JP2009103325A - Rolling bearing device - Google Patents

Rolling bearing device Download PDF

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JP2009103325A
JP2009103325A JP2009032702A JP2009032702A JP2009103325A JP 2009103325 A JP2009103325 A JP 2009103325A JP 2009032702 A JP2009032702 A JP 2009032702A JP 2009032702 A JP2009032702 A JP 2009032702A JP 2009103325 A JP2009103325 A JP 2009103325A
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bearing device
rolling bearing
rolling
rolling element
inner ring
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Japanese (ja)
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Masanori Sowa
正典 曽和
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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
    • 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
    • F16C19/50—Other types of ball or roller bearings
    • F16C19/505—Other types of ball or roller bearings with the diameter of the rolling elements of one row differing from the diameter of those of another row
    • 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
    • F16C19/38—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 two or more rows of rollers
    • F16C19/383—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 two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • F16C19/385—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 two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings
    • F16C19/386—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 two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings 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
    • 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
    • F16C2240/80—Pitch circle diameters [PCD]
    • 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
    • F16C2326/00—Articles relating to transporting
    • F16C2326/01—Parts of vehicles in general
    • F16C2326/02—Wheel hubs or castors

Abstract

<P>PROBLEM TO BE SOLVED: To lengthen a service life by enhancing rigidity while avoiding an enlargement of a device, in a rolling bearing device installed in a narrow place. <P>SOLUTION: This rolling bearing device includes an inner ring member 2 having a flange 15 on an outer peripheral surface on one side in the axial direction and having first and second inner ring raceway surfaces 16 and 17 of two rows in the axial direction on an outer peripheral surface on the other side in the axial direction, an outer ring member 1 having first and second outer ring raceway surfaces 12 and 13 of two rows in the axial direction respectively opposed in the radial direction to the first and second inner ring raceway surfaces 16 and 17 of the two rows of the inner ring member 2 on an inner peripheral surface and having a flange 14 on the outer peripheral surface, and first and second rolling element groups 4 and 5 of two rows in the axial direction interposed between the first and second outer ring raceway surfaces 12 and 13 of the outer ring member 1 and the first and second inner ring raceway surfaces 16 and 17 of the inner ring member 2. The relationship between a pitch circle diameter D<SB>1</SB>of the first rolling element group 4 and a pitch circle diameter D<SB>2</SB>of the second rolling element group 5 is set to D<SB>1</SB>>D<SB>2</SB>. The diameter of the respective rolling elements of the first rolling element group 4 is set small, and the rolling element number of the first rolling element group 4 is increased. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

本発明は、車両用や各種産業機器等に適用する転がり軸受装置に関する。   The present invention relates to a rolling bearing device applied to vehicles and various industrial equipment.

図１０を参照してこの種の転がり軸受装置を複列外向きのアンギュラ玉軸受装置に適用して説明する（例えば特許文献１参照）。この複列外向きのアンギュラ玉軸受装置５００は、外輪１と、ハブ軸２と、内輪３と、玉群４、５とを有する。外輪１は、不図示の車体に固定され、内周面に軸方向二列の軌道面１２，１３を有するとともに、車両アウタ側の軌道面の車両インナ側における外周面に前記車体に固定するためのフランジ１４を有する。ハブ軸２は、車両アウタ側の外周面に車輪を取り付けるためのフランジ１５を有するとともに、軸方向中間の外周面に車両アウタ側の軌道面１６を有する。内輪３は、ハブ軸２の車両インナ側の外周面に一体回転可能に嵌合装着され、外周面に車両インナ側の軌道面１７を有する。玉群４，５は、外輪１とハブ軸２と内輪３それぞれの軌道面間において設けられる。   This type of rolling bearing device will be described with reference to FIG. 10 as applied to a double-row outward angular ball bearing device (see, for example, Patent Document 1). This double-row outward angular ball bearing device 500 includes an outer ring 1, a hub shaft 2, an inner ring 3, and ball groups 4 and 5. The outer ring 1 is fixed to a vehicle body (not shown), has two raceways 12 and 13 in the axial direction on the inner peripheral surface, and is fixed to the vehicle body on the outer peripheral surface on the vehicle inner side of the track surface on the vehicle outer side. The flange 14 is provided. The hub shaft 2 has a flange 15 for attaching a wheel to the outer peripheral surface on the vehicle outer side, and has a track surface 16 on the vehicle outer side on the outer peripheral surface in the middle in the axial direction. The inner ring 3 is fitted and mounted on the outer peripheral surface of the hub shaft 2 on the vehicle inner side so as to be integrally rotatable, and has a track surface 17 on the outer side of the vehicle inner side. The ball groups 4 and 5 are provided between the raceways of the outer ring 1, the hub shaft 2 and the inner ring 3.


特開２０００−３８００４号公報JP 2000-38004 A

上記転がり軸受装置５００の場合、設計の容易さや生産コスト低減の観点から、両列の玉群４，５同士が互いの軸方向中間点に対して軸方向左右対称の構造に作られている。このように軸方向左右対称の構造を有する転がり軸受装置５００において、その長寿命化を図る手段の一つとして各列の玉群４，５の軸方向距離やピッチ円直径を大きくすることにより各列の玉群４，５の軸受負荷中心間距離を大きくし、その高剛性化を図ることが考えられる。しかしながら、このような高剛性化構造では、転がり軸受装置全体の寸法が大型化せざるを得なくなる一方、転がり軸受装置５００それ自体が狭隘な車体の一部に取り付けられる構造となっているから、装置を大型化する余地はほとんどない。そのため、従来の転がり軸受装置では、その高剛性化を図ることは困難である。   In the case of the rolling bearing device 500, from the viewpoint of ease of design and reduction in production cost, the ball groups 4 and 5 in both rows are formed in a symmetrical structure in the axial direction with respect to each other in the axial direction. Thus, in the rolling bearing device 500 having a symmetrical structure in the axial direction, each of the ball groups 4 and 5 in each row is increased by increasing the axial distance and pitch circle diameter as one of means for extending the service life. It is conceivable to increase the distance between the bearing load centers of the ball groups 4 and 5 in the row to increase the rigidity. However, in such a highly rigid structure, the size of the entire rolling bearing device is inevitably increased, while the rolling bearing device 500 itself is a structure that can be attached to a part of a narrow vehicle body. There is little room to increase the size of the device. Therefore, it is difficult to increase the rigidity of the conventional rolling bearing device.

したがって、本発明は、狭隘な車体に対して、装置を大型化させることなく高剛性化を図れる構造でもって、転がり軸受装置の長寿命化を図れるようにすることを解決課題とする。   Accordingly, an object of the present invention is to make it possible to extend the life of a rolling bearing device with a structure capable of increasing the rigidity of a narrow vehicle body without increasing the size of the device.

本発明の転がり軸受装置は、軸方向一方側の外周面にフランジを有し、軸方向他方側の外周面に軸方向二列の第１、第２内輪軌道面を有する内輪部材と、内周面に前記内輪部材の二列の第１、第２内輪軌道面と径方向でそれぞれ対向する軸方向二列の第１、第２外輪軌道面を有し、外周面にフランジを有する外輪部材と、前記外輪部材の第１、第２外輪軌道面と前記内輪部材の第１、第２内輪軌道面との間に介装される軸方向二列の第１、第２転動体群とを含み、前記第１転動体群のピッチ円直径Ｄ1と、前記第２転動体群のピッチ円直径Ｄ2との関係が、Ｄ1＞Ｄ2に設定され、前記第１転動体群の各転動体の直径が小さく設定されているとともに、前記第１転動体群の転動体数が増大されている。 A rolling bearing device according to the present invention includes an inner ring member having a flange on the outer peripheral surface on one axial side and two first and second inner ring raceway surfaces in the axial direction on the outer peripheral surface on the other axial side. An outer ring member having two rows of first and second outer ring raceways in the axial direction opposed to the first and second inner ring raceway surfaces in two rows of the inner ring member on the surface, and a flange on the outer peripheral surface; The first and second rolling element groups in two rows in the axial direction interposed between the first and second outer ring raceway surfaces of the outer ring member and the first and second inner ring raceway surfaces of the inner ring member. , the pitch circle diameter D 1 of the first rolling member group, the relationship between the pitch circle diameter D 2 of the second rolling member group is set to D 1> D 2, the rolling of the first rolling element unit The diameter of the moving body is set small, and the number of rolling bodies of the first rolling body group is increased.

また、本発明の転がり軸受装置は、前記第１転動体群の各転動体の直径が、前記第２転動体群の各転動体の直径の８８％よりも小さく、８１％よりも大きく設定されている。   In the rolling bearing device of the present invention, the diameter of each rolling element of the first rolling element group is set to be smaller than 88% and larger than 81% of the diameter of each rolling element of the second rolling element group. ing.

また、本発明の転がり軸受装置は、前記第１転動体群の転動体数が、前記第２転動体群の転動体数の１８２％よりも小さく設定されている。   In the rolling bearing device of the present invention, the number of rolling elements of the first rolling element group is set to be smaller than 182% of the number of rolling elements of the second rolling element group.

また、本発明の転がり軸受装置は、前記Ｄ1と前記Ｄ2との関係が、Ｄ1≦１．４９×Ｄ2に設定されている。 Further, the rolling bearing device of the present invention, the relationship D 1 and the D 2, are set to D 1 ≦ 1.49 × D 2.

ここで、Ｄ1＞Ｄ2の関係は、Ｄ1を大きく設定することにより実現し、Ｄ2は一定とする。 Here, the relationship of D 1 > D 2 is realized by setting D 1 large, and D 2 is constant.

本発明の転がり軸受装置では、内輪部材のフランジと外輪部材のフランジとの間にできる自由空間を有効利用して軸方向一方側の転動体群のピッチ円直径を、軸方向他方側に比べて大きく設定している。そのため、各列の転動体群同士の軸受負荷中心間距離を増大させることができる。その結果、装置の大型化を避けつつ、転がり軸受装置の高剛性化および長寿命化を図ることができる。   In the rolling bearing device of the present invention, the pitch circle diameter of the rolling element group on one side in the axial direction is made larger than that on the other side in the axial direction by effectively utilizing the free space formed between the flange of the inner ring member and the flange of the outer ring member. It is set large. Therefore, the distance between the bearing load centers of the rolling element groups in each row can be increased. As a result, it is possible to increase the rigidity and extend the life of the rolling bearing device while avoiding an increase in the size of the device.

このような構成とした場合、Ｄ1をＤ2よりも大きくしつつ、Ｄ1をＤ2の１４９％以下にとどめている。そのため、拡径スペースを超過して転がり軸受装置が大型化したり、転がり軸受装置の重量や製造コストが上昇するのを最小限度に抑えつつ、転がり軸受装置の高剛性化および長寿命化を図ることができる。なお、前記Ｄ1と前記Ｄ2との関係を１．１０×Ｄ2≦Ｄ1≦１．４９×Ｄ2とすれば、上記作用・効果がより顕著となり好ましい。 In such a configuration, D 1 is made larger than D 2 and D 1 is kept at 149% or less of D 2 . Therefore, to increase the rigidity and extend the life of the rolling bearing device while minimizing the increase in the size of the rolling bearing device beyond the expansion space and the increase in weight and manufacturing cost of the rolling bearing device. Can do. Note that it is preferable that the relationship between D 1 and D 2 is 1.10 × D 2 ≦ D 1 ≦ 1.49 × D 2 , since the above-described operation and effect become more remarkable.

さらに、第１転動体群における転動体の直径が小さく設定されており、それに伴い、転動体の周方向の介装数が多く設定されている。その結果、各転動体群の１個あたりの荷重を分散することができ、転がり軸受装置の剛性をさらに向上させることができる。   Furthermore, the diameter of the rolling elements in the first rolling element group is set to be small, and accordingly, the number of rolling elements interposed in the circumferential direction is set to be large. As a result, the load per one rolling element group can be distributed, and the rigidity of the rolling bearing device can be further improved.

以上説明したように、本発明の転がり軸受装置によれば、車輪が取り付けられる内輪部材のフランジと、車体に固定される外輪部材のフランジとの間にできる自由空間を有効利用して車両アウタ側の転動体のピッチ円直径を大きく設定している。これにより、装置の大型化を避けつつ各列の転動体の軸受負荷中心間距離を増大させると同時に、転動体の介装数を多くすることができる。その結果、転がり軸受装置の剛性が向上し、その長寿命化を図ることができる。   As described above, according to the rolling bearing device of the present invention, the free space formed between the flange of the inner ring member to which the wheel is attached and the flange of the outer ring member fixed to the vehicle body can be effectively used to make the vehicle outer side. The pitch circle diameter of the rolling element is set large. As a result, the distance between the bearing load centers of the rolling elements in each row can be increased while avoiding an increase in the size of the apparatus, and at the same time, the number of interposed rolling elements can be increased. As a result, the rigidity of the rolling bearing device can be improved and its life can be extended.

本発明の参考例に係る転がり軸受装置の全体構成を示す断面図Sectional drawing which shows the whole structure of the rolling bearing apparatus which concerns on the reference example of this invention 図１の転がり軸受装置の上半分断面図Cross section of the upper half of the rolling bearing device of FIG. 本発明の実施形態に係る転がり軸受装置の全体構成を示す断面図Sectional drawing which shows the whole structure of the rolling bearing apparatus which concerns on embodiment of this invention. 図３の転がり軸受装置の上半分断面図Cross-sectional view of the upper half of the rolling bearing device of FIG. 車両アウタ側の玉の配列を示す説明図Explanatory drawing showing the arrangement of balls on the vehicle outer side 本発明の他の実施形態に係る転がり軸受装置の全体構成を示す断面図Sectional drawing which shows the whole structure of the rolling bearing apparatus which concerns on other embodiment of this invention. 本発明の他の実施形態に係る転がり軸受装置の全体構成を示す断面図Sectional drawing which shows the whole structure of the rolling bearing apparatus which concerns on other embodiment of this invention. 本発明の他の実施形態に係る転がり軸受装置の上半分を示す断面図Sectional drawing which shows the upper half of the rolling bearing apparatus which concerns on other embodiment of this invention. 本発明の他の実施形態に係る転がり軸受装置の上半分を示す断面図Sectional drawing which shows the upper half of the rolling bearing apparatus which concerns on other embodiment of this invention. 従来の転がり軸受装置の全体構成を示す断面図Sectional drawing which shows the whole structure of the conventional rolling bearing apparatus

以下、本発明の参考例に係る転がり軸受装置を、図面を参照して詳細に説明する。この転がり軸受装置は、車両用車軸の軸受用に適用して説明する。この転がり軸受装置は、従動輪側を例にとっている。図１は本発明の参考例に係る転がり軸受装置の全体構成を示す断面図、図２は、図１の転がり軸受装置の上半分断面図である。図１で軸方向左側は車両アウタ側（軸方向一方側）を、軸方向右側は車両インナ側（軸方向他方側）を示す。   Hereinafter, a rolling bearing device according to a reference example of the present invention will be described in detail with reference to the drawings. This rolling bearing device will be described as applied to a bearing for a vehicle axle. This rolling bearing device takes the driven wheel side as an example. FIG. 1 is a cross-sectional view showing the overall configuration of a rolling bearing device according to a reference example of the present invention, and FIG. 2 is a cross-sectional view of the upper half of the rolling bearing device of FIG. In FIG. 1, the left side in the axial direction shows the vehicle outer side (one side in the axial direction), and the right side in the axial direction shows the vehicle inner side (the other side in the axial direction).

図例の転がり軸受装置１００は、複列外向きアンギュラ玉軸受装置として、外輪１と、ハブ軸２と、内輪３と、一対の玉群４，５と、一対の保持器６，７と、一対のシール部材８，９とを有する。   The rolling bearing device 100 of the illustrated example is an outer ring 1, a hub shaft 2, an inner ring 3, a pair of ball groups 4, 5, and a pair of cages 6, 7, as a double-row outward angular ball bearing device. A pair of seal members 8 and 9 are provided.

外輪１は、外輪部材として、内周面に軸方向二列の軌道面１２，１３を有するとともに、車両アウタ側の軌道面１２の車両インナ側における外周面に車両（不図示）に固定するためのフランジ１４を有する。   The outer ring 1 has, as outer ring members, two raceways 12 and 13 in the axial direction on the inner circumferential surface, and is fixed to a vehicle (not shown) on the outer circumferential surface on the vehicle inner side of the raceway surface 12 on the vehicle outer side. The flange 14 is provided.

ハブ軸２は、内輪部材の一部分として、車両アウタ側の外周面に車輪（不図示）を取り付けるためのフランジ１５を有するとともに、軸方向中間の外周面に外輪１の車両アウタ側の軌道面１２と対向する一列の軌道面１６を有する。内輪３は、内輪部材の一部分として、ハブ軸２における車両インナ側の外周面に該ハブ軸２と一体回転可能に嵌合装着され、外周面に外輪１の車両インナ側の軌道面１３と対向する一列の軌道面１７を有する。   As a part of the inner ring member, the hub axle 2 has a flange 15 for attaching a wheel (not shown) to the outer peripheral surface on the vehicle outer side, and the outer peripheral track surface 12 of the outer ring 1 on the outer peripheral surface in the axial direction. And a row of raceway surfaces 16 facing each other. As a part of the inner ring member, the inner ring 3 is fitted and mounted on the outer peripheral surface of the hub shaft 2 on the vehicle inner side so as to be integrally rotatable with the hub shaft 2, and faces the raceway surface 13 of the outer ring 1 on the vehicle inner side. And a row of raceway surfaces 17.

玉群４，５は、転動体として、外輪１の軌道面１２，１３とハブ軸２および内輪３の各軌道面１６，１７との間において軸方向に二列介装される。   The ball groups 4 and 5 are interposed as two rolling elements in the axial direction between the raceway surfaces 12 and 13 of the outer ring 1 and the raceway surfaces 16 and 17 of the hub shaft 2 and the inner ring 3.

一対の保持器６，７それぞれは、各列の玉群４，５を保持する。   Each of the pair of cages 6 and 7 holds a group of balls 4 and 5 in each row.

各列のシール部材８，９は、外輪１の内周の軸方向両側において、外輪１とハブ軸２との間、外輪１と内輪３との間それぞれの環状空間を軸方向で仕切っており、当該環状空間内にグリースを密封している。   The seal members 8 and 9 in each row partition the annular spaces between the outer ring 1 and the hub shaft 2 and between the outer ring 1 and the inner ring 3 in the axial direction on both axial sides of the inner circumference of the outer ring 1. The grease is sealed in the annular space.

ハブ軸２の車両インナ側端部は、内輪３の外端面に対してかしめられており、かしめ部１０を形成する。このかしめによりハブ軸２と内輪３は一体回転可能になるとともに、転がり軸受装置１００に対して所要の予圧が付与される。   The vehicle inner side end portion of the hub axle 2 is caulked against the outer end surface of the inner ring 3 to form a caulking portion 10. By this caulking, the hub shaft 2 and the inner ring 3 can rotate together and a required preload is applied to the rolling bearing device 100.

本参考例では、次の構成を有することを特徴とする。すなわち、上述した構成を有する転がり軸受装置１００の場合、外輪１のフランジ１４の車両インナ側が車両の一部であるナックル（不図示）に固定され、ハブ軸２のフランジ１５の車両アウタ側に車輪（不図示）が取り付けられる。このとき、外輪１のフランジ１４とハブ軸２のフランジ１５との間には環状の自由空間１１が存在する。本実施形態では、この環状の自由空間１１に着目して、図１に示すように、車両アウタ側の玉群４のピッチ円直径Ｄ1と、車両インナ側の玉群５のピッチ円直径Ｄ2との関係をＤ1＞Ｄ2に設定している。但し、このＤ1＞Ｄ2の関係は、Ｄ1を大きく設定することにより実現し、Ｄ2は一定とする。これに伴い、ハブ軸２の軌道面１６を内輪３の軌道面１７よりも拡径し、あわせて外輪１の車両アウタ側の軌道面１２を車両インナ側の軌道面１３よりも拡径している。 This reference example is characterized by having the following configuration. That is, in the case of the rolling bearing device 100 having the above-described configuration, the vehicle inner side of the flange 14 of the outer ring 1 is fixed to a knuckle (not shown) that is a part of the vehicle, and the wheel is connected to the vehicle outer side of the flange 15 of the hub shaft 2. (Not shown) is attached. At this time, an annular free space 11 exists between the flange 14 of the outer ring 1 and the flange 15 of the hub axle 2. In this embodiment, by paying attention to the free space 11 of the annular, as shown in FIG. 1, the pitch circle diameter D 1 of the ball group 4 of the vehicle outer side, the pitch circle diameter D of the ball group 5 of the vehicle inner side 2 is set such that D 1 > D 2 . However, this relationship of D 1 > D 2 is realized by setting D 1 large, and D 2 is constant. Along with this, the diameter of the raceway surface 16 of the hub axle 2 is made larger than that of the raceway surface 17 of the inner ring 3, and the raceway surface 12 on the outer side of the outer ring 1 is made larger than the raceway surface 13 on the vehicle inner side. Yes.

このように、Ｄ1＞Ｄ2に設定することにより、転がり軸受装置１００の剛性が向上する。以下、Ｄ1＞Ｄ2に設定することと、転がり軸受装置１００の剛性向上との因果関係を説明する。 Thus, the rigidity of the rolling bearing device 100 is improved by setting D 1 > D 2 . Hereinafter, a causal relationship between setting D 1 > D 2 and improving the rigidity of the rolling bearing device 100 will be described.

図２において、Ｄ1＝Ｄ2としたとき（図中の点線）の各列の玉群４，５の中心からハブ軸２および内輪３の各軌道面１６，１７に加わる力の作用方向を示す作用線をそれぞれＦ1，Ｆ2とし、これらと転がり軸受装置１００の中心軸線Ｏとの交点をそれぞれＯ1，Ｏ2とする。一方、Ｄ1＞Ｄ2としたときの車両アウタ側の玉群４の中心からハブ軸２の軌道面１６に加わる力の作用方向を示す作用線をＦ3とし、これと転がり軸受装置１００の中心軸線Ｏとの交点をＯ3とする。このとき、交点Ｏ1，Ｏ2間の距離をＬ1とし、交点Ｏ1，Ｏ3間の距離をＬ2とすると、Ｌ2＞Ｌ1の関係となる。 In FIG. 2, when D 1 = D 2 (dotted line in the figure), the acting direction of force applied to the raceway surfaces 16 and 17 of the hub shaft 2 and the inner ring 3 from the center of the ball groups 4 and 5 in each row is shown. The acting lines shown are F 1 and F 2 , respectively, and the intersections of these with the central axis O of the rolling bearing device 100 are O 1 and O 2 , respectively. On the other hand, an action line indicating the action direction of the force applied to the raceway surface 16 of the hub shaft 2 from the center of the ball group 4 on the vehicle outer side when D 1 > D 2 is set as F 3, and this and the rolling bearing device 100 The intersection with the central axis O is defined as O 3 . At this time, assuming that the distance between the intersections O 1 and O 2 is L 1 and the distance between the intersections O 1 and O 3 is L 2 , the relation of L 2 > L 1 is established.

これらの距離Ｌ1，Ｌ2は、軸受負荷中心間距離を示しており、これらＬ1，Ｌ2が大きいほど、転がり軸受装置１００の剛性が大きくなる。したがって、Ｄ1＞Ｄ2に設定することにより、軸受負荷中心間距離が増大し、転がり軸受装置１００の剛性を向上させることができ、ひいては転がり軸受装置１００の長寿命化につながる。 These distances L 1 and L 2 indicate the distance between the bearing load centers. The larger L 1 and L 2 are, the greater the rigidity of the rolling bearing device 100 is. Therefore, by setting D 1 > D 2 , the distance between the bearing load centers can be increased, the rigidity of the rolling bearing device 100 can be improved, and the life of the rolling bearing device 100 can be extended.

ところで、Ｄ1＞Ｄ2に設定すると、当該玉群４の周方向における介装スペースが増大する。その分、玉群４の介装数を増やすことにより、玉４の一個当たりの荷重を分散することができるので、転がり軸受装置１００の剛性および寿命をさらに向上させることができる。 However, when set to D 1> D 2, interposed space in the circumferential direction of the ball group 4 is increased. Accordingly, the load per ball 4 can be dispersed by increasing the number of interpositions of the ball group 4, so that the rigidity and life of the rolling bearing device 100 can be further improved.

以下、Ｄ1および玉群４の介装数の最適な設定について試験により検証しているので、説明する。 Hereinafter, the optimum setting of the number of interventions of D 1 and the ball group 4 is verified by a test, and will be described.

この試験に用いた転がり軸受装置１００は、車両インナ側の玉５について、Ｄ2＝４９ｍｍ、直径は１２．７ｍｍ、介装数は１１個とし、車両アウタ側の玉４については、その直径を玉５と同じ１２．７ｍｍとした。この試験では、車両アウタ側の玉４について、Ｄ1および介装数をいろいろ変化させて転がり軸受装置１００の剛性および寿命を確認した。従来例としては、玉４，５について、Ｄ1＝Ｄ2＝４９ｍｍ、直径は共に１２．７ｍｍ、介装数は共に１１個に設定した。 The rolling bearing device 100 used for this test is such that the ball 5 on the vehicle inner side has D 2 = 49 mm, the diameter is 12.7 mm, the number of intervention is 11, and the ball 4 on the vehicle outer side has a diameter of It was 12.7 mm which is the same as the ball 5. In this test, the rigidity and life of the rolling bearing device 100 were confirmed for the balls 4 on the vehicle outer side by changing D 1 and the number of interventions in various ways. As a conventional example, for balls 4 and 5, D 1 = D 2 = 49 mm, both diameters were set to 12.7 mm, and the number of interventions was set to 11 pieces.

転がり軸受装置１００の剛性は、転がり軸受装置１００に径方向に一定の荷重をかけたときの転がり軸受装置１００の傾きを計測して確認し、寿命は、転がり軸受装置１００を回転させ寿命に至るまでの走行距離を計測して確認する。なお、転がり軸受装置１００の剛性を示す傾き（単位：分）は、その値が小さいほど転がり軸受装置１００の剛性が高いことを示しており、転がり軸受装置１００の寿命を示す走行距離（単位：万ｋｍ）は、その値が大きいほど転がり軸受装置１００の寿命が長いことを示す。   The rigidity of the rolling bearing device 100 is confirmed by measuring the inclination of the rolling bearing device 100 when a constant load is applied to the rolling bearing device 100 in the radial direction, and the life is reached by rotating the rolling bearing device 100. Measure the distance traveled up to and check. In addition, the inclination (unit: minute) which shows the rigidity of the rolling bearing apparatus 100 has shown that the rigidity of the rolling bearing apparatus 100 is so high that the value is small, and the travel distance (unit: unit) which shows the lifetime of the rolling bearing apparatus 100. 10,000 km) indicates that the larger the value is, the longer the life of the rolling bearing device 100 is.

Figure 2009103325
Figure 2009103325

表１において、試料１では、Ｄ1をＤ2の１１０％とし、玉４の介装数を玉５と同じ１１個としている。この場合、転がり軸受装置１００は、従来例との比較において、剛性が９８％と向上しており、寿命も玉４側が１０８％、玉５側が１０７％と向上している。 In Table 1, in Sample 1, D 1 is 110% of D 2 and the number of balls 4 interposed is 11 which is the same as balls 5. In this case, in the rolling bearing device 100, the rigidity is improved to 98% in comparison with the conventional example, and the life is also improved to 108% on the ball 4 side and 107% on the ball 5 side.

試料２では、Ｄ1をＤ2の１４９％とし、玉４の介装数を１６個としている。この場合、転がり軸受装置１００は、従来例との比較において、剛性が８４％と向上しており、寿命も玉４側が２５７％、玉５側が１２１％と向上している。しかも、試料１との比較においても、剛性、寿命ともに向上している。 In sample 2, D 1 is 149% of D 2 , and the number of balls 4 is 16. In this case, in the rolling bearing device 100, the rigidity is improved to 84% in comparison with the conventional example, and the life is improved to 257% on the ball 4 side and 121% on the ball 5 side. Moreover, both the rigidity and the life are improved in comparison with the sample 1.

ただし、Ｄ1をＤ2の１４９％より大きく設定すると、転がり軸受装置１００の大型化、重量化の問題があるため、Ｄ1はＤ2の１４９％以下に設定するのが好ましい。 However, if D 1 is set larger than 149% of D 2 , there is a problem of an increase in the size and weight of the rolling bearing device 100. Therefore, D 1 is preferably set to 149% or less of D 2 .

以上より、１．１０×Ｄ2≦Ｄ1≦１．４９×Ｄ2に設定するのが好ましく、さらには、Ｄ1＝１．４９×Ｄ2、つまりＤ1＝７３ｍｍに設定すれば、剛性、寿命ともに優れた転がり軸受装置１００とすることができる。 From the above, it is preferable to set 1.10 × D 2 ≦ D 1 ≦ 1.49 × D 2 , and further, if D 1 = 1.49 × D 2 , that is, D 1 = 73 mm, rigidity is set. In addition, the rolling bearing device 100 having an excellent lifetime can be obtained.

以上のように、本参考例では、車両アウタ側の玉群４のピッチ円直径を大きく設定している。そのため、外輪１のフランジ１４と内輪３のフランジ１５との間に生じるスペースを有効に活用して転がり軸受装置１００における玉群４，５の互いの軸受負荷中心間距離を増大させることができ、転がり軸受装置１００の剛性を向上させることができる。しかも、車両アウタ側の玉群４の周方向における介装スペースも増大するため、その分、玉群４の介装数を増やすことができ、転がり軸受装置１００の剛性をさらに向上させることができる。   As described above, in this reference example, the pitch circle diameter of the ball group 4 on the vehicle outer side is set large. Therefore, the space generated between the flange 14 of the outer ring 1 and the flange 15 of the inner ring 3 can be effectively utilized to increase the distance between the bearing load centers of the ball groups 4 and 5 in the rolling bearing device 100, The rigidity of the rolling bearing device 100 can be improved. In addition, since the interposing space in the circumferential direction of the ball group 4 on the vehicle outer side is also increased, the number of intervening ball groups 4 can be increased correspondingly, and the rigidity of the rolling bearing device 100 can be further improved. .

なお、本発明は、上述の参考例に限定されるものではなく、以下に述べる実施形態にも適用可能である。   In addition, this invention is not limited to the above-mentioned reference example, It can apply also to embodiment described below.

（１）図３は、本発明の実施形態に係る転がり軸受装置の全体構成を示す断面図、図４は、図３の転がり軸受装置の上半分断面図、図５は、車両アウタ側の玉の配列を示す説明図である。図３で軸方向左側は車両アウタ側（軸方向一方側）を、軸方向右側は車両インナ側（軸方向他方側）を示す。   (1) FIG. 3 is a sectional view showing the overall configuration of the rolling bearing device according to the embodiment of the present invention, FIG. 4 is a sectional view of the upper half of the rolling bearing device of FIG. 3, and FIG. It is explanatory drawing which shows the arrangement | sequence. In FIG. 3, the left side in the axial direction indicates the vehicle outer side (one side in the axial direction), and the right side in the axial direction indicates the inner side of the vehicle (the other side in the axial direction).

図３に示す転がり軸受装置１００の基本的構成は、上記参考例と同様であるが、異なる点は、車両アウタ側の玉４の直径を小さくしている点である。これに伴い、ハブ軸２の軌道面１６は、上記参考例よりもさらに径方向外側に拡径する。   The basic configuration of the rolling bearing device 100 shown in FIG. 3 is the same as that of the reference example described above, but is different in that the diameter of the ball 4 on the vehicle outer side is reduced. As a result, the raceway surface 16 of the hub shaft 2 expands further radially outward than the reference example.

このように、上記参考例に加えて、車両アウタ側の玉４の直径を小さくすることによっても、転がり軸受装置１００の剛性が向上する。以下、車両アウタ側の玉４の直径の縮小と、転がり軸受装置１００の剛性向上との因果関係を説明する。   Thus, in addition to the above reference example, the rigidity of the rolling bearing device 100 is also improved by reducing the diameter of the balls 4 on the vehicle outer side. Hereinafter, a causal relationship between the reduction in the diameter of the ball 4 on the vehicle outer side and the improvement in the rigidity of the rolling bearing device 100 will be described.

図４において、車両アウタ側の玉４の直径を小さくしないとき（図中の点線）の各列の玉群４，５の中心から内輪およびハブ軸の各軌道面１６，１７に加わる力の作用方向を示す作用線をそれぞれＦ1，Ｆ3とし、これらと転がり軸受装置１００の中心軸線Ｏとの交点をそれぞれＯ1，Ｏ3とする。一方、車両アウタ側の玉４の直径を小さくしたときのこの車両アウタ側の玉群４の中心からハブ軸２の軌道面１６に加わる力の作用方向を示す作用線をＦ4とし、これと転がり軸受装置１００の中心軸線Ｏとの交点をＯ4とする。このとき、交点Ｏ1，Ｏ3間の距離をＬ2とし、交点Ｏ1，Ｏ4間の距離をＬ3とすると、Ｌ3＞Ｌ2の関係となる。 In FIG. 4, when the diameter of the balls 4 on the vehicle outer side is not reduced (dotted line in the figure), the action of the force applied to the raceways 16, 17 of the inner ring and the hub axle from the center of the ball groups 4, 5 in each row. The action lines indicating the directions are F 1 and F 3 , respectively, and the intersections between these and the central axis O of the rolling bearing device 100 are O 1 and O 3 , respectively. On the other hand, when the diameter of the ball 4 on the vehicle outer side is reduced, the line of action indicating the direction of action of the force applied to the raceway surface 16 of the hub shaft 2 from the center of the ball group 4 on the vehicle outer side is F 4. An intersection point with the central axis O of the rolling bearing device 100 is defined as O 4 . At this time, if the distance between the intersections O 1 and O 3 is L 2 and the distance between the intersections O 1 and O 4 is L 3 , the relationship L 3 > L 2 is established.

既に説明したように、これらの距離Ｌ2，Ｌ3は、軸受負荷中心間距離を示しており、これらＬ2，Ｌ3が大きいほど、転がり軸受装置１００の剛性が大きくなる。したがって、車両アウタ側の玉４の直径を小さくすることにより、上記実施形態に比べてさらに軸受負荷中心間距離の増大を図ることができ、転がり軸受装置１００の剛性をさらに向上させることができる。 As already described, these distances L 2 and L 3 indicate the distance between the bearing load centers, and the larger L 2 and L 3 are, the greater the rigidity of the rolling bearing device 100 is. Therefore, by reducing the diameter of the balls 4 on the vehicle outer side, the distance between the bearing load centers can be further increased as compared with the above embodiment, and the rigidity of the rolling bearing device 100 can be further improved.

さらに、以上のように車両アウタ側の玉４の直径を小さくすることにより、上記参考例に比べてさらに車両アウタ側の玉群４の周方向における介装数を増やすことができる。図５に示すように、玉４の直径を小さくすると、周方向に隣り合う玉４同士の配置間隔を狭めることができるので、玉４の介装数を増やすことができる。これにより、玉一個当たりの荷重を分散することができ、転がり軸受装置１００の剛性がさらに向上する。   Furthermore, by reducing the diameter of the balls 4 on the vehicle outer side as described above, it is possible to further increase the number of interventions in the circumferential direction of the ball group 4 on the vehicle outer side compared to the above reference example. As shown in FIG. 5, when the diameter of the balls 4 is reduced, the arrangement interval between the balls 4 adjacent to each other in the circumferential direction can be reduced, so that the number of interposed balls 4 can be increased. Thereby, the load per ball | bowl can be disperse | distributed and the rigidity of the rolling bearing apparatus 100 further improves.

ただし、玉４の直径を小さくするにつれ、転がり軸受装置１００の剛性は向上するものの、寿命は低下する傾向にある。そのため、玉４の直径は、従来例に比べて転がり軸受装置１００の寿命が低下しない範囲で適切に設定する必要がある。   However, as the diameter of the balls 4 is reduced, the life of the rolling bearing device 100 tends to be reduced, although the rigidity of the rolling bearing device 100 is improved. Therefore, it is necessary to set the diameter of the ball 4 appropriately within a range in which the life of the rolling bearing device 100 is not reduced as compared with the conventional example.

以下、玉４の直径および介装数の最適な設定について試験により検証しているので説明する。この試験に用いた転がり軸受装置１００は、車両インナ側の玉５について、Ｄ2＝４９ｍｍ、直径は１２．７ｍｍ、介装数は１１個とする。車両アウタ側の玉４について、Ｄ1は、上記実施形態での試験の結果に基づき、転がり軸受装置１００の剛性、寿命ともに最も向上するＤ1＝７３ｍｍに設定した。この試験では、車両アウタ側の玉４について、直径および介装数をいろいろ変化させて転がり軸受装置１００の剛性および転がり寿命を確認した。従来例としては、玉４，５について、Ｄ1＝Ｄ2＝４９ｍｍ、直径は共に１２．７ｍｍ、介装数は共に１１個に設定した。なお、転がり軸受装置１００の剛性および寿命の測定方法は上記実施形態と同様である。 Hereinafter, the optimum setting of the diameter and the number of interventions of the balls 4 is verified by a test and will be described. In the rolling bearing device 100 used in this test, D 2 = 49 mm, the diameter is 12.7 mm, and the number of intervention is 11 for the ball 5 on the vehicle inner side. With respect to the ball 4 on the vehicle outer side, D 1 is set to D 1 = 73 mm, which improves the rigidity and life of the rolling bearing device 100 most, based on the test results in the above embodiment. In this test, for the balls 4 on the vehicle outer side, the rigidity and the rolling life of the rolling bearing device 100 were confirmed by changing the diameter and the number of interventions. As a conventional example, for balls 4 and 5, D 1 = D 2 = 49 mm, both diameters were set to 12.7 mm, and the number of interventions was set to 11 pieces. The method for measuring the rigidity and life of the rolling bearing device 100 is the same as in the above embodiment.

Figure 2009103325
Figure 2009103325

表２において、試料１では、玉４の直径を玉５の直径の８８％としており、玉４の介装数を１８個としている。この場合、従来例との比較で、剛性は８４％と向上しており、寿命も玉４側が１４７％、玉５側が１２０％といずれも向上している。   In Table 2, in the sample 1, the diameter of the ball 4 is 88% of the diameter of the ball 5, and the number of interposed balls 4 is 18. In this case, compared with the conventional example, the rigidity is improved to 84%, and the lifetime is improved to 147% on the ball 4 side and 120% on the ball 5 side.

試料２では、玉４の直径を玉５の直径の８１％としており、玉４の介装数を２０個としている。この場合も、従来例との比較で、剛性は８３％と向上しており、寿命も玉４側が１１５％、玉５側が１１７％といずれも向上している。ちなみにこの場合、玉４側の寿命が試料１に比べて低下している。   In the sample 2, the diameter of the balls 4 is 81% of the diameter of the balls 5, and the number of interposed balls 4 is 20. Also in this case, compared with the conventional example, the rigidity is improved to 83%, and the lifetime is improved to 115% on the ball 4 side and 117% on the ball 5 side. Incidentally, in this case, the life on the ball 4 side is shorter than that of the sample 1.

試料３では、玉４の直径を玉５の直径の７５％としており、玉４の介装数を２１個としている。この場合、従来例との比較で、剛性は８２％と向上している。しかし、寿命は、従来例との比較で、玉５側が１１７％と向上しているのに対して、玉４側が７８％と低下している。   In the sample 3, the diameter of the ball 4 is 75% of the diameter of the ball 5, and the number of interposed balls 4 is 21. In this case, the rigidity is improved to 82% as compared with the conventional example. However, in comparison with the conventional example, the life is improved to 117% on the ball 5 side, and is reduced to 78% on the ball 4 side.

以上より、玉４の直径の下限値は、Ｄ1＝７３ｍｍとしたとき、玉５の直径の８１％、すなわち約１０．３２ｍｍとするのが好ましく、さらには、玉４の直径を約１０．３２ｍｍ、玉４の介装数を２０個に設定すると、極めて剛性が高く、しかも長寿命な転がり軸受装置１００とすることができる。 From the above, the lower limit of the diameter of the ball 4 is preferably 81% of the diameter of the ball 5, that is, about 10.32 mm when D 1 = 73 mm, and further, the diameter of the ball 4 is about 10.4 mm. If the number of interventions of 32 mm and balls 4 is set to 20, the rolling bearing device 100 having extremely high rigidity and a long life can be obtained.

以上のように、上記参考例に加えて、車両アウタ側の玉４の直径を小さくすることによって、転がり軸受装置１００における軸受負荷中心間距離をさらに増大させることができるので、転がり軸受装置１００のさらなる剛性化を図ることができる。また、車両アウタ側の玉群４の周方向の介装数を多くすることができるので、転がり軸受装置１００の剛性がさらに向上する。   As described above, in addition to the above reference example, the distance between the bearing load centers in the rolling bearing device 100 can be further increased by reducing the diameter of the balls 4 on the vehicle outer side. Further rigidity can be achieved. In addition, since the number of interposed balls 4 on the vehicle outer side in the circumferential direction can be increased, the rigidity of the rolling bearing device 100 is further improved.

（２）図６は、本発明のさらに他の実施形態に係る転がり軸受装置の全体構成を示す断面図である。   (2) FIG. 6 is a cross-sectional view showing an overall configuration of a rolling bearing device according to still another embodiment of the present invention.

図６において、図１から図２と対応する部分には同一の符号を付しており、その同一の符号に係る部分の詳しい説明は省略する。図６で軸方向左側は車両アウタ側（軸方向一方側）を、軸方向右側は車両インナ側（軸方向他方側）を示す。   6, parts corresponding to those in FIGS. 1 to 2 are denoted by the same reference numerals, and detailed description of the parts related to the same reference numerals is omitted. In FIG. 6, the left side in the axial direction shows the vehicle outer side (one side in the axial direction), and the right side in the axial direction shows the vehicle inner side (the other side in the axial direction).

転がり軸受装置２００は、内輪部材としてハブホイール４３と等速ジョイント４０とを有する。   The rolling bearing device 200 includes a hub wheel 43 and a constant velocity joint 40 as inner ring members.

この転がり軸受装置２００においても、外輪部材として外輪１、これと同心に配置された内輪部材としてハブホイール４３および等速ジョイントの軸部４２とを有する。   This rolling bearing device 200 also has an outer ring 1 as an outer ring member, and a hub wheel 43 and a shaft portion 42 of a constant velocity joint as inner ring members arranged concentrically therewith.

外輪１は、内周面に軸方向二列の軌道面１２，１３を有するとともに、車両アウタ側の軌道面１２の車両インナ側における外周面に車両（不図示）に固定するためのフランジ１４を有する。   The outer ring 1 has two axial rows of raceway surfaces 12 and 13 on the inner circumferential surface, and a flange 14 for fixing to a vehicle (not shown) on the outer circumferential surface of the raceway surface 12 on the vehicle outer side on the vehicle inner side. Have.

ハブホイール４３は、車両アウタ側外周面に車輪（不図示）を取り付けるためのフランジ１５を有するとともに、車両インナ側の外周面に一列の軌道面１６を有する。   The hub wheel 43 has a flange 15 for attaching a wheel (not shown) to the outer peripheral surface of the vehicle outer side, and a row of track surfaces 16 on the outer peripheral surface of the vehicle inner side.

等速ジョイント４０は、車両インナ側に椀形外輪４１を、車両アウタ側に軸部４２をそれぞれ有する。軸部４２は、車両インナ側の外周面に一列の軌道面１７を有し、車両アウタ側の外周面に対してハブホイール４３が一体回転可能に嵌合装着される。なお、椀形外輪４１の内部詳細は省略する。   The constant velocity joint 40 has a bowl-shaped outer ring 41 on the vehicle inner side and a shaft portion 42 on the vehicle outer side. The shaft portion 42 has a row of track surfaces 17 on the outer peripheral surface on the vehicle inner side, and the hub wheel 43 is fitted and attached to the outer peripheral surface on the vehicle outer side so as to be integrally rotatable. Details of the inside of the bowl-shaped outer ring 41 are omitted.

外輪１の二列の軌道面１２，１３のそれぞれと、ハブホイール４３、軸部４２それぞれの各軌道面１６，１７との間において、転動体としての玉群４，５が介装される。一対の保持器６，７それぞれは、各列の玉群４，５を保持する。   Ball groups 4, 5 as rolling elements are interposed between the two rows of raceway surfaces 12, 13 of the outer ring 1 and the raceway surfaces 16, 17 of the hub wheel 43 and the shaft portion 42, respectively. Each of the pair of cages 6 and 7 holds a group of balls 4 and 5 in each row.

軸部４２の車両アウタ側の端部は、ハブホイール４３の車両アウタ側端面にかしめられており、かしめ部１０を形成する。   An end portion of the shaft portion 42 on the vehicle outer side is caulked to a vehicle outer side end surface of the hub wheel 43 to form the caulking portion 10.

このような構成の転がり軸受装置２００も、外輪１のフランジ１４の車両インナ側が車両の一部であるナックル（不図示）に固定され、ハブホイール４３のフランジ１５の車両アウタ側に車輪（不図示）が取り付けられる。このとき、外輪１のフランジ１４とハブホイール４３のフランジ１５との間には環状の自由空間１１が存在する。   Also in the rolling bearing device 200 having such a configuration, the vehicle inner side of the flange 14 of the outer ring 1 is fixed to a knuckle (not shown) which is a part of the vehicle, and the wheel (not shown) is connected to the vehicle outer side of the flange 15 of the hub wheel 43. ) Is attached. At this time, an annular free space 11 exists between the flange 14 of the outer ring 1 and the flange 15 of the hub wheel 43.

この転がり軸受装置２００でも、車両アウタ側の玉群４のピッチ円直径Ｄ1と、車両インナ側の玉群５のピッチ円直径Ｄ2との関係をＤ1＞Ｄ2に設定している。また、当該車両アウタ側の玉４の直径を小さく設定し、当該玉４の介装数を増やすこともできる。 In this rolling bearing device 200, the pitch circle diameter D 1 of the ball group 4 of the vehicle outer side, a relation between the pitch circle diameter D 2 set of balls 5 of the vehicle inner side is set to D 1> D 2. Moreover, the diameter of the ball 4 on the vehicle outer side can be set to be small, and the number of interposed balls 4 can be increased.

このように設定したときの具体的構成および作用、効果は、基本的に上述の実施形態と同様である。   The specific configuration, operation, and effect when set in this way are basically the same as those of the above-described embodiment.

（３）本発明は、図７で示すように、駆動輪側の転がり軸受装置３００にも適用することができる。   (3) The present invention can also be applied to a rolling bearing device 300 on the drive wheel side, as shown in FIG.

図示例の転がり軸受装置３００は、基本的には上記実施形態の転がり軸受装置１００と同様であるが、異なる点は、ハブ軸２が中空とされている点である。このハブ軸２の中空部分に、図示しないが、アクスルシャフトが挿入され、結合される。   The rolling bearing device 300 of the illustrated example is basically the same as the rolling bearing device 100 of the above embodiment, but the difference is that the hub shaft 2 is hollow. Although not shown, an axle shaft is inserted into and coupled to the hollow portion of the hub shaft 2.

（４）本発明は、図８で示すように、ハブ軸２の外周面に軸方向一対の内輪３ａ、３ｂを嵌合装着した転がり軸受装置４００にも適用することができる。   (4) The present invention can also be applied to a rolling bearing device 400 in which a pair of axial inner rings 3a and 3b are fitted to the outer peripheral surface of the hub shaft 2 as shown in FIG.

また、このような形式の転がり軸受装置において、図９に示すように、転動体群を円錐ころ群１８、１９とすることもできる。この場合、車両アウタ側の各円錐ころ１８の径を小さくしてもよい。   Further, in such a type of rolling bearing device, as shown in FIG. 9, the rolling element groups may be tapered roller groups 18 and 19. In this case, the diameter of each tapered roller 18 on the vehicle outer side may be reduced.

１ 外輪
２ ハブ軸
３ 内輪
４ 玉（車両アウタ側）
５ 玉（車両インナ側）
１１ 自由空間
１４ フランジ
１５ フランジ
１００ 転がり軸受装置 1 outer ring 2 hub axle 3 inner ring 4 ball (vehicle outer side)
5 balls (vehicle inner side)
11 Free space 14 Flange 15 Flange 100 Rolling bearing device

Claims (4)

軸方向一方側の外周面にフランジを有し、軸方向他方側の外周面に軸方向二列の第１、第２内輪軌道面を有する内輪部材と、
内周面に前記内輪部材の二列の第１、第２内輪軌道面と径方向でそれぞれ対向する軸方向二列の第１、第２外輪軌道面を有し、外周面にフランジを有する外輪部材と、
前記外輪部材の第１、第２外輪軌道面と前記内輪部材の第１、第２内輪軌道面との間に介装される軸方向二列の第１、第２転動体群とを含み、
前記第１転動体群のピッチ円直径Ｄ1と、前記第２転動体群のピッチ円直径Ｄ2との関係が、Ｄ1＞Ｄ2に設定され、
前記第１転動体群の各転動体の直径が小さく設定されているとともに、前記第１転動体群の転動体数が増大されている転がり軸受装置。 An inner ring member having a flange on the outer circumferential surface on one side in the axial direction and having two rows of first and second inner ring raceways in the axial direction on the outer circumferential surface on the other side in the axial direction;
An outer ring having two rows of first and second outer ring raceways in the axial direction facing the first and second inner ring raceway surfaces in two rows of the inner ring member on the inner circumferential surface, and a flange on the outer circumferential surface. Members,
Two axial first and second rolling element groups interposed between the first and second outer ring raceway surfaces of the outer ring member and the first and second inner ring raceway surfaces of the inner ring member;
The relationship between the pitch circle diameter D1 of the first rolling element group and the pitch circle diameter D2 of the second rolling element group is set to D1> D2,
A rolling bearing device in which the diameter of each rolling element of the first rolling element group is set small, and the number of rolling elements of the first rolling element group is increased. 請求項１の転がり軸受装置において、
前記第１転動体群の各転動体の直径が、前記第２転動体群の各転動体の直径の８８％よりも小さく、８１％よりも大きく設定されている転がり軸受装置。 In the rolling bearing device of claim 1,
A rolling bearing device in which the diameter of each rolling element of the first rolling element group is set to be smaller than 88% and larger than 81% of the diameter of each rolling element of the second rolling element group. 請求項２の転がり軸受装置において、
前記第１転動体群の転動体数が、前記第２転動体群の転動体数の１８２％よりも小さく設定されている転がり軸受装置。 In the rolling bearing device according to claim 2,
A rolling bearing device in which the number of rolling elements in the first rolling element group is set to be smaller than 182% of the number of rolling elements in the second rolling element group. 請求項１の転がり軸受装置において、
前記Ｄ1と前記Ｄ2との関係が、Ｄ1≦１．４９×Ｄ2に設定されている転がり軸受装置。 In the rolling bearing device of claim 1,
A rolling bearing device in which the relationship between the D1 and the D2 is set to D1 ≦ 1.49 × D2.
JP2009032702A 2009-02-16 2009-02-16 Rolling bearing device Withdrawn JP2009103325A (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2013543462A (en) * 2010-11-29 2013-12-05 本田技研工業株式会社 Shortened drive shaft stem

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS576125A (en) * 1980-06-13 1982-01-13 Nachi Fujikoshi Corp Flanged using bearing and is assembly method
JPS5790416A (en) * 1980-11-26 1982-06-05 Nachi Fujikoshi Corp Monobloc type plural rows cone roller bearing and its assembly procedure
JPH0427216A (en) * 1990-05-22 1992-01-30 Nec Eng Ltd Facsimile extension transfer system
JP2003232343A (en) * 2002-02-06 2003-08-22 Nsk Ltd Wheel bearing equipment

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS576125A (en) * 1980-06-13 1982-01-13 Nachi Fujikoshi Corp Flanged using bearing and is assembly method
JPS5790416A (en) * 1980-11-26 1982-06-05 Nachi Fujikoshi Corp Monobloc type plural rows cone roller bearing and its assembly procedure
JPH0427216A (en) * 1990-05-22 1992-01-30 Nec Eng Ltd Facsimile extension transfer system
JP2003232343A (en) * 2002-02-06 2003-08-22 Nsk Ltd Wheel bearing equipment

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2013543462A (en) * 2010-11-29 2013-12-05 本田技研工業株式会社 Shortened drive shaft stem

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