transmissions have been made lighter by forming components such as housings from aluminum alloys. However, the increase in the weight of rolling bearings as described above has led to a reduction in the weight of power transmission devices. It is not preferable because it becomes a hindering factor.

本発明は、転がり軸受の重量増を抑制しつつ、効果的にフランジ部の強度を高めることが可能な転がり軸受及びこれを備えた動力伝達装置を提供することを目的とする。   An object of the present invention is to provide a rolling bearing capable of effectively increasing the strength of the flange portion while suppressing an increase in the weight of the rolling bearing and a power transmission device including the rolling bearing.

（１）本発明の第１の観点に係る転がり軸受は、径方向に対向する一対の軌道輪と、一対の軌道輪の間に転動可能に設けられた転動体と、一方の軌道輪から径方向外方に突出し、複数のボルト挿通孔が周方向に間隔をあけて形成されるとともに当該ボルト挿通孔に挿入されたボルトによってハウジングに固定されるフランジ部と、を備えている転がり軸受であって、前記フランジ部は、周方向に関して、軸方向の厚さ寸法が異なる複数の領域を有している。   (1) A rolling bearing according to the first aspect of the present invention includes a pair of raceways opposed in the radial direction, a rolling element provided between the pair of raceways so as to be capable of rolling, and one raceway. A rolling bearing that protrudes radially outward and has a plurality of bolt insertion holes formed at intervals in the circumferential direction and fixed to the housing by bolts inserted into the bolt insertion holes. And the said flange part has a several area | region from which the thickness dimension of an axial direction differs regarding the circumferential direction.

動力伝達軸を支持する転がり軸受は、周方向の特定の位相に集中して負荷が付与される場合がある。例えば、トランスミッション等の動力伝達装置においては、転がり軸受によって支持される動力伝達軸に歯車が設けられ、この歯車と他の歯車との噛み合いによって動力伝達軸に回転動力が伝達される。歯車は周方向の一点で力を受けるため、動力伝達軸には回転方向の負荷だけでなく特定のラジアル方向の負荷も受け、この負荷は動力伝達軸を介して転がり軸受の特定の位相に付与される。
本発明は、ハウジングに固定されるフランジ部が、周方向に関して、軸方向の厚さ寸法が異なる複数の領域を有している。そのため、上記のように動力伝達軸からの負荷が特定の位相に集中する場合には、その位相に対応させて軸方向の厚さ寸法を大きくすることができ、逆に、負荷が小さい位相に対応させて軸方向の厚さ寸法を小さくすることができる。これにより、転がり軸受の重量増を抑制しつつ、負荷の分布に応じて効果的にフランジ部の強度を高めることができる。 A rolling bearing that supports a power transmission shaft may be applied with a load concentrated on a specific phase in the circumferential direction. For example, in a power transmission device such as a transmission, a gear is provided on a power transmission shaft supported by a rolling bearing, and rotational power is transmitted to the power transmission shaft by meshing the gear with another gear. Since the gear receives a force at one point in the circumferential direction, the power transmission shaft receives not only a rotational load but also a specific radial load, and this load is applied to a specific phase of the rolling bearing via the power transmission shaft. Is done.
In the present invention, the flange portion fixed to the housing has a plurality of regions with different axial thickness dimensions in the circumferential direction. Therefore, when the load from the power transmission shaft is concentrated in a specific phase as described above, the thickness dimension in the axial direction can be increased corresponding to the phase, and conversely, the load is reduced in a phase. Correspondingly, the axial thickness dimension can be reduced. Thereby, the intensity | strength of a flange part can be effectively raised according to distribution of load, suppressing the weight increase of a rolling bearing.

（２）前記フランジ部は、軸方向の一方の側面が平坦面に形成され、他方の側面が前記厚さ寸法の相違により凹凸形状に形成されていてもよい。
（３）また、前記フランジ部は、ハウジングに当接する側面が凹凸形状に形成されていることが好ましい。この場合、フランジ部に対向するハウジング側の側面も、フランジ部に合わせた凹凸形状に形成されていれば、両者の位置合わせを容易に行え、凹凸形状の段部同士を周方向に当接させれば、周方向の廻り止めも行うことができる。 (2) The flange portion may be formed such that one side surface in the axial direction is a flat surface, and the other side surface is formed in a concavo-convex shape due to the difference in the thickness dimension.
(3) Moreover, it is preferable that the said flange part is formed in the uneven | corrugated shape at the side surface contact | abutted to a housing. In this case, if the side surface on the housing side facing the flange portion is also formed in a concavo-convex shape that matches the flange portion, both can be easily aligned and the concavo-convex step portions are brought into contact with each other in the circumferential direction. If so, it is possible to prevent the circumferential rotation.

（４）本発明の第２の観点に係る転がり軸受は、径方向に対向する一対の軌道輪と、一対の軌道輪の間に転動可能に設けられた転動体と、一方の軌道輪から径方向外方に突出し、複数のボルト挿通孔が周方向に間隔をあけて形成されるとともに当該ボルト挿通孔に挿入されたボルトによってハウジングに固定されるフランジ部と、を備えている転がり軸受であって、前記フランジ部は、前記ボルト挿通孔が形成され前記ハウジングに直接的に取り付けられる複数の被取付部と、周方向に隣接する被取付部の間に形成される補強部とを含み、前記フランジ部は、周方向に関して、前記補強部の径方向の厚さ寸法が異なる複数の領域を有している。   (4) A rolling bearing according to a second aspect of the present invention includes a pair of raceways opposed to each other in a radial direction, a rolling element provided between the pair of raceways so as to roll, and one raceway. A rolling bearing that protrudes radially outward and has a plurality of bolt insertion holes formed at intervals in the circumferential direction and fixed to the housing by bolts inserted into the bolt insertion holes. The flange portion includes a plurality of attached portions in which the bolt insertion holes are formed and directly attached to the housing, and a reinforcing portion formed between the attached portions adjacent in the circumferential direction, The said flange part has several area | region where the thickness dimension of the radial direction of the said reinforcement part differs regarding the circumferential direction.

前述したように、動力伝達軸等の動力伝達軸を支持する転がり軸受は、周方向の特定の位相に集中して負荷が付与される場合がある。このような場合に、本発明では、動力伝達軸からの負荷が集中する位相に対応させて補強部の径方向の厚さ寸法を大きくすることができ、逆に、負荷が小さい位相に対応させて補強部の径方向の厚さ寸法を小さくすることができる。これにより、転がり軸受の重量増を抑制しつつ、負荷の分布に応じて効果的にフランジ部の強度を高めることができる。   As described above, a rolling bearing that supports a power transmission shaft such as a power transmission shaft may be applied with a load concentrated on a specific phase in the circumferential direction. In such a case, in the present invention, the thickness dimension in the radial direction of the reinforcing portion can be increased in correspondence with the phase in which the load from the power transmission shaft is concentrated. Thus, the thickness dimension in the radial direction of the reinforcing portion can be reduced. Thereby, the intensity | strength of a flange part can be effectively raised according to distribution of load, suppressing the weight increase of a rolling bearing.

（５）上記（１）〜（４）の転がり軸受において、前記ボルト挿通孔が周方向に関して不等間隔で配置されている場合、前記ボルト挿通孔の間隔が広い領域で前記厚さ寸法が小さく、狭い領域で前記厚さ寸法が大きく設定されていてもよい。
ボルト挿通孔は、フランジ部に付与される負荷の分布に合わせて形成される場合がある。すなわち、負荷の集中する位相に対応させてボルト挿通孔を集中して配置し、負荷が低い位相に対応させてボルト挿通孔の間隔を広くする場合がある。このような場合、上記構成の転がり軸受を採用することによって、負荷の集中する位相では厚さ寸法を大きくして強度の増大を図り、負荷の低い位相では厚さ寸法を小さくして重量の増大を抑制することができる。
なお、上記の「不等間隔」とは、ボルト挿通孔の全ての間隔が相互に異なっている場合や、少なくとも一つの間隔が他の間隔と異なる場合も含む。 (5) In the rolling bearings of the above (1) to (4), when the bolt insertion holes are arranged at unequal intervals in the circumferential direction, the thickness dimension is small in a region where the interval between the bolt insertion holes is wide. The thickness dimension may be set large in a narrow region.
The bolt insertion hole may be formed according to the distribution of the load applied to the flange portion. That is, the bolt insertion holes may be arranged in a concentrated manner corresponding to the phase in which the load is concentrated, and the interval between the bolt insertion holes may be increased in correspondence with the phase in which the load is low. In such a case, by adopting the rolling bearing of the above configuration, the thickness dimension is increased to increase the strength in the phase where the load is concentrated, and the thickness dimension is decreased and the weight is increased in the phase where the load is low. Can be suppressed.
In addition, said "unequal space | interval" includes the case where all the space | intervals of a bolt insertion hole are mutually different, and the case where at least 1 space | interval differs from other space | intervals.

（６）また、前記ボルト挿通孔が周方向に関して不等間隔で配置されている場合、前記ボルト挿通孔の間隔が広い領域で前記厚さ寸法が大きく、狭い領域で前記厚さ寸法が小さく設定されていてもよい。
ボルト挿通孔は、周囲の部品との位置関係で不等間隔に配置されることがあり、この場合、動力伝達軸からの負荷が集中するにも関わらず、ボルト挿通孔の間隔が広くなってしまう場合もある。このような場合には、上記構成を採用することによって、ボルト挿通孔の間隔が広い領域であっても厚さ寸法を大きくして強度を高めることができ、ボルト挿通孔の間隔が狭い領域では厚さ寸法を小さくして重量増を抑制することができる。 (6) When the bolt insertion holes are arranged at unequal intervals in the circumferential direction, the thickness dimension is set to be large in a region where the interval between the bolt insertion holes is wide, and the thickness dimension is set to be small in a narrow region. May be.
The bolt insertion holes may be arranged at unequal intervals due to the positional relationship with the surrounding parts. In this case, the distance between the bolt insertion holes becomes wide even though the load from the power transmission shaft is concentrated. Sometimes it ends up. In such a case, by adopting the above configuration, even in a region where the distance between the bolt insertion holes is wide, the thickness dimension can be increased to increase the strength, and in a region where the distance between the bolt insertion holes is small. The thickness dimension can be reduced to suppress an increase in weight.

（７）本発明の第３の観点に係る転がり軸受は、径方向に対向する一対の軌道輪と、一対の軌道輪の間に転動可能に設けられた転動体と、一方の軌道輪から径方向外方に突出し、複数のボルト挿通孔が周方向に間隔をあけて形成されるとともに当該ボルト挿通孔に挿入されたボルトによってハウジングに固定されるフランジ部と、を備えている転がり軸受であって、前記フランジ部は、前記ボルト挿通孔が形成され前記ハウジングに直接的に取り付けられる複数の被取付部と、周方向に隣接する被取付部の間のうち、少なくとも１箇所を除いて形成される補強部とを含む。   (7) A rolling bearing according to a third aspect of the present invention includes a pair of raceways opposed to each other in a radial direction, a rolling element provided between the pair of raceways so as to be capable of rolling, and one raceway. A rolling bearing that protrudes radially outward and has a plurality of bolt insertion holes formed at intervals in the circumferential direction and fixed to the housing by bolts inserted into the bolt insertion holes. And the said flange part is formed except at least one place among the some to-be-attached parts in which the said bolt insertion hole is formed and attached to the said housing directly, and the to-be-attached parts adjacent to the circumferential direction. And a reinforcing portion.

前述したように、動力伝達軸等の動力伝達軸を支持する転がり軸受は、周方向の特定の位相に集中して負荷が付与される場合がある。このような場合に、本発明では、動力伝達軸からの負荷が集中する位相に対応させて補強部を形成し、逆に、負荷が小さい位相に対応する部分には補強部を形成しないようにすることができる。これにより、転がり軸受の重量増を抑制しつつ、負荷の分布に応じて効果的にフランジ部の強度を高めることができる。   As described above, a rolling bearing that supports a power transmission shaft such as a power transmission shaft may be applied with a load concentrated on a specific phase in the circumferential direction. In such a case, in the present invention, the reinforcing portion is formed corresponding to the phase where the load from the power transmission shaft is concentrated, and conversely, the reinforcing portion is not formed in the portion corresponding to the phase where the load is small. can do. Thereby, the intensity | strength of a flange part can be effectively raised according to distribution of load, suppressing the weight increase of a rolling bearing.

（８）本発明の第４の観点に係る動力伝達装置は、上記（１）〜（７）のいずれかに記載の転がり軸受と、この転がり軸受のフランジ部が固定されるハウジングと、このハウジング内で前記転がり軸受によって回転自在に支持された動力伝達軸と、を有し、前記フランジ部は、前記動力伝達軸からの負荷の分布に応じて前記厚さ寸法の異なる領域が設定されている。   (8) A power transmission device according to a fourth aspect of the present invention includes a rolling bearing according to any one of (1) to (7), a housing to which a flange portion of the rolling bearing is fixed, and the housing A power transmission shaft that is rotatably supported by the rolling bearing, and the flange portion is set with regions having different thickness dimensions according to a load distribution from the power transmission shaft. .

（９）本発明の第５の観点に係る動力伝達装置は、上記（３）に記載の転がり軸受と、この転がり軸受のフランジ部が固定されるハウジングと、このハウジング内で前記転がり軸受によって回転自在に支持された動力伝達軸と、を有し、前記フランジ部に当接する前記ハウジングの側面に、当該フランジ部の凸部に対応する凹部と、当該フランジ部の凹部に対応する凸部とが形成されている。
このように、フランジ部の凹凸形状に対応する凹凸形状をハウジングに形成することで、フランジ部をハウジングに取り付けるときの周方向の位置合わせを容易に行うことができる。 (9) A power transmission device according to a fifth aspect of the present invention includes a rolling bearing according to (3) above, a housing to which a flange portion of the rolling bearing is fixed, and rotation in the housing by the rolling bearing. A power transmission shaft that is freely supported, and a concave portion corresponding to the convex portion of the flange portion and a convex portion corresponding to the concave portion of the flange portion on a side surface of the housing that contacts the flange portion. Is formed.
In this way, by forming the concave and convex shape corresponding to the concave and convex shape of the flange portion in the housing, it is possible to easily align the circumferential direction when the flange portion is attached to the housing.

（１０）この動力伝達装置の場合、前記フランジ部の側面における凹凸の境界に位置する段部と、前記ハウジングの側面における凹凸の境界に位置する段部とが、互いに周方向に対向して当接していることが好ましい。
このような構成によって、フランジ部の周方向の廻り止めを行うことができる。 (10) In the case of this power transmission device, the step portion located at the uneven boundary on the side surface of the flange portion and the step portion located at the uneven boundary on the side surface of the housing are opposed to each other in the circumferential direction. It is preferable to contact.
With such a configuration, it is possible to prevent the flange portion from rotating in the circumferential direction.

本発明によれば、転がり軸受の重量増を抑制しつつ、効果的にフランジ部の強度を高めることができる。   ADVANTAGE OF THE INVENTION According to this invention, the intensity | strength of a flange part can be raised effectively, suppressing the weight increase of a rolling bearing.

本発明の第１の実施形態に係る動力伝達装置の一部の縦断面図である。It is a longitudinal section of some power transmission devices concerning a 1st embodiment of the present invention. 動力伝達装置のハウジング、動力伝達軸、及び転がり軸受の平面図である。It is a top view of the housing of a power transmission device, a power transmission shaft, and a rolling bearing. 転がり軸受の外輪を示す斜視図である。It is a perspective view which shows the outer ring | wheel of a rolling bearing. 転がり軸受の外輪を示す正面図である。It is a front view which shows the outer ring | wheel of a rolling bearing. 転がり軸受の外輪を示す側面図である。It is a side view which shows the outer ring | wheel of a rolling bearing. 本発明の第２の実施形態に係る動力伝達装置のハウジング、動力伝達軸、及び転がり軸受の平面図である。It is a top view of the housing of the power transmission device which concerns on the 2nd Embodiment of this invention, a power transmission shaft, and a rolling bearing. 転がり軸受の外輪を示す斜視図である。It is a perspective view which shows the outer ring | wheel of a rolling bearing. 本発明の第３の実施形態に係る動力伝達装置の転がり軸受の外輪を示す側面図である。It is a side view which shows the outer ring | wheel of the rolling bearing of the power transmission device which concerns on the 3rd Embodiment of this invention. 本発明の第４の実施形態に係る動力伝達装置の転がり軸受の外輪を示す側面図である。It is a side view which shows the outer ring | wheel of the rolling bearing of the power transmission device which concerns on the 4th Embodiment of this invention. 本発明の第５の実施形態に係る動力伝達装置の転がり軸受の外輪を示す側面図である。It is a side view which shows the outer ring | wheel of the rolling bearing of the power transmission device which concerns on the 5th Embodiment of this invention.

以下、図面を参照しつつ本発明の実施形態を説明する。
図１は、本発明の第１の実施形態に係る動力伝達装置の一部の縦断面図である。図２は、動力伝達装置のハウジング、動力伝達軸、及び転がり軸受の平面図である。
図１に示されるように、本実施形態の動力伝達装置１０は、例えば自動車に搭載されるトランスミッションやトランスファーであり、ハウジング１１と、このハウジング１１に固定される転がり軸受１２と、ハウジング１１内で転がり軸受１２によって回転可能に支持される動力伝達軸１３とを備えている。なお、図示はしていないが、動力伝達軸１３には歯車やスプロケット、プーリ等の動力伝達部材が設けられ、この動力伝達部材を介して回転動力の伝達が行われる。 Hereinafter, embodiments of the present invention will be described with reference to the drawings.
FIG. 1 is a longitudinal sectional view of a part of a power transmission device according to a first embodiment of the present invention. FIG. 2 is a plan view of the housing, the power transmission shaft, and the rolling bearing of the power transmission device.
As shown in FIG. 1, a power transmission device 10 according to the present embodiment is a transmission or a transfer mounted on an automobile, for example, and includes a housing 11, a rolling bearing 12 fixed to the housing 11, and a housing 11. And a power transmission shaft 13 that is rotatably supported by the rolling bearing 12. Although not shown, the power transmission shaft 13 is provided with a power transmission member such as a gear, a sprocket, and a pulley, and rotational power is transmitted through the power transmission member.

転がり軸受１２は、複列のアンギュラ玉軸受であり、動力伝達装置１０のハウジング１１に取り付けられる外輪（軌道輪）２１と、動力伝達軸１３に取り付けられる内輪（軌道輪）２２と、外輪２１及び内輪２２の間に軸方向に関して２列に配列された複数の玉（転動体）２３と、各列の玉２３の周方向の間隔を保持する保持器２４とを備えている。   The rolling bearing 12 is a double-row angular ball bearing, and includes an outer ring (orbital ring) 21 attached to the housing 11 of the power transmission device 10, an inner ring (orbital ring) 22 attached to the power transmission shaft 13, an outer ring 21, and A plurality of balls (rolling elements) 23 arranged in two rows in the axial direction between the inner rings 22, and a cage 24 that holds a circumferential interval between the balls 23 in each row.

外輪２１は、内周に２列の軌道面を有しており、外周の軸方向一端部には、径方向外方に突出するフランジ部２５が設けられている。そして、このフランジ部２５が固定ボルト２６によってハウジング１１に固定されている。また、外輪２１は、ハウジング１１に形成された開口部１１ａに隙間をあけて嵌合されている。外輪２１の外周面には、周溝２１ａが形成されており、この周溝２１ａに嵌合されたＯリング２８によって、ハウジング１１と外輪２１との間がシールされている。   The outer ring 21 has two rows of raceway surfaces on the inner periphery, and a flange portion 25 that protrudes radially outward is provided at one axial end portion of the outer periphery. The flange portion 25 is fixed to the housing 11 by a fixing bolt 26. The outer ring 21 is fitted in an opening 11 a formed in the housing 11 with a gap. A circumferential groove 21 a is formed on the outer circumferential surface of the outer ring 21, and the space between the housing 11 and the outer ring 21 is sealed by an O-ring 28 fitted in the circumferential groove 21 a.

内輪２２は、各列の玉２３に対応して軸方向に並べて設けられた１対の内輪構成部材２２Ａ，２２Ｂによって構成されている。各内輪構成部材２２Ａ，２２Ｂの外周には、単列の軌道面が形成されている。
外輪２１の内周面の軸方向両端部と、内輪２２の外周面の軸方向両端部との間には、シール部材２７が設けられており、このシール部材２７によって外輪２１及び内輪２２の間が密閉されている。
各保持器２４は、金属製、又は合成樹脂製であり、玉２３を収容するためのポケットが周方向に複数形成されている。 The inner ring 22 is constituted by a pair of inner ring constituting members 22A and 22B provided in line in the axial direction corresponding to the balls 23 in each row. A single-row track surface is formed on the outer circumference of each of the inner ring constituent members 22A and 22B.
Seal members 27 are provided between both axial end portions of the inner peripheral surface of the outer ring 21 and both axial end portions of the outer peripheral surface of the inner ring 22, and the seal member 27 provides a space between the outer ring 21 and the inner ring 22. Is sealed.
Each cage 24 is made of metal or synthetic resin, and a plurality of pockets for accommodating the balls 23 are formed in the circumferential direction.

次に、外輪２１のフランジ部２５について詳細に説明する。
図３は、転がり軸受１２の外輪２１を示す斜視図、図４は、同じく正面図、図５は、同じく側面図である。
本実施形態の外輪２１のフランジ部２５には、４個のボルト挿通孔３１が形成されている。そして、この４個のボルト挿通孔３１に挿通された固定ボルト２６を、ハウジング１１に締結することによって、外輪２１がハウジング１１に取り付けられている。外輪２１の外周面は、ハウジング１１の開口部１１ａに遊嵌されているため、外輪２１は実質的にフランジ部２５のみによってハウジング１１に固定されている。 Next, the flange portion 25 of the outer ring 21 will be described in detail.
3 is a perspective view showing the outer ring 21 of the rolling bearing 12, FIG. 4 is a front view, and FIG. 5 is a side view.
Four bolt insertion holes 31 are formed in the flange portion 25 of the outer ring 21 of the present embodiment. The outer ring 21 is attached to the housing 11 by fastening the fixing bolts 26 inserted through the four bolt insertion holes 31 to the housing 11. Since the outer peripheral surface of the outer ring 21 is loosely fitted in the opening 11 a of the housing 11, the outer ring 21 is substantially fixed to the housing 11 only by the flange portion 25.

フランジ部２５は、ボルト挿通孔３１が形成されることによって、ハウジング１１に直接的に取り付けられる被取付部３２と、周方向に隣接する被取付部３２の間に位置し、専ら補強として機能する補強部３３とを有している。被取付部３２は、ボルト挿通孔３１を形成することができる程度の大きさで外輪２１から径方向外方へ突出している。一方、補強部３３は、被取付部３２よりも径方向への突出量が小さく、ほぼ一定の径方向の厚さ寸法ｔ３で形成されている。被取付部３２と補強部３３との境界部は、Ｒ状に滑らかに連なっている。   The flange portion 25 is located between the attached portion 32 that is directly attached to the housing 11 and the attached portion 32 that is adjacent in the circumferential direction by forming the bolt insertion hole 31, and functions exclusively as a reinforcement. And a reinforcing portion 33. The attached portion 32 protrudes radially outward from the outer ring 21 with such a size that the bolt insertion hole 31 can be formed. On the other hand, the reinforcing portion 33 has a smaller amount of protrusion in the radial direction than the attached portion 32, and is formed with a substantially constant radial thickness dimension t3. The boundary portion between the mounted portion 32 and the reinforcing portion 33 is smoothly connected in an R shape.

本実施形態では、複数のボルト挿通孔３１は周方向に関して不等間隔で配置されている。そのため、ボルト挿通孔３１が形成された被取付部３２についても不等間隔で設けられている。また、補強部３３の周方向の長さも、不均一となっている。
図４及び図５に示されるように、フランジ部２５は、周方向に関して、軸方向の厚さ寸法が異なる２つの領域Ｒ１，Ｒ２を有している。具体的に、軸方向の厚さ寸法ｔ１が大きい第１の領域Ｒ１と、軸方向の厚さ寸法ｔ２が小さい第２の領域Ｒ２とを有している。また、第１の領域Ｒ１と第２の領域Ｒ２とは、それぞれ２個の被取付部３２を含み、第１の領域Ｒ１と第２の領域Ｒ２との境界が補強部３３の途中に配置されている。各領域Ｒ１，Ｒ２において、それぞれ被取付部３２と補強部３３の軸方向の厚さ寸法は同一とされている。以下の説明では、フランジ部２５の第１の領域Ｒ１に配置される部分を厚肉部２５Ａということがあり、第２の領域Ｒ２に配置される部分を薄肉部２５Ｂということがある。 In the present embodiment, the plurality of bolt insertion holes 31 are arranged at unequal intervals in the circumferential direction. For this reason, the mounted portions 32 in which the bolt insertion holes 31 are formed are also provided at unequal intervals. Further, the circumferential length of the reinforcing portion 33 is also not uniform.
As shown in FIGS. 4 and 5, the flange portion 25 has two regions R <b> 1 and R <b> 2 having different axial thickness dimensions with respect to the circumferential direction. Specifically, it has a first region R1 having a large axial thickness dimension t1 and a second region R2 having a small axial thickness dimension t2. Each of the first region R1 and the second region R2 includes two attached portions 32, and the boundary between the first region R1 and the second region R2 is disposed in the middle of the reinforcing portion 33. ing. In each area | region R1, R2, the thickness dimension of the axial direction of the to-be-attached part 32 and the reinforcement part 33 is made the same, respectively. In the following description, the portion disposed in the first region R1 of the flange portion 25 may be referred to as a thick portion 25A, and the portion disposed in the second region R2 may be referred to as a thin portion 25B.

図２に示されるように、フランジ部２５は、軸方向の一側面（図２における右側の側面）が平坦な面に形成されている。これに対して、フランジ部２５の軸方向の他側面（図２における左側の側面）２５ｂ１，２５ｂ２は、第１，第２の領域Ｒ１，Ｒ２の軸方向の厚さ寸法ｔ１，ｔ２の相違により、凹凸形状に形成されている。すなわち、当該側面２５ｂ１，２５ｂ２は、第１の領域Ｒ１（厚肉部２５Ａ）において凸状となり、第２の領域Ｒ２（薄肉部２５Ｂ）において凹状となっている。そして、本実施形態では、凹凸形状のフランジ部２５の側面２５ｂ１，２５ｂ２が、ハウジング１１の側面１１ｂ１，１１ｂ２に当接するようになっている。   As shown in FIG. 2, the flange portion 25 is formed such that one side surface in the axial direction (the right side surface in FIG. 2) is flat. On the other hand, the other axial side surface (left side surface in FIG. 2) 25b1 and 25b2 of the flange portion 25 is caused by the difference in the axial thickness dimensions t1 and t2 of the first and second regions R1 and R2. It is formed in an uneven shape. That is, the side surfaces 25b1 and 25b2 are convex in the first region R1 (thick portion 25A) and concave in the second region R2 (thin portion 25B). In the present embodiment, the side surfaces 25 b 1 and 25 b 2 of the concave and convex flange portion 25 come into contact with the side surfaces 11 b 1 and 11 b 2 of the housing 11.

フランジ部２５に当接するハウジング１１の側面（当接面）１１ｂ１，１１ｂ２は、フランジ部２５の凹凸形状に合わせた凹凸形状に形成されている。すなわち、当該当接面１１ｂ１，１１ｂ２は、フランジ部２５の第１の領域Ｒ１に対応する部分１１ｂ１が凹状となり、第２の領域Ｒ２に対応する部分１１ｂ２が凸状となっている。
また、フランジ部２５の第１の領域Ｒ１と第２の領域Ｒ２との境界に位置する段部２５ｃは、軸方向に沿った面に形成されている。これに対してハウジング１１の当接面１１ｂ１，１１ｂ２における凸状の部分１１ｂ２と凹状の部分１１ｂ１との境界に位置する段部１１ｃも軸方向に沿った面に形成されている。そして、フランジ部２５側の段部２５ｃとハウジング１１側の段部１１ｃとは、周方向に対向し、互いに当接している。 The side surfaces (contact surfaces) 11b1 and 11b2 of the housing 11 that abut on the flange portion 25 are formed in an uneven shape that matches the uneven shape of the flange portion 25. That is, the contact surfaces 11b1 and 11b2 have a concave portion 11b1 corresponding to the first region R1 of the flange portion 25 and a convex portion 11b2 corresponding to the second region R2.
Moreover, the step part 25c located in the boundary of 1st area | region R1 and 2nd area | region R2 of the flange part 25 is formed in the surface along an axial direction. On the other hand, the step part 11c located in the boundary of the convex part 11b2 and the concave part 11b1 in contact surface 11b1, 11b2 of the housing 11 is also formed in the surface along an axial direction. The step portion 25c on the flange portion 25 side and the step portion 11c on the housing 11 side face each other in the circumferential direction and are in contact with each other.

本実施形態において、動力伝達軸１３には、歯車（ギヤ）やスプロケット、プーリ等の動力伝達部材が取り付けられ、この動力伝達部材を介して回転動力が伝達される。そして、例えば、動力伝達部材が歯車である場合には、この歯車は周方向の１点で他の歯車と噛み合うため、動力伝達軸には、回転方向の負荷だけでなく特定のラジアル方向の負荷も受ける。そして、転がり軸受１２は、歯車の噛み合い位置に依存して特定の周方向の位相で負荷が集中し、他の位相で負荷が小さくなる。   In the present embodiment, a power transmission member such as a gear (gear), sprocket, pulley, or the like is attached to the power transmission shaft 13, and rotational power is transmitted through the power transmission member. For example, when the power transmission member is a gear, this gear meshes with other gears at one point in the circumferential direction. Therefore, the power transmission shaft has a load in a specific radial direction as well as a load in the rotational direction. Also receive. In the rolling bearing 12, the load is concentrated at a specific circumferential phase depending on the meshing position of the gear, and the load is reduced at other phases.

一方、本実施形態では、外輪２１に設けられたフランジ部２５が、軸方向の厚さ寸法（ｔ１）の大きい第１の領域Ｒ１と、厚さ寸法（ｔ２）の小さい第２の領域Ｒ２とを有している。そして、これらの領域Ｒ１，Ｒ２は、転がり軸受１２に付与される負荷の分布に対応して設定される。すなわち、第１の領域Ｒ１は、負荷の集中する位相に対応して設定され、第２の領域Ｒ２は、負荷の小さい位相に対応して設定される。   On the other hand, in the present embodiment, the flange portion 25 provided on the outer ring 21 includes a first region R1 having a large axial thickness dimension (t1) and a second region R2 having a small thickness dimension (t2). have. And these area | region R1, R2 is set corresponding to distribution of the load provided to the rolling bearing 12. FIG. That is, the first region R1 is set corresponding to the phase where the load is concentrated, and the second region R2 is set corresponding to the phase where the load is small.

これにより、負荷が集中する位相では、フランジ部２５の強度を高めることができ、負荷が小さい位相では、フランジ部２５の強度を低下させることができる。したがって、負荷の集中する位相を基準にして、フランジ部２５全体の厚さ寸法を一律に大きく設定する場合に比べて、重量の増大を抑制しつつ、効果的にフランジ部２５の強度を高めることができる。   Thereby, the strength of the flange portion 25 can be increased in the phase where the load is concentrated, and the strength of the flange portion 25 can be reduced in the phase where the load is small. Therefore, the strength of the flange portion 25 can be effectively increased while suppressing an increase in weight, compared to a case where the thickness dimension of the entire flange portion 25 is uniformly set large with reference to the phase where the load is concentrated. Can do.

また、図２に示されるように、ハウジング１１に対向するフランジ部２５の側面２５ｂ１，２５ｂ２が凹凸形状に形成され、ハウジング１１の側面１１ｂ１，１１ｂ２も凹凸形状に形成され、フランジ部２５の段部２５ｃとハウジング１１の段部１１ｃとが周方向に当接している。したがって、転がり軸受１２の外輪２１に付与された周方向の負荷は、固定ボルト２６だけでなく、段部１１ｃ，２５ｃを介してハウジング１１にも付与される。そのため固定ボルト２６にかかる負担を軽減することができ、固定ボルト２６として、強度が低くより軽量なものを使用することが可能となる。また、フランジ部２５の凹凸形状とハウジング１１の凹凸形状とを対応させることで、ハウジング１１に対してフランジ部２５を固定するときの位置合わせを容易に行うことができる。   Further, as shown in FIG. 2, the side surfaces 25 b 1 and 25 b 2 of the flange portion 25 facing the housing 11 are formed in a concavo-convex shape, and the side surfaces 11 b 1 and 11 b 2 of the housing 11 are also formed in a concavo-convex shape. 25c and the step part 11c of the housing 11 contact | abut in the circumferential direction. Therefore, the circumferential load applied to the outer ring 21 of the rolling bearing 12 is applied not only to the fixing bolt 26 but also to the housing 11 via the step portions 11c and 25c. Therefore, the burden on the fixing bolt 26 can be reduced, and the fixing bolt 26 having a lower strength and a lighter weight can be used. Further, by aligning the uneven shape of the flange portion 25 with the uneven shape of the housing 11, it is possible to easily align the flange portion 25 with respect to the housing 11.

図６は、本発明の第２の実施形態に係る動力伝達装置１０のハウジング１１、動力伝達軸１３、及び転がり軸受１２の平面図、図７は、転がり軸受１２の外輪２１を示す斜視図である。
本実施形態は、互いに対向するフランジ部２５とハウジング１１の側面２５ｂ、１１ｂがいずれも平坦面に形成され、ハウジング１１に対向しないフランジ部２５の側面（図６における右側の側面）２５ｄ１，２５ｄ２が凹凸形状に形成されたものである。その他の構成は、上記第１の実施形態と同様であるため、詳細な説明を省略する。また、本実施形態は、フランジ部２５の凹凸形状とハウジング１１の凹凸形状とを対応させることに基づく作用効果を除き、第１の実施形態と同様の作用効果を奏する。 6 is a plan view of the housing 11, the power transmission shaft 13, and the rolling bearing 12 of the power transmission device 10 according to the second embodiment of the present invention. FIG. 7 is a perspective view showing the outer ring 21 of the rolling bearing 12. FIG. is there.
In the present embodiment, the flange portion 25 and the side surfaces 25b and 11b of the housing 11 that are opposite to each other are formed as flat surfaces, and the side surface (right side surface in FIG. 6) 25d1 and 25d2 of the flange portion 25 that does not face the housing 11 are It is formed in an uneven shape. Since other configurations are the same as those of the first embodiment, detailed description thereof is omitted. In addition, this embodiment has the same functions and effects as those of the first embodiment except for the function and effect based on matching the uneven shape of the flange portion 25 with the uneven shape of the housing 11.

図８は、本発明の第３の実施形態に係る動力伝達装置１０の転がり軸受１２の外輪２１を示す側面図である。
本実施形態の転がり軸受１２は、第１の実施形態とは異なり、フランジ部２５の軸方向の厚さが一定に形成されている。そして、フランジ部２５は、外輪２１の周囲の大部分の領域Ｒ３に形成されているが、一部の領域Ｒ４には形成されていない。より具体的には、周方向に隣接するボルト挿通孔３１の間のうちの一箇所に、補強部３３のない領域Ｒ４が存在している。そして、本実施形態では、動力伝達軸１３からの負荷が集中する位相にフランジ部２５のある領域Ｒ３を対応させ、負荷が小さい位相にフランジ部２５のない領域Ｒ４を対応させている。したがって、本実施形態においても、フランジ部２５の凹凸形状とハウジング１１の凹凸形状とを対応させることに基づく作用効果を除き、第１の実施形態と同様の作用効果を奏する。 FIG. 8 is a side view showing the outer ring 21 of the rolling bearing 12 of the power transmission device 10 according to the third embodiment of the present invention.
Unlike the first embodiment, the rolling bearing 12 of the present embodiment is formed such that the axial thickness of the flange portion 25 is constant. And although the flange part 25 is formed in most area | regions R3 around the outer ring | wheel 21, it is not formed in one part area | region R4. More specifically, a region R4 without the reinforcing portion 33 exists at one place between the bolt insertion holes 31 adjacent in the circumferential direction. In this embodiment, the region R3 with the flange portion 25 is associated with the phase where the load from the power transmission shaft 13 is concentrated, and the region R4 without the flange portion 25 is associated with the phase with a small load. Therefore, also in the present embodiment, the same operational effects as those of the first embodiment are obtained except for the operational effect based on the correspondence between the concave and convex shape of the flange portion 25 and the concave and convex shape of the housing 11.

図９は、本発明の第４の実施形態に係る動力伝達装置１０の転がり軸受１２の外輪２１を概略的に示す側面図である。
本実施形態は、フランジ部２５の軸方向及び径方向の厚さ寸法を、ボルト挿通孔３１の配置との関係で設定したものとなっている。
本実施形態のボルト挿通孔３１は、第１実施形態と同様に不等間隔で形成されている。そして、ボルト挿通孔３１の間隔が狭くなっている領域Ｒ５は、他の領域Ｒ６に比べてフランジ部２５（補強部３３）の軸方向及び径方向の厚さ寸法が小さくなっている。 FIG. 9 is a side view schematically showing the outer ring 21 of the rolling bearing 12 of the power transmission device 10 according to the fourth embodiment of the present invention.
In this embodiment, the axial and radial thickness dimensions of the flange portion 25 are set in relation to the arrangement of the bolt insertion holes 31.
The bolt insertion holes 31 of the present embodiment are formed at unequal intervals as in the first embodiment. And the area | region R5 where the space | interval of the bolt insertion hole 31 is narrow has the axial direction and radial direction thickness dimension of the flange part 25 (reinforcement part 33) small compared with the other area | region R6.

具体的に、図９（ａ）に示す例は、最もボルト挿通孔３１の間隔が狭い領域Ｒ５でフランジ部２５における補強部３３の軸方向の厚さ寸法が小さくなっている（厚さ寸法が小さい部分をハッチングで示す）。また、図９（ｂ）に示す例は、最もボルト挿通孔３１の間隔が狭い領域Ｒ５で補強部３３の径方向の厚さ寸法ｔ４が小さくなっている（厚さ寸法が小さい部分をハッチングで示す）。そして、その他の領域Ｒ６においては、補強部３３の軸方向の厚さ寸法及び径方向の厚さ寸法ｔ３が相対的に大きくなり、強度が高められている。   Specifically, in the example shown in FIG. 9A, the axial thickness dimension of the reinforcing portion 33 in the flange portion 25 is small in the region R5 where the distance between the bolt insertion holes 31 is the narrowest (the thickness dimension is Small areas are hatched). In the example shown in FIG. 9B, the radial thickness dimension t4 of the reinforcing portion 33 is small in the region R5 where the distance between the bolt insertion holes 31 is the narrowest (the portion with the small thickness dimension is hatched). Show). And in other area | region R6, the thickness dimension of the axial direction of the reinforcement part 33 and the thickness dimension t3 of radial direction become relatively large, and the intensity | strength is raised.

ボルト挿通孔３１の配置は、ハウジング１１内における転がり軸受１２の周囲の部品との位置関係によって不等間隔とせざるを得ない場合があり、通常は、ボルト挿通孔３１の間隔が狭い領域では、広い領域に比べてフランジ部２５の強度が高くなる。そのため、本実施形態においては、ボルト挿通孔３１の間隔が最も狭い領域Ｒ５では、フランジ部２５（補強部３３）の軸方向又は径方向の厚さ寸法を小さくすることによって、過剰に強度が高まらないようにし、逆に、ボルト挿通孔３１の間隔が広い領域Ｒ６では、フランジ部２５の軸方向又は径方向の厚さ寸法を大きくすることによって強度を高めている。これにより、重量の増大を抑制しつつ効果的にフランジ部２５の強度を高めることができる。なお、図９（ａ）に示す例では、領域Ｒ５内の補強部３３だけでなく、これに隣接する被取付部３２の軸方向の厚さ寸法も小さくしてもよい。   The arrangement of the bolt insertion holes 31 may be inevitably spaced due to the positional relationship with the components around the rolling bearing 12 in the housing 11. Normally, in the region where the intervals between the bolt insertion holes 31 are narrow, The strength of the flange portion 25 is higher than that in a wide area. Therefore, in this embodiment, in the region R5 where the distance between the bolt insertion holes 31 is the narrowest, the strength is excessively increased by reducing the axial or radial thickness dimension of the flange portion 25 (reinforcing portion 33). On the contrary, in the region R6 where the interval between the bolt insertion holes 31 is wide, the strength is increased by increasing the axial or radial thickness dimension of the flange portion 25. Thereby, the intensity | strength of the flange part 25 can be raised effectively, suppressing the increase in a weight. In the example shown in FIG. 9A, not only the reinforcing portion 33 in the region R5 but also the thickness dimension in the axial direction of the attached portion 32 adjacent thereto may be reduced.

図１０は、本発明の第５の実施形態に係る動力伝達装置１０の転がり軸受１２の外輪２１を概略的に示す側面図である。
本実施形態も、フランジ部２５の軸方向及び径方向の厚さ寸法を、ボルト挿通孔３１の配置との関係で設定したものとなっている。
本実施形態のボルト挿通孔３１は、第４の実施形態と同様に不等間隔で形成されている。そして、ボルト挿通孔３１の間隔が広くなっている領域Ｒ８でフランジ部２５の軸方向及び径方向の厚さ寸法が小さくなっている。 FIG. 10 is a side view schematically showing the outer ring 21 of the rolling bearing 12 of the power transmission device 10 according to the fifth embodiment of the present invention.
Also in the present embodiment, the axial and radial thickness dimensions of the flange portion 25 are set in relation to the arrangement of the bolt insertion holes 31.
The bolt insertion holes 31 of the present embodiment are formed at unequal intervals as in the fourth embodiment. And the thickness dimension of the axial direction and radial direction of the flange part 25 is small in area | region R8 where the space | interval of the bolt insertion hole 31 is wide.

具体的に、図１０（ａ）に示す例は、最もボルト挿通孔３１の間隔が広い領域Ｒ８で、フランジ部２５における補強部３３の軸方向の厚さ寸法が小さくなっている（厚さ寸法が小さい部分をハッチングで示す）。また、図１０（ｂ）に示す例は、最もボルト挿通孔３１の間隔が広い領域Ｒ８で、補強部３３の径方向の厚さ寸法ｔ４が小さくなっている（厚さ寸法が小さい部分をハッチングで示す）。そして、その他の領域Ｒ７においては、軸方向の厚さ寸法及び径方向の厚さ寸法ｔ３がそれぞれ相対的に大きくなり、強度が高められている。   Specifically, in the example shown in FIG. 10A, the axial thickness dimension of the reinforcing portion 33 in the flange portion 25 is small in the region R8 where the distance between the bolt insertion holes 31 is the widest (thickness size). Is shown by hatching). In the example shown in FIG. 10B, the radial thickness dimension t4 of the reinforcing portion 33 is small in the region R8 where the distance between the bolt insertion holes 31 is the widest (the portion with the small thickness dimension is hatched). ). In the other region R7, the axial thickness dimension and the radial thickness dimension t3 are relatively large, and the strength is increased.

ボルト挿通孔３１は、第４の実施形態で説明したように周囲の部品との関係（レイアウト上の関係）で不等間隔に配置されるほか、転がり軸受１２に付与される負荷の分布の関係（強度上の関係）で不等間隔に配置される場合がある。例えば、負荷が集中する位相ではボルト挿通孔３１の間隔を狭くすることによって強度を高めることがある。このような場合、ボルト挿通孔３１の間隔が広い領域Ｒ８は、転がり軸受１２に付与される負荷も小さくなるため、それほど強度を高める必要がない。したがって、本実施形態のように、当該領域Ｒ８におけるフランジ部２５（補強部３３）の軸方向又は径方向の厚さ寸法を小さくすることによって強度を低下させ、重量増大を抑制しつつ効果的に強度を高めることが有効である。なお、図１０（ａ）に示す例では、領域Ｒ８内の補強部３３だけでなく、これに隣接する被取付部３２の軸方向の厚さ寸法も小さくしてもよい。   As described in the fourth embodiment, the bolt insertion holes 31 are arranged at unequal intervals in relation to surrounding parts (layout relationship), and also the relationship of the distribution of the load applied to the rolling bearing 12. There are cases where they are arranged at unequal intervals in relation to strength. For example, in the phase where the load is concentrated, the strength may be increased by narrowing the interval between the bolt insertion holes 31. In such a case, since the load applied to the rolling bearing 12 is reduced in the region R8 where the interval between the bolt insertion holes 31 is large, it is not necessary to increase the strength so much. Therefore, as in the present embodiment, the strength is reduced by reducing the axial or radial thickness dimension of the flange portion 25 (reinforcing portion 33) in the region R8, and the increase in weight is effectively suppressed. It is effective to increase the strength. In the example shown in FIG. 10A, not only the reinforcing portion 33 in the region R8 but also the axial thickness dimension of the attached portion 32 adjacent thereto may be reduced.

本発明は、上記実施形態に限定されることなく特許請求の範囲に記載された発明の範囲内において適宜変更可能である。
例えば、本発明の転がり軸受１２は、動力伝達装置１０以外の装置にも適用可能である。また、フランジ部２５は、外輪２１に設けられたものに限らず、内輪２２に設けられてもよい。また、複数のボルト挿通孔３１は、周方向に関して等間隔に形成されていてもよい。
また、本発明は、上記各実施形態の一部又は全部の構成を組み合わせたものであってもよい。例えば、フランジ部の軸方向の厚さ寸法が異なる複数の領域と、補強部の径方向の厚さ寸法が異なる領域とを組み合わせてもよい。また、フランジ部の厚さ寸法が異なる複数の領域と、補強部が形成されていない領域とを組み合わせてもよい。
また、上記各実施形態においては、フランジ部２５は、軸方向の厚さ寸法、又は補強部３３の径方向の厚さ寸法が異なる３つ以上の領域を有していてもよい。 The present invention is not limited to the above-described embodiment, and can be appropriately changed within the scope of the invention described in the claims.
For example, the rolling bearing 12 of the present invention can be applied to devices other than the power transmission device 10. Further, the flange portion 25 is not limited to the one provided on the outer ring 21 but may be provided on the inner ring 22. Further, the plurality of bolt insertion holes 31 may be formed at equal intervals in the circumferential direction.
In addition, the present invention may be a combination of some or all of the above embodiments. For example, you may combine the some area | region where the thickness dimension of the axial direction of a flange part differs, and the area | region where the thickness dimension of the radial direction of a reinforcement part differs. Moreover, you may combine the several area | region from which the thickness dimension of a flange part differs, and the area | region in which the reinforcement part is not formed.
Moreover, in each said embodiment, the flange part 25 may have 3 or more area | regions from which the thickness dimension of an axial direction differs from the thickness dimension of the radial direction of the reinforcement part 33. FIG.

１０：動力伝達装置、１１：ハウジング、１１ｃ：段部、１２：転がり軸受、１３：動力伝達軸、２１：外輪（軌道輪）、２２：内輪（軌道輪）、２３：玉（転動体）、２５：フランジ部、２５ａ：段部、２６：固定ボルト、３１：ボルト挿通孔、３２：被取付部、３３：補強部、Ｒ１〜Ｒ８：領域 10: Power transmission device, 11: Housing, 11c: Stepped portion, 12: Rolling bearing, 13: Power transmission shaft, 21: Outer ring (track ring), 22: Inner ring (track ring), 23: Ball (rolling element), 25: flange part, 25a: step part, 26: fixing bolt, 31: bolt insertion hole, 32: attached part, 33: reinforcing part, R1 to R8: region

Claims (10)

径方向に対向する一対の軌道輪と、一対の軌道輪の間に転動可能に設けられた転動体と、一方の軌道輪から径方向外方に突出し、複数のボルト挿通孔が周方向に間隔をあけて形成されるとともに当該ボルト挿通孔に挿入されたボルトによってハウジングに固定されるフランジ部と、を備えている転がり軸受であって、
前記フランジ部は、周方向に関して、軸方向の厚さ寸法が異なる複数の領域を有している、転がり軸受。 A pair of raceways opposed in the radial direction, a rolling element provided between the pair of raceways so as to be able to roll, and a plurality of bolt insertion holes extending in the circumferential direction projecting radially outward from one raceway A rolling bearing having a flange portion formed at an interval and fixed to the housing by a bolt inserted into the bolt insertion hole,
The said flange part is a rolling bearing which has several area | regions from which the thickness dimension of an axial direction differs regarding the circumferential direction. 前記フランジ部は、軸方向の一方の側面が平坦面に形成され、他方の側面が前記厚さ寸法の相違により凹凸形状に形成されている、請求項１に記載の転がり軸受。   2. The rolling bearing according to claim 1, wherein one side surface in the axial direction of the flange portion is formed as a flat surface, and the other side surface is formed in a concavo-convex shape due to the difference in the thickness dimension. 前記フランジ部は、ハウジングに当接する側面が凹凸形状に形成されている、請求項２に記載の転がり軸受。   The rolling bearing according to claim 2, wherein a side surface of the flange portion that contacts the housing is formed in an uneven shape. 径方向に対向する一対の軌道輪と、一対の軌道輪の間に転動可能に設けられた転動体と、一方の軌道輪から径方向外方に突出し、複数のボルト挿通孔が周方向に間隔をあけて形成されるとともに当該ボルト挿通孔に挿入されたボルトによってハウジングに固定されるフランジ部と、を備えている転がり軸受であって、
前記フランジ部は、前記ボルト挿通孔が形成され前記ハウジングに直接的に取り付けられる複数の被取付部と、周方向に隣接する被取付部の間に形成される補強部とを含み、
前記フランジ部は、周方向に関して、前記補強部の径方向の厚さ寸法が異なる複数の領域を有している、転がり軸受。 A pair of raceways opposed in the radial direction, a rolling element provided between the pair of raceways so as to be able to roll, and a plurality of bolt insertion holes extending in the circumferential direction projecting radially outward from one raceway A rolling bearing having a flange portion formed at an interval and fixed to the housing by a bolt inserted into the bolt insertion hole,
The flange portion includes a plurality of attached portions in which the bolt insertion holes are formed and attached directly to the housing, and a reinforcing portion formed between the attached portions adjacent in the circumferential direction,
The said flange part is a rolling bearing which has several area | region where the thickness dimension of the radial direction of the said reinforcement part differs regarding the circumferential direction. 前記ボルト挿通孔が周方向に関して不等間隔で配置されており、
前記ボルト挿通孔の間隔が広い領域で前記厚さ寸法が小さく、狭い領域で前記厚さ寸法が大きく設定されている、請求項１〜４のいずれか１項に記載の転がり軸受。 The bolt insertion holes are arranged at unequal intervals in the circumferential direction,
The rolling bearing according to claim 1, wherein the thickness dimension is set to be small in a region where the interval between the bolt insertion holes is wide, and the thickness dimension is set to be large in a narrow region. 前記ボルト挿通孔が周方向に関して不等間隔で形成されており、
前記ボルト挿通孔の間隔が広い領域で前記厚さ寸法が大きく、狭い領域で前記厚さ寸法が小さく設定されている、請求項１〜４のいずれか１項に記載の転がり軸受。 The bolt insertion holes are formed at unequal intervals in the circumferential direction,
The rolling bearing according to any one of claims 1 to 4, wherein the thickness dimension is set large in a region where the interval between the bolt insertion holes is wide, and the thickness dimension is set small in a narrow region. 径方向に対向する一対の軌道輪と、一対の軌道輪の間に転動可能に設けられた転動体と、一方の軌道輪から径方向外方に突出し、複数のボルト挿通孔が周方向に間隔をあけて形成されるとともに当該ボルト挿通孔に挿入されたボルトによってハウジングに固定されるフランジ部と、を備えている転がり軸受であって、
前記フランジ部は、前記ボルト挿通孔が形成され前記ハウジングに直接的に取り付けられる複数の被取付部と、周方向に隣接する被取付部の間のうち、少なくとも１箇所を除いて形成される補強部とを含む、転がり軸受。 A pair of raceways opposed in the radial direction, a rolling element provided between the pair of raceways so as to be able to roll, and a plurality of bolt insertion holes extending in the circumferential direction projecting radially outward from one raceway A rolling bearing having a flange portion formed at an interval and fixed to the housing by a bolt inserted into the bolt insertion hole,
The flange portion is formed by removing at least one of a plurality of attached portions in which the bolt insertion holes are formed and directly attached to the housing, and attached portions adjacent in the circumferential direction. Rolling bearing including a part. 請求項１〜７のいずれか１項に記載された転がり軸受と、この転がり軸受のフランジ部が固定されるハウジングと、このハウジング内で前記転がり軸受によって回転自在に支持された動力伝達軸と、を有し、前記フランジ部は、前記動力伝達軸からの負荷の分布に応じて前記厚さ寸法の異なる領域が設定されている、動力伝達装置。   A rolling bearing according to any one of claims 1 to 7, a housing to which a flange portion of the rolling bearing is fixed, a power transmission shaft rotatably supported by the rolling bearing in the housing, The flange portion is a power transmission device in which regions having different thickness dimensions are set according to a distribution of a load from the power transmission shaft. 請求項３に記載された転がり軸受と、この転がり軸受のフランジ部が固定されるハウジングと、このハウジング内で前記転がり軸受によって回転自在に支持された動力伝達軸と、を有し、
前記フランジ部に当接する前記ハウジングの側面に、当該フランジ部の凸部に対応する凹部と、当該フランジ部の凹部に対応する凸部とが形成されている、動力伝達装置。 A rolling bearing according to claim 3, a housing to which a flange portion of the rolling bearing is fixed, and a power transmission shaft rotatably supported by the rolling bearing in the housing,
A power transmission device, wherein a concave portion corresponding to the convex portion of the flange portion and a convex portion corresponding to the concave portion of the flange portion are formed on a side surface of the housing that contacts the flange portion. 前記フランジ部の側面における凹凸の境界に位置する段部と、前記ハウジングの側面における凹凸の境界に位置する段部とが、互いに周方向に対向して当接している、請求項９に記載の動力伝達装置。   The step part located in the uneven | corrugated boundary in the side surface of the said flange part and the step part located in the uneven | corrugated boundary in the side surface of the said housing contact | abut each other in the circumferential direction. Power transmission device.
JP2013246476A 2013-11-28 2013-11-28 Rolling bearing, and power transmission device equipped with the same Pending JP2015105670A (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2017013917A1 (en) * 2015-07-21 2017-01-26 日本精工株式会社 Bearing unit

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2017013917A1 (en) * 2015-07-21 2017-01-26 日本精工株式会社 Bearing unit
JP2017025998A (en) * 2015-07-21 2017-02-02 日本精工株式会社 Bearing unit
CN107923441A (en) * 2015-07-21 2018-04-17 日本精工株式会社 Bearing unit
EP3327300A4 (en) * 2015-07-21 2018-05-30 NSK Ltd. Bearing unit
US10520028B2 (en) 2015-07-21 2019-12-31 Nsk Ltd. Bearing unit

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