JP2012154379A - Rolling bearing device - Google Patents

Rolling bearing device Download PDF

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Publication number
JP2012154379A
JP2012154379A JP2011012492A JP2011012492A JP2012154379A JP 2012154379 A JP2012154379 A JP 2012154379A JP 2011012492 A JP2011012492 A JP 2011012492A JP 2011012492 A JP2011012492 A JP 2011012492A JP 2012154379 A JP2012154379 A JP 2012154379A
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Japan
Prior art keywords
inner ring
shaft
rolling bearing
bearing device
housing
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Pending
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JP2011012492A
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Japanese (ja)
Inventor
Manabu Chiga
学 千賀
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NSK Ltd
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NSK Ltd
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Priority to JP2011012492A priority Critical patent/JP2012154379A/en
Publication of JP2012154379A publication Critical patent/JP2012154379A/en
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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
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/063—Fixing them on the shaft
    • 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
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/067—Fixing them in a 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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/36—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers
    • F16C19/364—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • 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
    • F16C19/548—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings in O-arrangement

Abstract

PROBLEM TO BE SOLVED: To provide a rolling bearing device which can be used in combination with a race ring, a housing, a shaft or the like of a conventional rolling bearing device and which suppresses causes of a creep phenomenon between an outer ring and a housing or between an inner ring and a shaft, by working on the components in such a manner that on a fitting face in a loading zone, the surface of one component can easily follow the surface of the other component, or by inducing a compressive strain to reduce a tensile strain acting on a surface.SOLUTION: The rolling bearing device includes the outer ring, the inner ring, a plurality of rolling elements, the housing in which the outer ring is assembled, and the shaft in which the inner ring is assembled. At least one circumferential surface of the outer ring, inner ring, housing and shaft includes a plurality of grooves penetrating in an axial direction.

Description

本発明は、転がり軸受装置に関し、特にクリープ現象の発生を抑制する転がり軸受装置に関する。   The present invention relates to a rolling bearing device, and more particularly to a rolling bearing device that suppresses the occurrence of a creep phenomenon.

転がり軸受装置は、自動車や各種産業機械等の各種回転機械装置で、回転軸等を支持する軸受部に広く使用されている。この転がり軸受装置の概略的構成の一例を図１に示す。図１の転がり軸受装置１は、ダンプトラック用である。この転がり軸受装置は、重量の重い車輪を、懸架装置に対して回転自在に支持している。この様な、転がり軸受装置では、外輪はハウジングに対して、内輪は軸に対して、僅かなすき間又は締め代を持って固定され、互いの相対回転であるクリープ現象が防止されている。しかし、高荷重下や、急激な回転停止が行われたり、すき間の値や締め代が十分でない場合等において、外輪とハウジングの間、または内輪と軸の間にて、クリープ現象が生じる可能性があった。   Rolling bearing devices are widely used in bearing parts that support rotating shafts and the like in various rotating machine devices such as automobiles and various industrial machines. An example of a schematic configuration of the rolling bearing device is shown in FIG. The rolling bearing device 1 of FIG. 1 is for a dump truck. This rolling bearing device supports a heavy wheel so as to be rotatable with respect to the suspension device. In such a rolling bearing device, the outer ring is fixed to the housing and the inner ring is fixed to the shaft with a slight clearance or tightening margin to prevent a creep phenomenon that is a relative rotation of each other. However, creep may occur between the outer ring and the housing or between the inner ring and the shaft under heavy loads, sudden rotation stoppage, or when the clearance or tightening allowance is insufficient. was there.

この部分の改善の先行技術としては、図５のように、転がり軸受装置１０の内輪２２に凸部２２ａ、軸２６に凹部２６ａを設けて非円形としたものがある。これは、前記内輪２２と軸２６を組み立てる際、前記凸部２２ａと前記凹部２６ａを係合させて、内輪２２と軸２６の間のクリープ現象を防止するものである（例えば、特許文献１参照）。   As a prior art for improving this portion, as shown in FIG. 5, there is a non-circular shape in which a convex portion 22 a is provided on the inner ring 22 of the rolling bearing device 10 and a concave portion 26 a is provided on the shaft 26. This is to prevent the creep phenomenon between the inner ring 22 and the shaft 26 by engaging the convex portion 22a and the concave portion 26a when assembling the inner ring 22 and the shaft 26 (see, for example, Patent Document 1). ).

実開平２−１２２２１７号公報Japanese Utility Model Publication No. 2-122217

しかし、図５のように、凸部２２ａと凹部２６ａを設ける場合、凸部２２ａと凹部２６ａの間のすきまが最小限になる様に、凸部２２ａと凹部２６の両方を精度良く加工する必要がある。また、内輪２２と軸２６のそれぞれに、凸部２２ａと凹部２６が一対になる様に設ける必要がある。その為、従来の、凸部２２ａと凹部２６が無い内輪や軸と、組合わせ難いという問題があった。   However, as shown in FIG. 5, when providing the convex portion 22a and the concave portion 26a, it is necessary to process both the convex portion 22a and the concave portion 26 with high accuracy so that the clearance between the convex portion 22a and the concave portion 26a is minimized. There is. Further, it is necessary to provide the inner ring 22 and the shaft 26 so that the convex portion 22a and the concave portion 26 are paired. For this reason, there is a problem that it is difficult to combine with the conventional inner ring or shaft without the convex portion 22a and the concave portion 26.

本発明は、上述のような従来技術の問題に鑑み、従来の転がり軸受装置の、軌道輪や、ハウジングや、軸等と組合わせて使用することが可能であり、負荷圏の嵌合面において一方の部品の表面に他方の部品の表面が追従し易いように加工したり、表面に作用する引張り応力を減少させるように圧縮応力を作用させることにより、外輪とハウジングの間、または内輪と軸の間にて、クリープ現象が生じる可能性を抑制した転がり軸受装置を提供することを目的とする。   The present invention can be used in combination with a bearing ring, a housing, a shaft, and the like of a conventional rolling bearing device in view of the problems of the prior art as described above. By processing the surface of one part so that the surface of the other part can easily follow, or by applying a compressive stress to reduce the tensile stress acting on the surface, between the outer ring and the housing or between the inner ring and the shaft An object of the present invention is to provide a rolling bearing device that suppresses the possibility of a creep phenomenon occurring between the two.

上記目的を達成するために、本発明による転がり軸受装置は、外輪と内輪と複数の転動体と、外輪を組み込む為のハウジングと、内輪を組み込む為の軸からなり、前記外輪、内輪、ハウジング、軸の少なくともいずれか１つの周面に、軸方向に貫通した複数の溝を設けたことを特徴とする。   In order to achieve the above object, a rolling bearing device according to the present invention comprises an outer ring, an inner ring, a plurality of rolling elements, a housing for incorporating the outer ring, and a shaft for incorporating the inner ring, the outer ring, the inner ring, the housing, A plurality of grooves penetrating in the axial direction are provided on at least one peripheral surface of the shaft.

本発明の転がり軸受装置によれば、従来の転がり軸受装置の、軌道輪や、ハウジングや、軸等と組合わせて使用することが可能であり、負荷圏の嵌合面において一方の部品の表面に他方の部品の表面が追従し易いように加工したり、表面に作用する引張り応力を減少させるように圧縮応力を作用させることにより、外輪とハウジングの間、または内輪と軸の間にて、クリープ現象が生じる可能性を抑制した転がり軸受装置を提供できる。   According to the rolling bearing device of the present invention, the conventional rolling bearing device can be used in combination with a bearing ring, a housing, a shaft, etc., and the surface of one part in the mating surface of the load zone By making the surface of the other part easy to follow, or by applying a compressive stress to reduce the tensile stress acting on the surface, between the outer ring and the housing or between the inner ring and the shaft, It is possible to provide a rolling bearing device that suppresses the possibility of a creep phenomenon.

本発明に係る転がり軸受装置の断面図Sectional drawing of the rolling bearing apparatus which concerns on this invention 本発明に係る転がり軸受装置の第１実施例形態の部分断面図Partial sectional view of the first embodiment of the rolling bearing device according to the present invention 本発明に係る転がり軸受装置の第２実施形態の部分断面図Partial sectional drawing of 2nd Embodiment of the rolling bearing apparatus which concerns on this invention. 本発明に係る転がり軸受装置の第３実施形態の部分断面図Partial sectional view of a third embodiment of the rolling bearing device according to the present invention. 従来の転がり軸受装置の部分斜視図Partial perspective view of a conventional rolling bearing device

以下、本発明を実施するための形態について図面を用いて説明する。図１は本発明の実施の形態による転がり軸受装置の断面図である。本発明による転がり軸受装置１は、外輪３と内輪２と複数の転動体４と、外輪３を組み込む為のハウジング７と、内輪２を組み込む為の軸６からなる。図１では、外輪３が回転し、転動体４は、外輪３からの荷重を受け、内輪２は、転動体４からの荷重を受けている。   Hereinafter, embodiments for carrying out the present invention will be described with reference to the drawings. FIG. 1 is a sectional view of a rolling bearing device according to an embodiment of the present invention. A rolling bearing device 1 according to the present invention includes an outer ring 3, an inner ring 2, a plurality of rolling elements 4, a housing 7 for incorporating the outer ring 3, and a shaft 6 for incorporating the inner ring 2. In FIG. 1, the outer ring 3 rotates, the rolling element 4 receives a load from the outer ring 3, and the inner ring 2 receives a load from the rolling element 4.

＜第１実施形態＞
図２は、本発明に係る転がり軸受装置の第１実施形態の部分断面図である。図２では、軸６の負荷が加えられる負荷圏Ａの周方向に引張り応力が発生していない範囲の外周面６ａに、軸方向に貫通した複数の溝５、５を、転動体の周方向の間隔より狭い間隔にて設けている。これは、クリープ現象が、転動体からの荷重の影響を受けて発生している為、前記溝５の周方向の間隔を転動体の周方向の間隔より狭くすることにより、軸外周面６ａの溝５と溝５の間の部分５ａが、内輪内周面２ａの周方向の動きに追従し易くなるため、軸６と内輪２の相対的運動であるクリープ現象を抑制出来るからである。また、周方向に引張り応力が発生していない範囲の外周面６ａに、前記溝５を設ける理由は、溝底５ｂ、５ｂに引張り応力による亀裂が発生し難くする為である。また、本実施形態では、軸のみに溝を設け、内輪は従来の内輪を組合わせて、クリープ現象を抑制している。また、本実施形態では、外輪が回転する場合を例示しているが、内輪が回転する場合には、ハウジングに上記と同様の複数の溝を設けることにより、上記と同様の効果が得られる。 <First Embodiment>
FIG. 2 is a partial cross-sectional view of the first embodiment of the rolling bearing device according to the present invention. In FIG. 2, a plurality of grooves 5, 5 penetrating in the axial direction are formed on the outer peripheral surface 6 a in a range where no tensile stress is generated in the circumferential direction of the load zone A to which the load of the shaft 6 is applied. It is provided at an interval narrower than the interval. This is because the creep phenomenon occurs due to the influence of the load from the rolling elements, so that the circumferential interval of the grooves 5 is made smaller than the circumferential interval of the rolling elements, so that This is because the portion 5a between the groove 5 and the groove 5 can easily follow the movement in the circumferential direction of the inner ring inner peripheral surface 2a, so that the creep phenomenon, which is the relative movement between the shaft 6 and the inner ring 2, can be suppressed. The reason why the groove 5 is provided on the outer peripheral surface 6a in a range where no tensile stress is generated in the circumferential direction is that cracks due to the tensile stress hardly occur in the groove bottoms 5b and 5b. In this embodiment, a groove is provided only on the shaft, and the inner ring is combined with a conventional inner ring to suppress the creep phenomenon. Moreover, although the case where an outer ring | wheel rotates is illustrated in this embodiment, when an inner ring | wheel rotates, the effect similar to the above is acquired by providing the same groove | channel as the above in a housing.

＜第２実施形態＞
図３は、本発明に係る転がり軸受装置の第２実施形態の部分断面図である。図３では、内輪２の非負荷圏（負荷圏Ａではない部分）の周方向に引張り応力が発生していない範囲の内周面２ｂに、軸方向に貫通した複数の溝５、５を設けている。この様な溝が無い場合は、負荷圏Ａで転動体から受ける荷重により、負荷圏Ａの内輪内周面２ａには、引張りひずみが発生する。それに対して、この様な溝を設けると、内輪２が、負荷圏に長軸が位置する様な楕円状に変形する為、負荷圏の内輪内周面の長軸付近の表面に、圧縮ひずみが発生し易くなる。その為、溝が無い場合の引張りひずみは、溝５による圧縮ひずみにより抑制されるので、負荷圏Ａでの内輪内周面２ａと軸外周面６ａの間に、クリープ現象が生じる原因を抑制することができる。また、周方向に引張りひずみが発生していない範囲の内周面２ｂに、前記溝５を設ける理由は、溝底５ｂ、５ｂに引張り応力による亀裂が発生し難くする為である。また、本実施形態では、内輪２のみに溝５を設け、軸６は従来の軸を組合わせて、クリープ現象を抑制している。なお、前記溝５は、負荷が最大になる部分に、最大の圧縮ひずみが働くように設けることが好ましい。また、本実施形態では、図１の様に、外輪３が回転する場合を例示しているが、内輪２が回転する場合には、外輪外周面３ａに上記と同様の複数の溝を設けることにより、上記と同様の効果が得られる。 Second Embodiment
FIG. 3 is a partial sectional view of a second embodiment of the rolling bearing device according to the present invention. In FIG. 3, a plurality of grooves 5, 5 penetrating in the axial direction are provided on the inner peripheral surface 2 b in a range where no tensile stress is generated in the circumferential direction of the non-load zone (the portion that is not the load zone A) of the inner ring 2. ing. When there is no such groove, tensile strain is generated on the inner ring inner peripheral surface 2a of the load zone A due to the load received from the rolling elements in the load zone A. On the other hand, when such a groove is provided, the inner ring 2 is deformed into an elliptical shape in which the major axis is located in the load zone, so that the compressive strain is applied to the surface near the major axis of the inner ring inner surface of the load zone. Is likely to occur. Therefore, since the tensile strain in the absence of the groove is suppressed by the compressive strain due to the groove 5, the cause of the creep phenomenon between the inner ring inner peripheral surface 2a and the shaft outer peripheral surface 6a in the load zone A is suppressed. be able to. The reason why the groove 5 is provided in the inner peripheral surface 2b in a range where no tensile strain is generated in the circumferential direction is that cracks due to tensile stress are hardly generated in the groove bottoms 5b and 5b. Moreover, in this embodiment, the groove | channel 5 is provided only in the inner ring | wheel 2, and the axis | shaft 6 has combined the conventional axis | shaft and has suppressed the creep phenomenon. In addition, it is preferable to provide the said groove | channel 5 so that the largest compressive strain may act in the part where load becomes the maximum. Further, in this embodiment, the case where the outer ring 3 rotates as illustrated in FIG. 1 is illustrated, but when the inner ring 2 rotates, a plurality of grooves similar to the above are provided on the outer ring outer peripheral surface 3a. Thus, the same effect as described above can be obtained.

＜第３実施形態＞
図４は、本発明に係る転がり軸受装置の第３実施形態の部分断面図である。本実施形態は、第１実施形態と第２実施形態を組み合わせている。図４では、負荷圏Ａの周方向に引張り応力が発生していない範囲の軸外周面６ａに、軸方向に貫通した複数の溝５を、転動体の周方向の間隔より狭い間隔にて設けており、内輪内周面２ａの非負荷圏の周方向に引張り応力が発生していない範囲に、軸方向に貫通した複数の溝５を設けている。この様な構造にしたことにより、前記と同様の理由にて、軸外周面６ａの溝５と溝５の間の部分５ａが、内輪内周面２ａの周方向の動きに追従し易くなり、引張りひずみも抑制されるので、負荷圏での内輪内周面２ａと軸外周面６ａの間に、クリープ現象が生じる原因を抑制することができる。また、本実施形態では、図１の外輪３が回転する場合を例示しているが、内輪２が回転する場合には、ハウジングの非負荷圏の内周面７ａと外輪外周面３ａに上記と同様の複数の溝を設けることにより、上記と同様の効果が得られる。 <Third Embodiment>
FIG. 4 is a partial sectional view of a third embodiment of the rolling bearing device according to the present invention. In the present embodiment, the first embodiment and the second embodiment are combined. In FIG. 4, a plurality of grooves 5 penetrating in the axial direction are provided on the shaft outer peripheral surface 6 a in a range where no tensile stress is generated in the circumferential direction of the load zone A at intervals smaller than the circumferential interval of the rolling elements. A plurality of grooves 5 penetrating in the axial direction are provided in a range where no tensile stress is generated in the circumferential direction of the non-load zone of the inner ring inner peripheral surface 2a. By having such a structure, for the same reason as described above, the portion 5a between the groove 5 and the groove 5 of the shaft outer peripheral surface 6a can easily follow the circumferential movement of the inner ring inner peripheral surface 2a. Since tensile strain is also suppressed, it is possible to suppress the cause of the creep phenomenon between the inner ring inner peripheral surface 2a and the shaft outer peripheral surface 6a in the load zone. Further, in the present embodiment, the case where the outer ring 3 of FIG. 1 rotates is illustrated, but when the inner ring 2 rotates, the inner peripheral surface 7a and the outer ring outer peripheral surface 3a of the non-load zone of the housing are described above. By providing a plurality of similar grooves, the same effect as described above can be obtained.

また、上述の実施形態は本発明の一例を示したものであって、本発明はこれらの実施形態に限定されるものではない。本発明の主旨を外れない限り、他の実施形態にも適用できる。   Moreover, the above-mentioned embodiment shows an example of this invention, Comprising: This invention is not limited to these embodiment. As long as the gist of the present invention is not deviated, the present invention can be applied to other embodiments.

１、１０ 転がり軸受装置
１ａ、１ｂ 転がり軸受
２、２２ 内輪
２ａ、２ｂ 内輪内周面
３ 外輪
３ａ 外輪外周面
４ 転動体
５ 溝
５ａ 溝と溝の間の部分
５ｂ 溝底
６、２６ 軸
６ａ 軸外周面
７ ハウジング
７ａ ハウジング内周面
２２ａ 凸部
２６ａ 凹部
Ａ 負荷圏 DESCRIPTION OF SYMBOLS 1, 10 Rolling bearing apparatus 1a, 1b Rolling bearings 2, 22 Inner ring 2a, 2b Inner ring inner peripheral surface 3 Outer ring 3a Outer ring outer peripheral surface 4 Rolling element 5 Groove 5a A portion 5b between the grooves 5b Groove bottom 6, 26 Shaft 6a Shaft Outer peripheral surface 7 Housing 7a Housing inner peripheral surface 22a Convex part 26a Concave part A Load zone

Claims (1)

外輪と内輪と複数の転動体と、外輪を組み込む為のハウジングと、内輪を組み込む為の軸からなり、前記外輪、内輪、ハウジング、軸の少なくともいずれか１つの周面に、軸方向に貫通した複数の溝を設けたことを特徴とする転がり軸受装置 An outer ring, an inner ring, a plurality of rolling elements, a housing for incorporating the outer ring, and a shaft for incorporating the inner ring, and penetrated at least one of the outer ring, the inner ring, the housing, and the shaft in the axial direction. Rolling bearing device provided with a plurality of grooves
JP2011012492A 2011-01-25 2011-01-25 Rolling bearing device Pending JP2012154379A (en)

Priority Applications (1)

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JP2011012492A JP2012154379A (en) 2011-01-25 2011-01-25 Rolling bearing device

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Application Number Priority Date Filing Date Title
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Publications (1)

Publication Number Publication Date
JP2012154379A true JP2012154379A (en) 2012-08-16

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2017075629A (en) * 2015-10-14 2017-04-20 株式会社デンソー Rotary electric machine

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2017075629A (en) * 2015-10-14 2017-04-20 株式会社デンソー Rotary electric machine

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