JP6357979B2 - Bearing device - Google Patents

Bearing device Download PDF

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JP6357979B2
JP6357979B2 JP2014173507A JP2014173507A JP6357979B2 JP 6357979 B2 JP6357979 B2 JP 6357979B2 JP 2014173507 A JP2014173507 A JP 2014173507A JP 2014173507 A JP2014173507 A JP 2014173507A JP 6357979 B2 JP6357979 B2 JP 6357979B2
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Prior art keywords
outer ring
ring member
raceway
housing
ring raceway
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JP2016048096A (en
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欽悟 北口
欽悟 北口
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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
    • 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
    • F16C35/07—Fixing them on the shaft or housing with interposition of an element
    • F16C35/077—Fixing them on the shaft or housing with interposition of an element between housing and outer race 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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • F16C19/541—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing
    • F16C19/542—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing with two rolling bearings with angular contact
    • F16C19/543—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing with two rolling bearings with angular contact in O-arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
    • F16C19/163—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls with angular contact

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

Description

本発明は、軸受装置に係り、より詳しくは、ハウジングと、アンギュラ玉軸受とからなる軸受装置に関する。   The present invention relates to a bearing device, and more particularly to a bearing device including a housing and an angular ball bearing.

従来、工作機械の主軸等には、複式のアンギュラ玉軸受がハウジング組込まれた軸受装置が使用される（特許文献１参照）。通常、前記軸受装置における複式のアンギュラ玉軸受は、回転精度を確保するために、運転時に予圧が付加されるように、静止状態で、所定の予圧または、微小なすきまとなるように設定されている。   Conventionally, a bearing device in which a double angular ball bearing is incorporated in a housing is used for a spindle of a machine tool or the like (see Patent Document 1). Usually, the double angular ball bearing in the bearing device is set to have a predetermined preload or a small clearance in a stationary state so that a preload is applied during operation in order to ensure rotational accuracy. Yes.

また、前記アンギュラ玉軸受の外輪と前記ハウジングの間は、ルーズフィットの嵌合となっている。前記アンギュラ玉軸受は、前記ハウジングに嵌入された後、前記ハウジングを構成する押え部材で、前記アンギュラ玉軸受の外輪の側面を軸線方向に締付けられることにより、前記ハウジングに固定される。   In addition, a loose fit is provided between the outer ring of the angular ball bearing and the housing. After the angular ball bearing is inserted into the housing, the side surface of the outer ring of the angular ball bearing is clamped in the axial direction by a pressing member constituting the housing, and is fixed to the housing.

前記アンギュラ玉軸受は、前記外輪の側面が軸線方向に締付けられ、前記ハウジングに固定されたとき、所定の予圧または微小なすきまとなるよう、予め、前記内輪の幅と前記外輪の幅が調整されている。しかし、前記外輪の側面に軸線方向に押圧されて固定される際、前記外輪に軸線方向の荷重が加わることで、前記外輪は、軸線方向に圧縮され、径方向に膨張する。   In the angular ball bearing, when the side surface of the outer ring is tightened in the axial direction and fixed to the housing, the width of the inner ring and the width of the outer ring are adjusted in advance so that a predetermined preload or a minute clearance is obtained. ing. However, when the outer ring is pressed and fixed to the side surface in the axial direction, an axial load is applied to the outer ring, whereby the outer ring is compressed in the axial direction and expanded in the radial direction.

前記外輪軌道の転動体と接触する位置において、前記外輪軌道が、転動体から離れる方向に変形すると、予圧の低下、または、すきまの増加が生じ、運転時の回転精度が低下する場合がある。軸線方向に圧縮されることによる、前記外輪軌道の転動体と接触する位置における転動体から離れる方向の変形は、前記外輪の内周の両端部にシール溝が形成された外輪において著しい。   If the outer ring raceway is deformed in a direction away from the rolling element at a position in contact with the rolling element of the outer ring raceway, a decrease in preload or an increase in clearance may occur, resulting in a reduction in rotational accuracy during operation. The deformation in the direction away from the rolling element at the position in contact with the rolling element of the outer ring raceway due to the compression in the axial direction is significant in the outer ring in which seal grooves are formed at both ends of the inner periphery of the outer ring.

特開２００５−１１３９５０号公報JP 2005-113950 A

本発明は、アンギュラ玉軸受をハウジングに組込んだときの、予圧の低下、または、すきまの増加が少なく、回転精度の低下を防止でき、加工が容易な軸受装置を提供することを目的としている。   An object of the present invention is to provide a bearing device that is easy to process and can prevent a decrease in preload or clearance and a decrease in rotational accuracy when an angular ball bearing is incorporated in a housing. .

上記の課題を解決するため、請求項１に係る発明の構成上の特徴は、アンギュラ玉軸受は、内周に外輪軌道と一対のシール溝が形成された外輪部材と、外周に内輪軌道が形成された内輪部材と、前記外輪軌道と前記内輪軌道の間で転動する複数の玉と、を有し、ハウジングは、内周に外輪嵌合面と、前記外輪嵌合面の軸線方向両端部から半径方向内方に縮径する一対の外輪押え面を有し、２個の前記アンギュラ玉軸受の、前記内輪部材が軸部材に固定され、前記外輪部材が、前期ハウジングの外輪嵌合面に隙間嵌めで嵌入され、前記外輪部材の側面が、前記一対の外輪押え面によって軸線方向に押圧されて、前記ハウジングに固定される軸受装置であって、前記外輪軌道は大端部と小端部を有し、一方の前記シール溝と前記外輪軌道の大端部との間の領域に、径方向に拡径する前記外輪軌道と同心の環状溝を有し、前記環状溝の最大径は前記シール溝の最大径より大きく形成されることにより、前記押圧による前記外輪軌道の変形を抑制することである。   In order to solve the above problems, the structural feature of the invention according to claim 1 is that an angular contact ball bearing has an outer ring member formed with an outer ring raceway and a pair of seal grooves on the inner circumference, and an inner ring raceway formed on the outer circumference. The inner ring member and a plurality of balls that roll between the outer ring raceway and the inner ring raceway, and the housing has an outer ring fitting surface on the inner periphery, and both axial ends of the outer ring fitting surface. A pair of outer ring pressing surfaces that are radially reduced inward from the inner ring member of the two angular ball bearings, the outer ring member being fixed to the outer ring fitting surface of the previous housing. A bearing device that is fitted with a gap fit, and the side surface of the outer ring member is pressed in the axial direction by the pair of outer ring pressing surfaces and fixed to the housing, wherein the outer ring raceway has a large end portion and a small end portion The seal groove on one side and the large end of the outer ring raceway An annular groove concentric with the outer ring raceway radially expanding in a region between the outer ring and a maximum diameter of the annular groove that is larger than a maximum diameter of the seal groove. It is to suppress the deformation of the track.

通常、２個のアンギュラ玉軸受は、ハウジングに固定されたとき、所定の予圧が与えられるように、予め、前記内輪の幅と前記外輪の幅が調整されている。前記２個のアンギュラ玉軸受は、前記内輪部材が軸部材に固定され、前記外輪部材が、前記ハウジングの前記外輪嵌合面に隙間嵌めで嵌入されている。また、２個のアンギュラ玉軸受の前記外輪の側面が、前記カバーの前記外輪嵌合面側に形成された前記外輪押え面によって軸線方向に押圧されて前記ハウジングに固定されている。   Usually, when the two angular ball bearings are fixed to the housing, the width of the inner ring and the width of the outer ring are adjusted in advance so that a predetermined preload is applied. In the two angular ball bearings, the inner ring member is fixed to a shaft member, and the outer ring member is fitted into the outer ring fitting surface of the housing with a clearance fit. Further, the side surfaces of the outer ring of the two angular ball bearings are fixed in the housing by being pressed in the axial direction by the outer ring pressing surface formed on the outer ring fitting surface side of the cover.

前記外輪の側面が、前記外輪押え面によって軸線方向に押圧されることによって、前記外輪部材が、軸線方向に圧縮され、径方向に膨張し、前記外輪軌道の転動体と接触する位置においては、前記外輪軌道は転動体から離れる方向に変形し、予圧が、目的の値より低下することがある。前記外輪軌道の転動体から離れる方向の変形は、前記外輪の内周の両端部にシール溝が形成された外輪において著しい。   When the outer ring side surface is pressed in the axial direction by the outer ring holding surface, the outer ring member is compressed in the axial direction, expanded in the radial direction, and in a position where it contacts the rolling elements of the outer ring raceway. The outer ring raceway may be deformed in a direction away from the rolling elements, and the preload may be lowered from a target value. The deformation in the direction away from the rolling elements of the outer ring raceway is remarkable in the outer ring in which seal grooves are formed at both ends of the inner periphery of the outer ring.

しかし、本発明の構成によれば、前記外輪の一方のシール溝と前記外輪軌道の間に、径方向に拡径する環状溝が形成されている。このため、前記外輪の側面が、前記外輪押え面によって軸線方向に押圧されたとき、環状溝２９の外方領域に圧縮荷重が集中し、外輪軌道２１周辺の応力増加が抑制される。前記外輪部材は、前記側面側の外周が径方向外方に拡径し、前記環状溝側の前記シール溝を含む端部が押圧方向に移動し、外輪軌道２１周辺の変形は小さい。   However, according to the configuration of the present invention, an annular groove that is radially expanded is formed between one seal groove of the outer ring and the outer ring raceway. For this reason, when the side surface of the outer ring is pressed in the axial direction by the outer ring pressing surface, a compressive load is concentrated on the outer region of the annular groove 29, and an increase in stress around the outer ring raceway 21 is suppressed. In the outer ring member, the outer periphery on the side surface side expands radially outward, the end including the seal groove on the annular groove side moves in the pressing direction, and deformation around the outer ring raceway 21 is small.

この結果、前記外輪軌道の前記転動体と接触する部位の軸線方向の圧縮変形および、径方向外方への変形は、通常のアンギュラ玉軸受にくらべ小さくなり、前記外輪部材の外輪軌道が、前記転動体から離れる方向に、大きく変形することはない。すなわち、前記２個のアンギュラ玉軸受の予圧が低下しにくく、予圧の低下による回転精度の低下が少ない。   As a result, axial compression deformation and radial outward deformation of the outer ring raceway in contact with the rolling elements are smaller than those of a normal angular ball bearing, and the outer ring raceway of the outer ring member is There is no significant deformation in the direction away from the rolling elements. That is, the pre-load of the two angular ball bearings is not easily lowered, and the rotational accuracy is not lowered due to the decrease of the pre-load.

上記の課題を解決するため、請求項２に係る発明の構成上の特徴は、前記外輪部材の前記環状溝は、軸方向の断面が径方向外方に頂点を有する三角形に形成されたことである。   In order to solve the above-mentioned problem, the structural feature of the invention according to claim 2 is that the annular groove of the outer ring member is formed in a triangle whose axial cross section has an apex radially outward. is there.

本発明の構成によれば、径方向に深い環状溝を、少ない切削量で、容易に形成することができる。   According to the configuration of the present invention, it is possible to easily form a deep annular groove in the radial direction with a small amount of cutting.

本発明によれば、アンギュラ玉軸受を、ハウジングに組込んだときの、予圧の低下、または、すきまの増加が少なく、回転精度の低下を防止でき、加工が容易な軸受装置を提供することができる。   According to the present invention, it is possible to provide a bearing device that is easy to process, in which an angular ball bearing is assembled in a housing, the decrease in preload or the increase in clearance is small, and the decrease in rotational accuracy can be prevented. it can.

本発明の一実施形態の軸受装置の一部断面図である。It is a partial cross section figure of the bearing apparatus of one Embodiment of this invention. 本発明の一実施形態の軸受装置の主要部の拡大説明図である。It is an expansion explanatory view of the principal part of the bearing device of one embodiment of the present invention. 本発明の一実施形態の軸受装置の作用を説明するＦＥＭ検討図である。It is a FEM examination figure explaining the effect | action of the bearing apparatus of one Embodiment of this invention. 従来の軸受装置の作用を説明するＦＥＭ検討図である。It is a FEM examination figure explaining the effect | action of the conventional bearing apparatus. 本発明の一実施形態の軸受装置の作用を説明する説明図である。It is explanatory drawing explaining an effect | action of the bearing apparatus of one Embodiment of this invention.

この発明の一実施形態の軸受装置を、以下図面を参照して説明する。   A bearing device according to an embodiment of the present invention will be described below with reference to the drawings.

図１は、本発明の一実施形態の軸受装置の断面図である。
図２は、本発明の一実施形態の軸受装置１の主要部の拡大説明図であり、主要部を模式的に示している。図２において、実線は外輪部材２０が、ハウジング６０に固定される前の状態を示している。二点鎖線は外輪部材２０が外輪正面２５を軸方向に押圧され、ハウジング６０に固定された状態を示している。
図１、図２によると、本発明の一実施形態の軸受装置１は、軸部材８０に固定された２個のアンギュラ玉軸受１０と、２個のアンギュラ玉軸受１０を収容するハウジング６０とを有している。 FIG. 1 is a cross-sectional view of a bearing device according to an embodiment of the present invention.
FIG. 2 is an enlarged explanatory view of a main part of the bearing device 1 according to the embodiment of the present invention, and schematically shows the main part. In FIG. 2, the solid line indicates a state before the outer ring member 20 is fixed to the housing 60. An alternate long and two short dashes line indicates a state in which the outer ring member 20 is pressed against the outer ring front surface 25 in the axial direction and fixed to the housing 60.
1 and 2, a bearing device 1 according to an embodiment of the present invention includes two angular ball bearings 10 fixed to a shaft member 80 and a housing 60 that accommodates the two angular ball bearings 10. Have.

アンギュラ玉軸受１０は、内周に外輪軌道２１が形成された外輪部材２０と、外周に内輪軌道３１が形成された内輪部材３０と、前記外輪軌道２１と前記内輪部材３０の内輪軌道３１の間に転動自在に配置された複数の玉４０と、複数の玉４０を保持する保持器４１と、外輪部材２０の内周と内輪部材３０の外周との間の内部空間を密封する２個のシール部材５０と、を有している。   The angular ball bearing 10 includes an outer ring member 20 having an outer ring raceway 21 formed on the inner periphery, an inner ring member 30 having an inner ring raceway 31 formed on the outer periphery, and an outer ring member 31 between the outer ring track 21 and the inner ring member 30. A plurality of balls 40, which are arranged so as to be freely rotatable, a cage 41 for holding the plurality of balls 40, and two inner spaces between the inner periphery of the outer ring member 20 and the outer periphery of the inner ring member 30. And a seal member 50.

外輪部材２０は軸受鋼等の鋼材からなる環体で、内周の軸線方向中間には外輪軌道２１が形成されている。内周部の軸線方向両端部には、それぞれ、径方向外方に凹むシール固定用のシール溝２７、２８が形成されている。外輪軌道２１の大径側の大端部２１ａとシール溝２７の間の領域が外輪カウンター面２３、外輪軌道２１の小径側の小端部２１ｂとシール溝２８の間の領域が外輪肩面２４となっている。   The outer ring member 20 is a ring made of a steel material such as bearing steel, and an outer ring raceway 21 is formed in the middle in the axial direction of the inner periphery. At both ends in the axial direction of the inner peripheral portion, seal fixing seal grooves 27 and 28 that are recessed radially outward are formed, respectively. The region between the large end 21a on the large diameter side of the outer ring raceway 21 and the seal groove 27 is the outer ring counter surface 23, and the region between the small end 21b on the small diameter side of the outer ring raceway 21 and the seal groove 28 is the outer ring shoulder surface 24. It has become.

外輪カウンター面２３には、前記外輪軌道と同心で、軸方向の断面が径方向外方に頂点を有する三角形である環状溝２９が形成されている。環状溝２９の外輪軌道２１側の内側側面２９ａは軸線に直角な平面に、環状溝２９のシール溝２７側の外側側面２９ｂは、軸線方向シール溝２７側が小径、軸線方向内側側面２９ａ側が大径のテーパー面に形成されている。環状溝２９の頂点２９ｃは、断面が内側側面２９ａ、外側側面２９ｂに接する微小な円弧状に形成されている。   The outer ring counter surface 23 is formed with an annular groove 29 that is concentric with the outer ring raceway and is a triangle whose axial cross section has a vertex in the radially outward direction. The inner side surface 29a of the annular groove 29 on the outer ring raceway 21 side is a plane perpendicular to the axis, and the outer side surface 29b of the annular groove 29 on the seal groove 27 side has a small diameter on the axial seal groove 27 side and a large diameter on the axial inner side surface 29a side. It is formed on the taper surface. An apex 29c of the annular groove 29 is formed in a minute arc shape whose cross section is in contact with the inner side surface 29a and the outer side surface 29b.

環状溝２９の頂点２９ｃの最大径ｄ２９は、シール溝２７の最大径ｄ２７より大きい。
また、外輪部材２０の外周は円筒形状の外輪外径面２２となっている。外輪部材２０の両端の側面のうち、外輪カウンター面２３側の側面は外輪正面２５、外輪肩面２４側の側面は外輪背面２６となっている。環状溝２９は、断面が三角形であり、矩形等の断面形状にくらべ、加工工数が少なく加工が容易である。 The maximum diameter d29 of the apex 29c of the annular groove 29 is larger than the maximum diameter d27 of the seal groove 27.
The outer periphery of the outer ring member 20 is a cylindrical outer ring outer diameter surface 22. Of the side surfaces of both ends of the outer ring member 20, the side surface on the outer ring counter surface 23 side is an outer ring front surface 25, and the side surface on the outer ring shoulder surface 24 side is an outer ring rear surface 26. The annular groove 29 has a triangular cross section and has a smaller number of processing steps than a cross section such as a rectangle and is easy to process.

図１において、内輪部材３０は軸受鋼等の鋼材からなる環体で、外周の軸方向中間に、断面が円弧形状の内輪軌道３１が形成されている。内輪軌道３１の両側端部から軸線方向両側に内輪肩面３３が形成されている。両内輪肩面３３の内輪軌道３１と反対側の両端部には径方向内方に凹むシール摺動溝３５が形成されている。   In FIG. 1, an inner ring member 30 is an annulus formed of a steel material such as bearing steel, and an inner ring raceway 31 having an arc-shaped cross section is formed in the middle in the axial direction of the outer periphery. Inner ring shoulder surfaces 33 are formed on both sides in the axial direction from both end portions of the inner ring raceway 31. Seal sliding grooves 35 that are recessed radially inward are formed at both ends of the inner ring shoulder surfaces 33 opposite to the inner ring raceway 31.

保持器４１は強化ポリアミド等の樹脂からなり、射出成型等によって環体に形成され、円周上等配に、複数の玉４０を保持する複数のポケット４２が区画形成されている。
玉４０は軸受鋼等の鋼材からなる球体である。複数の玉４０は保持器４１の複数のポケット４２内にそれぞれ保持され、外輪軌道２１と内輪軌道３１に接して、転動自在に配置されている。 The cage 41 is made of a resin such as reinforced polyamide, and is formed into an annular body by injection molding or the like, and a plurality of pockets 42 for holding a plurality of balls 40 are partitioned and formed on the circumference equally.
The ball 40 is a sphere made of a steel material such as bearing steel. The plurality of balls 40 are respectively held in a plurality of pockets 42 of the cage 41 and are in contact with the outer ring raceway 21 and the inner ring raceway 31 so as to be freely rollable.

２個のシール部材５０は、金属性の芯金５１とアクリル等の合成ゴムからなる環体で、外周端部に合成ゴムからなる固定部５２、内周端部に合成ゴムからなるリップ部５３が形成されている。２個のシール部材５０は、それぞれの固定部５２が、外輪部材２０のシール溝２７、２８に圧入により固定され、それぞれのリップ部５３が内輪部材３０の両側のシール摺動溝３５に摺接して配置されている。   The two seal members 50 are annular members made of a metal core 51 and synthetic rubber such as acrylic, a fixed portion 52 made of synthetic rubber at the outer peripheral end, and a lip portion 53 made of synthetic rubber at the inner peripheral end. Is formed. In the two seal members 50, the fixed portions 52 are fixed by press-fitting into the seal grooves 27 and 28 of the outer ring member 20, and the lip portions 53 are in sliding contact with the seal slide grooves 35 on both sides of the inner ring member 30. Are arranged.

ハウジング６０は、鋼材からなるハウジング本体６１と、鋼材からなるカバー６２を有している。ハウジング本体６１の内周には、円筒穴形状の外輪嵌合面６３が形成されている。外輪嵌合面６３の直径は、２個のアンギュラ玉軸受１０の外輪外径面２２の直径よりわずかに大きい。ハウジング本体６１には、外輪嵌合面６３の一方側の端部から径方向内方に縮径して、本体外輪押え面６４が形成されている。ハウジング本体６１の他方側の側面は、カバー受面６５となっている。   The housing 60 has a housing body 61 made of steel and a cover 62 made of steel. A cylindrical hole-shaped outer ring fitting surface 63 is formed on the inner periphery of the housing body 61. The diameter of the outer ring fitting surface 63 is slightly larger than the diameter of the outer ring outer diameter surface 22 of the two angular ball bearings 10. The housing main body 61 is formed with a main body outer ring pressing surface 64 by reducing the diameter radially inward from one end of the outer ring fitting surface 63. The other side surface of the housing body 61 is a cover receiving surface 65.

本体外輪押え面６４、および、カバー受面６５はいずれも、軸線に直角な平面に形成されている。カバー受面６５には複数の軸線方向のネジ穴６６が、円周上等配に配置されている。
カバー６２は、環状の円板で、一方の側面には、ハウジング本体６１の外輪嵌合面６３の直径より径方向内方に、軸線に直角な平面である、カバー外輪押え面６７が形成されており、本体外輪押え面６４とで、一対の外輪押え面が構成されている。 Both the main body outer ring pressing surface 64 and the cover receiving surface 65 are formed in a plane perpendicular to the axis. A plurality of axial screw holes 66 are arranged on the cover receiving surface 65 at equal intervals on the circumference.
The cover 62 is an annular disk, and a cover outer ring pressing surface 67 that is a plane perpendicular to the axis is formed on one side surface inward in the radial direction from the diameter of the outer ring fitting surface 63 of the housing body 61. The outer ring pressing surface 64 of the main body constitutes a pair of outer ring pressing surfaces.

前記一方の側面のカバー外輪押え面６７の径方向外方には、ハウジング本体６１のカバー受面６５に対峙して、軸線に直角な平面である、合せ面６８が形成されている。カバー６２は、合せ面６８をハウジング本体６１のカバー受面６５上に配置され、合せ面６８には、ハウジング本体６１の複数のネジ穴６６に対峙して、複数の通し穴６９が、円周上等配に形成されている。   A mating surface 68 that is a plane perpendicular to the axis is formed on the outer side of the cover outer ring pressing surface 67 on the one side surface in the radial direction, facing the cover receiving surface 65 of the housing body 61. The cover 62 has a mating surface 68 disposed on the cover receiving surface 65 of the housing body 61, and the mating surface 68 has a plurality of through holes 69 facing the plurality of screw holes 66 of the housing body 61. It is formed in the top level.

２個のアンギュラ玉軸受１０は、２個の外輪部材２０のそれぞれの外輪背面２６を接して配置され、軸部材８に固定されている。ここで、２個のアンギュラ玉軸受１０の内輪部材３０は、内輪内径面３２が軸部材８の外周面８１に嵌合され、一方側の内輪側面３４を軸肩部８２に接し、他方側の内輪側面３４をナット８３で締め付けられている。この状態で、２個のアンギュラ玉軸受１０には、所定の予圧が与えられている。   The two angular ball bearings 10 are arranged in contact with the outer ring back surfaces 26 of the two outer ring members 20 and are fixed to the shaft member 8. Here, the inner ring member 30 of the two angular ball bearings 10 has an inner ring inner surface 32 fitted to the outer peripheral surface 81 of the shaft member 8, the inner ring side surface 34 on one side is in contact with the shaft shoulder portion 82, and the other side. The inner ring side surface 34 is fastened with a nut 83. In this state, a predetermined preload is applied to the two angular ball bearings 10.

また、２個のアンギュラ玉軸受１０の外輪部材２０は、外輪外径面２２が、ハウジング本体６１の外輪嵌合面６３に隙間嵌めで嵌入され、一方側の外輪部材２０の外輪正面２５は、ハウジング本体６１の本体外輪押え面６４に接し、他方側の外輪部材２０の外輪正面２５は、カバー６２のカバー外輪押え面６７に接して配置されている。   Further, the outer ring member 20 of the two angular ball bearings 10 has an outer ring outer diameter surface 22 fitted into the outer ring fitting surface 63 of the housing body 61 with a gap fit, and the outer ring front surface 25 of the outer ring member 20 on one side is The outer ring front surface 25 of the outer ring member 20 on the other side is in contact with the cover outer ring pressing surface 67 of the cover 62 and is in contact with the main body outer ring pressing surface 64 of the housing main body 61.

図２は、図１の他方側の外輪部材２０の外輪正面２５と、カバー６２のカバー外輪押え面６７との関係を示している。図１の一方側の外輪部材２０の外輪正面２５と、ハウジング本体６１の本体外輪押え面６４との関係は、図２と全く同様である。 図２に実線で、外輪部材２０が、ハウジング６０に固定される前の状態が示されている。   FIG. 2 shows the relationship between the outer ring front surface 25 of the outer ring member 20 on the other side of FIG. 1 and the cover outer ring pressing surface 67 of the cover 62. The relationship between the outer ring front surface 25 of the outer ring member 20 on one side of FIG. 1 and the main body outer ring pressing surface 64 of the housing main body 61 is exactly the same as in FIG. The state before the outer ring member 20 is fixed to the housing 60 is shown by a solid line in FIG.

２個のアンギュラ玉軸受１０は、カバー６２の合せ面６８の複数の通し穴６９を挿通し、ハウジング本体６１のカバー受面６５の複数のネジ穴６６に螺合する複数のボルト７０の締付けによってハウジング本体６１に固定される。
図２の二点鎖線は、複数のボルト７０の締付けによって、外輪部材２０の外輪正面２５が軸線方向に押圧され、ハウジング６０に固定された状態を示している。 The two angular ball bearings 10 are inserted by inserting a plurality of through holes 69 in the mating surface 68 of the cover 62 and tightening a plurality of bolts 70 screwed into the plurality of screw holes 66 in the cover receiving surface 65 of the housing body 61. It is fixed to the housing body 61.
The two-dot chain line in FIG. 2 shows a state in which the outer ring front surface 25 of the outer ring member 20 is pressed in the axial direction by fastening a plurality of bolts 70 and fixed to the housing 60.

図２において、外輪部材２０の外輪正面２５が、カバー外輪押え面６７によって軸線方向に押圧されることにより、環状溝２９の頂点２９ｃの外方の外輪外周２２が径方向外方に拡径している。また、環状溝２９、シール溝２７を含む端部が押圧方向に移動し、外輪軌道２１周辺の変形は小さい。   In FIG. 2, the outer ring front surface 25 of the outer ring member 20 is pressed in the axial direction by the cover outer ring pressing surface 67, so that the outer ring outer periphery 22 outside the apex 29 c of the annular groove 29 expands radially outward. ing. Further, the end including the annular groove 29 and the seal groove 27 moves in the pressing direction, and deformation around the outer ring raceway 21 is small.

これは、外輪部材２０の一方のシール溝２７と外輪軌道２１の間に環状溝２９が形成されているため、環状溝２９の頂点２９ｃと外輪外径面２２の間の外方領域に、押圧による圧縮荷重が集中し、環状溝２９の頂点２９ｃを含む外方領域が押圧方向に移動し、外輪軌道２１を含む環状溝２９の頂点２９ｃより径方向内方の領域の応力増加が抑制されるためである。   This is because the annular groove 29 is formed between the one seal groove 27 of the outer ring member 20 and the outer ring raceway 21, so that it is pressed against the outer region between the apex 29 c of the annular groove 29 and the outer ring outer diameter surface 22. The compressive load due to the pressure is concentrated, the outer region including the apex 29c of the annular groove 29 moves in the pressing direction, and the stress increase in the region radially inward from the apex 29c of the annular groove 29 including the outer ring raceway 21 is suppressed. Because.

この結果、外輪軌道２１の玉４０と接触する部位の軸線方向の圧縮変形および、径方向外方への変形は、通常のアンギュラ玉軸受にくらべ小さくなり、外輪部材２０の外輪軌道２１が、玉４０から離れる方向に、大きく変形することはない。すなわち、２個のアンギュラ玉軸受１０の予圧が低下しにくく、予圧の低下による回転精度の低下が少ない。   As a result, axial compression deformation and radial outward deformation of the portion of the outer ring raceway 21 that contacts the ball 40 are smaller than those of a normal angular ball bearing, and the outer ring raceway 21 of the outer ring member 20 There is no significant deformation in the direction away from 40. That is, the preload of the two angular ball bearings 10 is difficult to decrease, and the decrease in rotational accuracy due to the decrease in preload is small.

以下、図３、図４、に基づいて、本発明の実施形態の転がり軸受装置１の作用を詳しく説明する。
図３は、図２の二点鎖線の状態における、アンギュラ玉軸受１０の外輪部材２０のＦＥＭ検討結果の一例を示している。ここで、アンギュラ玉軸受１０は、内径寸法１００ｍｍ、外径寸法１４０ｍｍ、幅寸法２０ｍｍとなっている。 Hereinafter, based on FIG. 3, FIG. 4, the effect | action of the rolling bearing apparatus 1 of embodiment of this invention is demonstrated in detail.
FIG. 3 shows an example of the FEM examination result of the outer ring member 20 of the angular ball bearing 10 in the state of the two-dot chain line in FIG. Here, the angular ball bearing 10 has an inner diameter of 100 mm, an outer diameter of 140 mm, and a width of 20 mm.

図３の検討条件は以下のとおりである。
（１）環状溝２９の頂点２９ｃの直径ｄ２９は、シール溝２７の最大径ｄ２７より大きく、外輪外径面２２の直径ｄ２２と直径ｄ２９の差は、直径ｄ２２と最大径ｄ２７の差の約２／３である。
（２）外輪部材２０は、平板によって軸線方向に３０ｋＮで押圧されている。
また、Ｐは外輪軌道２１と玉４０との接触位置を示している。 The examination conditions in FIG. 3 are as follows.
(1) The diameter d29 of the apex 29c of the annular groove 29 is larger than the maximum diameter d27 of the seal groove 27, and the difference between the diameter d22 and the diameter d29 of the outer ring outer diameter surface 22 is about 2 of the difference between the diameter d22 and the maximum diameter d27. / 3.
(2) The outer ring member 20 is pressed at 30 kN in the axial direction by a flat plate.
P indicates a contact position between the outer ring raceway 21 and the ball 40.

図４は、従来のアンギュラ玉軸受の外輪部材と同一形状、すなわち、環状溝２９を有しないときの、図３の検討条件と同じ諸元、条件での、外輪部材１２０のＦＥＭ検討結果を示している。図４においてＰ１は外輪軌道１２１と玉１３０との接触位置を示している。   FIG. 4 shows the FEM examination result of the outer ring member 120 in the same shape and condition as the examination condition of FIG. 3 when the same shape as the outer ring member of the conventional angular ball bearing, that is, the annular groove 29 is not provided. ing. In FIG. 4, P <b> 1 indicates a contact position between the outer ring raceway 121 and the ball 130.

図４に示すように、従来のアンギュラ玉軸受の外輪部材と同一形状の外輪部材１２０場合、Ｐ１は玉１３０から大きく離れる方向に変形している。しかし、図３における本発明の第１の実施形態の外輪部材２０の場合、外輪正面２５近くの外輪外周面２２の径方向外方への変形はみとめられるが、外輪軌道２１上のＰにおける玉３０から離れる方向への変形は認められない。すなわち、本発明の実施形態のアンギュラ玉軸受１０が外輪正面２５を軸方向に押圧され、ハウジングに固定されたのきの、アンギュラ玉軸受１０の予圧の減少や、すきまの増加は、従来のアンギュラ玉軸受にくらべ、はるかに小さい。   As shown in FIG. 4, in the case of the outer ring member 120 having the same shape as the outer ring member of the conventional angular ball bearing, P <b> 1 is deformed in a direction far away from the ball 130. However, in the case of the outer ring member 20 of the first embodiment of the present invention in FIG. 3, the outer ring outer peripheral surface 22 near the outer ring front surface 25 is deformed radially outward, but the ball at P on the outer ring track 21 Deformation away from 30 is not allowed. That is, when the angular ball bearing 10 according to the embodiment of the present invention is pressed against the outer ring front surface 25 in the axial direction and fixed to the housing, the decrease in the preload and the increase in the clearance of the angular ball bearing 10 are the conventional angular bearings. Much smaller than ball bearings.

図５は、本発明の実施形態の軸受装置１の作用を、従来の軸受装置と比較して、説明する説明図である。図５は、図３、図４の外輪部材２０、１２０のＦＥＭ検討結果を数値として表している。Ｉが図４の従来のアンギュラ玉軸受の外輪部材と同一形状の外輪部材１２０の変位、ＩＩが図３の本発明の実施形態の軸受装置１の外輪部材２０の変位を示している。   FIG. 5 is an explanatory diagram illustrating the operation of the bearing device 1 according to the embodiment of the present invention in comparison with a conventional bearing device. FIG. 5 shows the FEM examination results of the outer ring members 20 and 120 of FIGS. 3 and 4 as numerical values. I represents the displacement of the outer ring member 120 having the same shape as the outer ring member of the conventional angular ball bearing of FIG. 4, and II represents the displacement of the outer ring member 20 of the bearing device 1 of the embodiment of the present invention of FIG.

図５の縦軸は、外輪軌道２１、１２１の玉４０，１４０との接触位置Ｐ、Ｐ１の変位量を示している。図５には、軸線方向の変位量Δａと半径方向の変位量Δｒがプロットされている。軸線方向の変位量Δａは、プラスが圧縮側の変位、マイナスが引張り側の変位を示している。また、半径方向の変位量Δｒは、プラスが拡径側の変位、マイナスが縮径側の変位を示している。   The vertical axis in FIG. 5 indicates the displacement amounts of the contact positions P, P1 of the outer ring raceways 21, 121 with the balls 40, 140. In FIG. 5, the displacement amount Δa in the axial direction and the displacement amount Δr in the radial direction are plotted. With respect to the displacement amount Δa in the axial direction, plus indicates displacement on the compression side, and minus indicates displacement on the tension side. In addition, in the radial displacement amount Δr, plus indicates a displacement on the enlarged diameter side, and minus indicates a displacement on the reduced diameter side.

図５によると従来のアンギュラ玉軸受の外輪部材と同一形状の外輪部材１２０の場合、半径方向の変位量Δｒは拡径側に約１μｍ、軸線方向の変位量Δａは圧縮側に約１．２μｍであり、本発明の実施形態の外輪部材２０場合は半径方向の変位量Δｒは拡径側に約０．８μｍ、軸線方向の変位量Δａは圧縮側に約０．１μｍである。   According to FIG. 5, in the case of the outer ring member 120 having the same shape as the outer ring member of the conventional angular ball bearing, the radial displacement amount Δr is about 1 μm on the enlarged diameter side, and the axial displacement amount Δa is about 1.2 μm on the compression side. In the case of the outer ring member 20 according to the embodiment of the present invention, the radial displacement amount Δr is about 0.8 μm on the diameter expansion side, and the axial displacement amount Δa is about 0.1 μm on the compression side.

ここで、複式のアンギュラ玉軸受が組込まれた、軸受装置の軸線方向の予圧、または、すきまの変化をΔＣ（μｍ）とすると、ΔＣは簡略的に下記式１で表すことができる。αは接触角で、本検討においてはα＝３０°としている。
ΔＣ＝２×（Δｒ／tanα＋Δａ）（μｍ）---式１
従来のアンギュラ玉軸受を用いた軸受け装置の軸線方向の予圧、または、すきまの変化ΔＣ１を、式１にて求めると、ΔＣ１＝２×（１／ｔａｎ３０°＋１．２）＝５．９μｍとなる。すなわち、従来の軸受装置は、上述の検討条件において、５．９μｍの予圧の減少、または、すきまの増加が考えられる。 Here, ΔC (μm) represents ΔC (μm), and ΔC can be simply expressed by the following formula 1, in which a double angular ball bearing is incorporated, and the axial preload or the change in the clearance of the bearing device. α is a contact angle, and α = 30 ° in this study.
ΔC = 2 × (Δr / tan α + Δa) (μm) --- Equation 1
When the preload in the axial direction of a bearing device using a conventional angular ball bearing or the change ΔC1 in the clearance is obtained by Equation 1, ΔC1 = 2 × (1 / tan30 ° + 1.2) = 5.9 μm. . That is, in the conventional bearing device, a decrease in the preload of 5.9 μm or an increase in the clearance can be considered under the above-described examination conditions.

本発明の実施形態の軸受装置１の軸線方向の予圧、または、すきまの変化ΔＣ２を、式１にて求めると、ΔＣ２＝２×（０．８／ｔａｎ３０°＋０．１）＝１．５μｍとなる。すなわち、本発明の実施形態の軸受装置１は、上述の検討条件において、１．５μｍの予圧の増加、または、すきまの減少が考えられる。
上述の計算結果から、本発明の実施形態の軸受装置１は、従来のアンギュラ玉軸受を用いた軸受装置にくらべ、アンギュラ玉軸受の組込みによる、軸線方向の予圧の減少、または、すきまの増加がはるかに小さい。 When the preload in the axial direction of the bearing device 1 of the embodiment of the present invention or the change ΔC2 in the clearance is obtained by Equation 1, ΔC2 = 2 × (0.8 / tan30 ° + 0.1) = 1.5 μm. Become. That is, in the bearing device 1 according to the embodiment of the present invention, an increase in the preload of 1.5 μm or a decrease in the clearance can be considered under the above-described examination conditions.
From the above calculation results, the bearing device 1 according to the embodiment of the present invention has a reduction in the axial preload or an increase in the clearance due to the incorporation of the angular ball bearing, compared to the conventional bearing device using the angular ball bearing. Much smaller.

このように、本発明の実施形態の軸受装置１は、アンギュラ玉軸受１０を、ハウジング６０に組込んだときの、予圧の低下が少なく、回転精度の低下を防止できる。   As described above, the bearing device 1 according to the embodiment of the present invention has a small decrease in preload when the angular ball bearing 10 is incorporated in the housing 60, and can prevent a decrease in rotational accuracy.

上述の実施形態において、環状溝２９は、軸方向の断面が径方向外方に頂点を有する三角形であるが、この発明では、環状溝は、軸方向の断面が矩形等、他の断面形状の環状溝であっても良い。   In the above-described embodiment, the annular groove 29 is a triangle whose axial cross section has an apex radially outward. However, in the present invention, the annular groove has another cross-sectional shape such as a rectangular cross section in the axial direction. An annular groove may be used.

本発明はこうした実施形態に何等限定されるものではなく、本発明の要旨を逸脱しない範囲において、種々なる態様で実施し得ることは当然である。   The present invention is not limited to such embodiments, and can naturally be implemented in various modes without departing from the gist of the present invention.

１ ‥ 軸受装置
１０ ‥ アンギュラ玉軸受
２０、１２０ ‥ 外輪部材
２１、１２１ ‥ 外輪軌道
２１ａ ‥ 大端部
２１ｂ ‥ 小端部
２５ ‥ 側面
２７、２８、１２７、１２８‥ シール溝
２９ ‥ 環状溝
３０ ‥ 内輪部材
３１ ‥ 内輪軌道
４０，１４０ ‥ 玉
５０ ‥ シール部材
６０ ‥ ハウジング
６１ ‥ 外輪嵌合面
６３ ‥ 本体外輪押え面（外輪押え面）
６８ ‥ カバー外輪押え面（外輪押え面）
８０ ‥ 軸部材 DESCRIPTION OF SYMBOLS 1 ... Bearing apparatus 10 ... Angular contact ball bearing 20, 120 ... Outer ring member 21, 121 ... Outer ring raceway 21a ... Large end part 21b ... Small end part 25 ... Side face 27, 28, 127, 128 ... Seal groove 29 ... Annular groove 30 ... Inner ring member 31 ... Inner ring raceway 40, 140 ... Ball 50 ... Seal member 60 ... Housing 61 ... Outer ring fitting surface 63 ... Body outer ring press surface (outer ring press surface)
68 …… Cover outer ring presser surface (outer ring presser surface)
80 ... Shaft member

Claims (2)

アンギュラ玉軸受は、内周に外輪軌道と一対のシール溝が形成された外輪部材と、外周に内輪軌道が形成された内輪部材と、前記外輪軌道と前記内輪軌道の間で転動する複数の玉と、を有し、
ハウジングは、内周に外輪嵌合面と、前記外輪嵌合面の軸線方向両端部から径方向内方に縮径する一対の外輪押え面を有し、
２個の前記アンギュラ玉軸受の、前記内輪部材が軸部材に固定され、前記外輪部材が、前記ハウジングの外輪嵌合面に隙間嵌めで嵌入され、前記外輪部材の側面が、前記一対の外輪押え面によって軸線方向に押圧されて、前記ハウジングに固定される軸受装置であって、
前記外輪軌道は大端部と小端部を有し、一方の前記シール溝と前記外輪軌道の大端部との間の領域に、径方向に拡径する前記外輪軌道と同心の環状溝を有し、前記環状溝の最大径は前記シール溝の最大径より大きく形成されることにより、前記押圧による前記外輪軌道の変形を抑制することを特徴とする転がり軸受装置。 The angular ball bearing includes an outer ring member having an outer ring raceway and a pair of seal grooves formed on the inner periphery, an inner ring member having an inner ring raceway formed on the outer periphery, and a plurality of rollers that roll between the outer ring raceway and the inner ring raceway. A ball,
The housing has an outer ring fitting surface on the inner periphery, and a pair of outer ring holding surfaces that reduce in diameter radially inward from both axial ends of the outer ring fitting surface,
Of the two angular ball bearings, the inner ring member is fixed to a shaft member, the outer ring member is fitted into the outer ring fitting surface of the housing with a gap fit, and the side surfaces of the outer ring member are the pair of outer ring pressers A bearing device that is pressed in an axial direction by a surface and fixed to the housing,
The outer ring raceway has a large end portion and a small end portion, and an annular groove concentric with the outer ring raceway radially expanding in a region between the one seal groove and the large end portion of the outer ring raceway. The rolling bearing device is characterized in that deformation of the outer ring raceway due to the pressing is suppressed by forming a maximum diameter of the annular groove larger than a maximum diameter of the seal groove. 前記外輪部材の前記環状溝は、軸方向の断面が径方向外方に頂点を有する三角形に形成されたことを特徴とする請求項１に記載の転がり軸受装置。   2. The rolling bearing device according to claim 1, wherein the annular groove of the outer ring member is formed in a triangular shape having a cross section in the axial direction having an apex radially outward.
JP2014173507A 2014-08-28 2014-08-28 Bearing device Expired - Fee Related JP6357979B2 (en)

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DE9204957U1 (en) * 1992-04-09 1992-06-11 FAG Kugelfischer Georg Schäfer KGaA, 8720 Schweinfurt Multi-row rolling bearing
JP3419053B2 (en) * 1993-12-17 2003-06-23 日本精工株式会社 Double-row rolling bearing device with preload
JP3582380B2 (en) * 1998-11-05 2004-10-27 トヨタ自動車株式会社 bearing
JP2002089577A (en) * 2000-09-19 2002-03-27 Nsk Ltd Bearing device
JP2003166551A (en) * 2001-11-28 2003-06-13 Ntn Corp Angular contact ball bearing
JP2005003152A (en) * 2003-06-13 2005-01-06 Ntn Corp Ultrathin wall rolling bearing
JP2012163191A (en) * 2011-02-09 2012-08-30 Jtekt Corp Bearing device for wheel hub shaft
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