JP2012149686A - Wheel rolling bearing device - Google Patents

Wheel rolling bearing device Download PDF

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JP2012149686A
JP2012149686A JP2011007827A JP2011007827A JP2012149686A JP 2012149686 A JP2012149686 A JP 2012149686A JP 2011007827 A JP2011007827 A JP 2011007827A JP 2011007827 A JP2011007827 A JP 2011007827A JP 2012149686 A JP2012149686 A JP 2012149686A
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outer ring
outer side
ring raceway
raceway surface
wheel
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Tatsuya Yokota
竜哉 横田
淑人 ▲高▼田
Yoshito Takada
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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
    • F16C19/50—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
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
    • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
    • F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
    • F16C19/184—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement
    • F16C19/186—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement with three raceways provided integrally on parts other than race rings, e.g. third generation hubs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/38—Ball cages
    • F16C33/3806—Details of interaction of cage and race, e.g. retention, centring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/38—Ball cages
    • F16C33/41—Ball cages comb-shaped
    • F16C33/412—Massive or moulded comb cages, e.g. snap ball cages
    • 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

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

Abstract

PROBLEM TO BE SOLVED: To provide a wheel rolling bearing device with which it is possible to reduce material cost of a forging material of an outer ring member and to reduce time and labor for turning.SOLUTION: When a pitch circle diameter of a ball 50 in an inner side row is D1 and a pitch circle diameter of a ball 51 in an outer side row is D2, the D1 and D2 are set to have a relation of "D1<D2". Counter bore parts 42 and 47 of outer ring raceway surfaces 40 and 45 on an inner side and an outer side are formed into cylindrical surfaces flat in an axial direction. Annular grooves 41a and 46a are formed on inner peripheral surfaces of raceway shoulder parts 41 and 46 provided between the outer ring raceway surface 40 on the inner side and the outer ring raceway surface 45 on the outer side. In retainers 60 and 65 on the inner side and the outer side, engaged parts 64 and 69 which are engaged to each of the annular grooves 41a and 46a to regulate axial movement of the retainers 60 and 65 on the inner side and the outer side in relation to the outer ring member 30 are formed.

Description

この発明は車輪用転がり軸受装置に関する。   The present invention relates to a wheel rolling bearing device.

従来、車輪用転がり軸受装置（車輪用ハブユニットと呼ばれることもある）において、車輪が取り付けられるハブホイールのハブ軸の外周面に形成されたインナ側及びアウタ側の内輪軌道面と、外輪部材の内周面に形成されたインナ側及びアウタ側の外輪軌道面との間に、インナ側列及びアウタ側列の玉が転動可能に配列された構造のものがある。
また、車輪用転がり軸受装置において、外輪部材の嵌合軸部の外径寸法を、車体側部材の組付孔に嵌合可能な大きさに確保しながら、車輪用転がり軸受装置の軽量化や高剛性化を図るために、インナ側列の玉のピッチ円直径よりもアウタ側列の玉のピッチ円直径を大きく設定し、これによって、インナ側列の玉の個数よりもアウタ側列の玉の個数を多くしたものが知られている（例えば、特許文献１参照）。
この種の車輪用転がり軸受装置において、図１０に示すように、外輪部材３３０のインナ側及びアウタ側の外輪軌道面３４０、３４５に対し、インナ側の保持器３６０に保持されたインナ側列の玉３５０やアウタ側の保持器３６５に保持されたアウタ側列の玉３５１を組み付ける際などにおいて、外輪部材３３０のインナ側及びアウタ側の外輪軌道面３４０、３４５からインナ側列及びアウタ側列の玉３５０が脱落しないように、インナ側及びアウタ側の外輪軌道面３４０、３４５の軸受外側（カウンタボア部）には、これら外輪軌道面の接触角０°位置Ｐ３、Ｐ４を越えてインナ側及びアウタ側の外輪軌道面３４０、３４５の一部をなすカウンタ肩部３４２ａ、３４７ａが形成されるのが一般的である。
すなわち、外輪部材３３０のインナ側及びアウタ側の外輪軌道面３４０、３４５に対し、インナ側列及びアウタ側列の玉３５０、３５１をそれぞれ組み付ける場合、先ず、インナ側及びアウタ側の保持器３６０、３６５の各ポケット３６２、３６７にインナ側列及びアウタ側列の玉３５０、３５１をそれぞれ組み付ける。
その後、テーブル上面に、外輪部材３３０の一方の外輪軌道面、例えば、アウタ側の外輪軌道面３４５のカウンタ肩部３４７ａを上側にして配置する。ここで、外輪部材３３０のアウタ側の外輪軌道面３４５に対し、アウタ側の保持器３６５を備えたアウタ側列の玉３５１を押し込んで組み付ける。
次に、テーブル上面に、外輪部材３３０のインナ側の外輪軌道面３４０のカウンタ肩部３４７ａを上側にして配置する。この際、アウタ側の外輪軌道面３４５に組み付けたアウタ側列の玉３５１の脱落がカウンタ肩部３４７ａによって阻止される。
ここで、外輪部材３３０のインナ側の外輪軌道面３４０に対し、インナ側の保持器３６０を備えたインナ側列の玉３５０を押し込んで組み付ける。 2. Description of the Related Art Conventionally, in a rolling bearing device for a wheel (sometimes referred to as a wheel hub unit), inner and outer inner raceway surfaces formed on an outer peripheral surface of a hub axle of a hub wheel to which a wheel is attached, and outer ring members There is a structure in which balls of an inner side row and an outer side row are arranged so as to roll between an inner side and an outer side raceway surface formed on an inner peripheral surface.
Further, in the wheel rolling bearing device, the wheel rolling bearing device can be reduced in weight while securing the outer diameter dimension of the fitting shaft portion of the outer ring member to a size that can be fitted into the assembly hole of the vehicle body side member. In order to increase the rigidity, the pitch circle diameter of the balls on the outer side row is set to be larger than the pitch circle diameter of the balls on the inner side row, whereby the balls on the outer side row are larger than the number of balls on the inner side row. There are known ones having a larger number (see Patent Document 1, for example).
In this type of wheel rolling bearing device, as shown in FIG. 10, the inner side row held by the inner side retainer 360 with respect to the inner side and outer side outer ring raceway surfaces 340 and 345 of the outer ring member 330 is arranged. When assembling the outer side row balls 351 held by the balls 350 or the outer side cage 365, the inner side row and outer side row of the outer ring member 330 from the inner side and outer side outer ring raceway surfaces 340 and 345 are arranged. In order to prevent the balls 350 from falling off, the outer side raceway surfaces 340 and 345 on the inner and outer side raceway surfaces 340 and 345 have bearing inner sides (counter bore portions) beyond the contact angles 0 ° positions P3 and P4 of the outer raceway surfaces. In general, counter shoulder portions 342a and 347a that form part of the outer ring raceway surfaces 340 and 345 on the outer side are formed.
That is, when the inner side and outer side balls 350, 351 are assembled to the inner side and outer side outer ring raceway surfaces 340, 345 of the outer ring member 330, respectively, first, the inner side and outer side cages 360, The inner side row and outer side row balls 350 and 351 are assembled in the pockets 362 and 367 of the 365, respectively.
Thereafter, one outer ring raceway surface of the outer ring member 330, for example, the counter shoulder portion 347a of the outer ring raceway surface 345 is disposed on the upper surface of the table. Here, the outer side row balls 351 having the outer side retainer 365 are pushed into the outer side raceway surface 345 of the outer side member 330 and assembled.
Next, the counter shoulder portion 347a of the inner ring outer ring raceway surface 340 of the outer ring member 330 is arranged on the table upper surface. At this time, the counter shoulder portion 347a prevents the outer side row balls 351 from being attached to the outer side outer ring raceway surface 345 from falling off.
Here, the balls 350 in the inner side row provided with the inner side retainer 360 are pushed into the inner side outer ring raceway surface 340 of the outer ring member 330 and assembled.

特開２００４−１０８４４９号公報JP 2004-108449 A

ところで、前記した車輪用転がり軸受装置においては、インナ側列及びアウタ側列の玉３５０、３５１の脱落を防止するために、外輪部材３３０のインナ側及びアウタ側の外輪軌道面３４０、３４５の軸受外側（カウンタボア部）にカウンタ肩部３４２ａ、３４７ａを形成する必要がある。
このため、外輪部材３３０を鍛造品３３０ａから形成する場合、図１１と図１２に示すように、カウンタ肩部３４２ａ、３４７ａの表面を旋削したり研磨するための旋削取り代３３０ｂ、３３０ｃを確保しなければならない。これによって、鍛造品３３０ａに対する鍛造材料の材料費が高くなったり、旋削加工の手間が多くなる。 By the way, in the above-described wheel rolling bearing device, in order to prevent the balls 350 and 351 in the inner side row and the outer side row from falling off, the bearings on the outer side raceway surfaces 340 and 345 on the inner side and outer side of the outer ring member 330 are supported. Counter shoulders 342a and 347a must be formed on the outer side (counter bore).
Therefore, when the outer ring member 330 is formed from the forged product 330a, as shown in FIGS. 11 and 12, turning allowances 330b and 330c for turning and polishing the surfaces of the counter shoulder portions 342a and 347a are secured. There must be. As a result, the material cost of the forging material for the forged product 330a increases, and the labor for turning increases.

この発明の目的は、前記問題点に鑑み、外輪部材の鍛造材料の材料費の低減や、旋削加工の手間を軽減することができる車輪用転がり軸受装置を提供することである。   In view of the above problems, an object of the present invention is to provide a wheel rolling bearing device that can reduce the material cost of the forging material of the outer ring member and reduce the labor of turning.

前記課題を解決するために、この発明の請求項１に係る車輪用転がり軸受装置は、車輪が取り付けられるハブホイールのハブ軸の外周面に、軸方向に所定間隔を隔ててインナ側及びアウタ側の内輪軌道面が形成され、前記ハブ軸の外周に配設される外輪部材の内周面に、軸方向に所定間隔を隔ててインナ側及びアウタ側の外輪軌道面が形成され、前記インナ側及びアウタ側の内輪軌道面と、前記インナ側及びアウタ側の外輪軌道面との間にインナ側列及びアウタ側列の玉がインナ側及びアウタ側の保持器によって保持された状態で転動可能に配列され、前記インナ側列の玉のピッチ円直径をＤ１とし、前記アウタ側列の玉のピッチ円直径をＤ２としたときに、「Ｄ１＜Ｄ２」の関係となるように設定された車輪用転がり軸受装置であって、
前記インナ側及びアウタ側の外輪軌道面のそれぞれのカウンタボア部は、軸方向に平坦な円筒面に形成され、
前記インナ側の外輪軌道面と前記アウタ側の外輪軌道面との間に設けられたそれぞれの軌道肩部の内周面には、環状溝がそれぞれ形成され、
前記インナ側及びアウタ側の保持器には、前記各環状溝に係合して前記外輪部材に対する前記インナ側及びアウタ側の保持器の軸方向への移動を規制する係合部がそれぞれ形成されていることを特徴とする。 In order to solve the above-mentioned problems, a rolling bearing device for a wheel according to a first aspect of the present invention includes an inner side and an outer side on the outer peripheral surface of a hub shaft of a hub wheel to which the wheel is attached at a predetermined interval in the axial direction. An inner ring raceway surface is formed, and inner and outer outer ring raceway surfaces are formed on an inner circumferential surface of an outer ring member disposed on an outer circumference of the hub shaft at predetermined intervals in the axial direction. The balls in the inner side row and the outer side row can be rolled between the inner ring raceway surface on the outer side and the outer ring raceway surface on the inner side and the outer side while being held by the cage on the inner side and the outer side. In which the pitch circle diameter of the balls in the inner side row is D1, and the pitch circle diameter of the balls in the outer side row is D2, the wheels are set to have a relation of “D1 <D2” A rolling bearing device for
Each counter bore portion of the inner side and outer side outer ring raceway surfaces is formed in a cylindrical surface flat in the axial direction,
An annular groove is formed on the inner peripheral surface of each track shoulder provided between the inner-side outer ring raceway surface and the outer-side outer ring raceway surface,
The inner side and outer side retainers are respectively formed with engaging portions that engage with the respective annular grooves and restrict movement of the inner side and outer side retainers in the axial direction relative to the outer ring member. It is characterized by.

前記構成によると、インナ側列の玉のピッチ円直径Ｄ１よりもアウタ側列の玉のピッチ円直径Ｄ２を大きく設定することによって、車輪用転がり軸受装置の軽量化や高剛性化を良好に図ることが可能となる。
また、インナ側及びアウタ側の外輪軌道面のそれぞれのカウンタボア部を、軸方向に平坦な円筒面（インナ側及びアウタ側の外輪軌道面の接触角０°位置から平行な円筒面）に形成することによって、カウンタ肩部がない構造にする。また、インナ側及びアウタ側の外輪軌道面の軌道肩部の内周面に形成された各環状溝と、インナ側及びアウタ側の保持器に形成された係合部との係合力によってインナ側及びアウタ側の保持器の軸方向への移動を規制する。
すなわち、インナ側及びアウタ側の保持器の軸方向への移動を規制して玉の脱落を防止することによって、カウンタ肩部がない構造にすることができる。この結果、従来と比較して、外輪部材の鍛造材料の材料費の低減や、旋削加工の手間を軽減することができる。 According to the above configuration, by setting the pitch circle diameter D2 of the balls in the outer side row larger than the pitch circle diameter D1 of the balls in the inner side row, it is possible to favorably reduce the weight and increase the rigidity of the wheel rolling bearing device. It becomes possible.
Also, the counterbore portions of the inner side and outer side outer ring raceway surfaces are formed on cylindrical surfaces that are flat in the axial direction (cylindrical surfaces parallel to the contact angle 0 ° position of the inner side and outer side outer ring raceway surfaces). By doing so, a structure without a counter shoulder is obtained. Further, the inner side is formed by the engagement force between each annular groove formed on the inner circumferential surface of the raceway shoulder portion of the inner-side and outer-side outer ring raceway surface and the engagement portion formed on the inner-side and outer-side cage. And the movement of the outer side cage in the axial direction is restricted.
That is, by restricting movement of the inner side and outer side cages in the axial direction to prevent the balls from falling off, a structure without a counter shoulder can be obtained. As a result, it is possible to reduce the material cost of the forging material of the outer ring member and the labor of turning as compared with the conventional case.

請求項２に係る車輪用転がり軸受装置は、請求項１に記載の車輪用転がり軸受装置であって、
インナ側及びアウタ側の外輪軌道面のそれぞれの軌道肩部の間に形成された段差部と、ハブ軸のインナ側及びアウタ側の内輪軌道面の間に形成された段差部とが僅かな隙間をもって接近することによってラビリンス構造をなしていることを特徴とする。 The rolling bearing device for a wheel according to claim 2 is the rolling bearing device for a wheel according to claim 1,
There is a slight gap between the step formed between the inner and outer outer raceway surfaces of the inner and outer outer raceways and the step formed between the inner and outer raceways of the hub axle. It is characterized by having a labyrinth structure by approaching.

前記構成によると、外輪軌道面側の段差部と、ハブ軸側の段差部とがラビリンス構造をなすことによって、ラビリンス専用の部材を製作して外輪部材やハブ軸に組み付けることなく、軸受内に充填のグリース等の潤滑剤が軸受回転時の遠心力によって小径側から大径側へ流れることを抑制することができる。   According to the above configuration, the step portion on the outer ring raceway surface side and the step portion on the hub shaft side form a labyrinth structure, so that a member dedicated to the labyrinth can be manufactured and assembled to the outer ring member and the hub shaft without being assembled in the bearing. The lubricant such as filled grease can be prevented from flowing from the small diameter side to the large diameter side due to the centrifugal force when the bearing rotates.

この発明の実施例１に係る車輪用転がり軸受装置を示す縦断面図である。It is a longitudinal cross-sectional view which shows the rolling bearing device for wheels which concerns on Example 1 of this invention. 同じくハブ軸と外輪部材とインナ側列及びアウタ側列の玉との組み付け状態を拡大して示す縦断面図である。FIG. 5 is an enlarged longitudinal sectional view showing the assembled state of the hub shaft, the outer ring member, the inner side row and the outer side row ball. 同じく外輪部材のインナ側及びアウタ側の外輪軌道面にインナ側列及びアウタ側列の玉が配列された状態を示す縦断面図である。FIG. 5 is a longitudinal sectional view showing a state in which balls in the inner side row and the outer side row are arranged on the outer ring raceway surfaces on the inner side and the outer side of the outer ring member. 同じく外輪部材のインナ側の外輪軌道面とインナ側列の玉とインナ側の保持器との組み付け状態を拡大して示す縦断面図である。FIG. 5 is an enlarged longitudinal sectional view showing an assembled state of an inner ring outer ring raceway surface, an inner side row ball and an inner side retainer of the outer ring member. 同じく外輪部材のアウタ側の外輪軌道面とアウタ側列の玉とアウタ側の保持器との組み付け状態を拡大して示す縦断面図である。FIG. 5 is an enlarged longitudinal sectional view showing the assembled state of the outer ring raceway surface of the outer ring member, the outer side row balls and the outer side cage. 同じく外輪部材のインナ側の外輪軌道面とカウンタボア部とを拡大して示す縦断面図である。FIG. 5 is an enlarged longitudinal sectional view of the outer ring raceway surface on the inner side of the outer ring member and the counterbore part. 同じく外輪部材のアウタ側の外輪軌道面とカウンタボア部とを拡大して示す縦断面図である。Similarly, it is a longitudinal sectional view showing an outer ring raceway surface and a counter bore portion on the outer side of the outer ring member in an enlarged manner. 同じくインナ側及びアウタ側の保持器に保持されたインナ側列及びアウタ側列の玉が外輪部材のインナ側及びアウタ側の外輪軌道面に組み付けられる前の状態を示す説明図である。FIG. 6 is an explanatory view showing a state before the balls of the inner side row and the outer side row held by the inner side and outer side cages are assembled to the inner side and outer side outer raceway surfaces of the outer ring member. この発明の実施例２に係る車輪用転がり軸受装置のハブ軸と外輪部材とインナ側列及びアウタ側列の玉との組み付け状態を拡大して示す縦断面図である。It is a longitudinal cross-sectional view which expands and shows the assembly | attachment state of the hub axle of the wheel rolling bearing device which concerns on Example 2 of this invention, an outer ring member, the ball | bowl of an inner side row | line | column and an outer side row | line | column. 従来の車輪用転がり軸受装置を示す縦断面図である。It is a longitudinal cross-sectional view which shows the conventional rolling bearing device for wheels. 同じく外輪部材のインナ側の外輪軌道面のカウンタボア部にカウンタ肩部が形成された状態を拡大して示す縦断面図である。FIG. 5 is an enlarged longitudinal sectional view showing a state in which a counter shoulder is formed on the counter bore portion of the outer ring raceway surface on the inner side of the outer ring member. 同じく外輪部材のアウタ側の外輪軌道面のカウンタボア部にカウンタ肩部が形成された状態を拡大して示す縦断面図である。FIG. 5 is an enlarged longitudinal sectional view showing a state in which a counter shoulder is formed on the counter bore of the outer ring raceway surface on the outer side of the outer ring member.

この発明を実施するための形態について実施例にしたがって説明する。   A mode for carrying out the present invention will be described in accordance with an embodiment.

この発明の実施例１を図１〜図８にしたがって説明する。
図１に示すように、車輪用転がり軸受装置（車輪用ハブユニット）は、複列のアンギュラ玉軸受を構成するための内輪部材としてのハブ軸１５を一体に有するハブホイール１０と、外輪部材３０と、複列をなすインナ側列及びアウタ側列の玉５０、５１と、インナ側及びアウタ側の保持器６０、６５とを備えてユニット化されている。 A first embodiment of the present invention will be described with reference to FIGS.
As shown in FIG. 1, a wheel rolling bearing device (wheel hub unit) includes a hub wheel 10 integrally having a hub shaft 15 as an inner ring member for constituting a double row angular ball bearing, and an outer ring member 30. And inner side and outer side balls 50 and 51 forming double rows, and inner and outer side cages 60 and 65 are unitized.

図１に示すように、ハブホイール１０は、ハブ軸１５と、このハブ軸１５の車アウタ側端部に同一中心線上に形成されたフランジ体１１とを一体に有し、フランジ体１１の車アウタ側面には、ブレーキロータを間に挟んで車輪（図示しない）の中心孔が嵌込まれる車輪用嵌合部１３が形成されている。
また、フランジ体１１には、車輪を締め付ける複数のハブボルト１２が所定ピッチで圧入固定されている。 As shown in FIG. 1, the hub wheel 10 integrally includes a hub axle 15 and a flange body 11 formed on the same center line at an end portion on the vehicle outer side of the hub axle 15. A wheel fitting portion 13 into which a center hole of a wheel (not shown) is fitted is formed on the outer side surface with the brake rotor interposed therebetween.
A plurality of hub bolts 12 for fastening the wheel are press-fitted and fixed to the flange body 11 at a predetermined pitch.

図１に示すように、ハブ軸１５の外周面には、軸方向に所定間隔を隔ててインナ側及びアウタ側の内輪軌道面２０、２５がそれぞれ形成されている。
この実施例１において、ハブ軸１５は、フランジ体１１側が大径で先端側が小径に形成された段軸状に形成されている。そして、ハブ軸１５の大径部１６の片側（フランジ体１１側）に形成された大径肩部１６ａの外周面にアウタ側の内輪軌道面２５が形成されている。また、ハブ軸１５の小径部１７の外周面には内輪体２６が嵌め込まれ、この内輪体２６の外周面にインナ側の内輪軌道面２０が形成されている。
さらに、ハブ軸１５の小径部１７の端部から延出された筒部がかしめ具によって半径方向外方へかしめられてかしめ部１８が形成されることによって、ハブ軸１５の小径部１７の段差面とかしめ部１８との間に内輪体２６が挟持されるようになっている。 As shown in FIG. 1, inner ring raceway surfaces 20 and 25 on the inner side and the outer side are formed on the outer peripheral surface of the hub shaft 15 at predetermined intervals in the axial direction.
In the first embodiment, the hub shaft 15 is formed in a step shaft shape in which the flange body 11 side has a large diameter and the distal end side has a small diameter. An outer side raceway surface 25 on the outer side is formed on the outer peripheral surface of the large-diameter shoulder portion 16a formed on one side (flange body 11 side) of the large-diameter portion 16 of the hub shaft 15. An inner ring body 26 is fitted on the outer peripheral surface of the small-diameter portion 17 of the hub shaft 15, and an inner ring raceway surface 20 is formed on the outer peripheral surface of the inner ring body 26.
Further, the cylindrical portion extended from the end portion of the small-diameter portion 17 of the hub shaft 15 is caulked outwardly in the radial direction by a caulking tool to form the caulking portion 18, thereby forming a step in the small-diameter portion 17 of the hub shaft 15. An inner ring body 26 is sandwiched between the surface and the caulking portion 18.

図１と図２に示すように、外輪部材３０の一端側（車幅方向インナ側）には、車両の懸架装置（図示しない）に支持されたナックル、キャリア等の車体側部材の組付孔に嵌合される嵌合軸部３５が形成されている。また、外輪部材３０の外周面の嵌合軸部３５に隣接する部分には、車体側部材の取付面にボルトによって締結される車体側フランジ３１が一体に形成されている。
外輪部材３０の内周面には、ハブ軸１５のインナ側の内輪軌道面２０及びアウタ側の内輪軌道面２５に対応するインナ側の外輪軌道面４０とアウタ側の外輪軌道面４５とが軸方向に所定間隔を保って形成されている。 As shown in FIGS. 1 and 2, an assembly hole for a vehicle body side member such as a knuckle or a carrier supported by a vehicle suspension device (not shown) is provided on one end side (vehicle width direction inner side) of the outer ring member 30. A fitting shaft portion 35 is formed to be fitted to the. A vehicle body side flange 31 that is fastened to a mounting surface of the vehicle body side member by a bolt is integrally formed at a portion adjacent to the fitting shaft portion 35 on the outer peripheral surface of the outer ring member 30.
An inner side outer ring raceway surface 40 and an outer side outer ring raceway surface 45 corresponding to the inner side inner raceway surface 20 and the outer side inner ring raceway surface 25 of the hub axle 15 are pivoted on the inner peripheral surface of the outer ring member 30. It is formed at predetermined intervals in the direction.

インナ側及びアウタ側の内輪軌道面２０、２５と、インナ側及びアウタ側の外輪軌道面４０、４５との間には、インナ側列及びアウタ側列の各複数個の玉５０、５１が、インナ側及びアウタ側の保持器６０、６５に保持された状態で転動可能に配列されている。
そして、前記したハブ軸１５のかしめ部１８によるかしめ力によって、インナ側列及びアウタ側列の玉５０、５１にそれぞれ所要とする予圧が付与されるようになっている。 Between the inner side and outer side inner ring raceway surfaces 20, 25 and the inner side and outer side outer ring raceway surfaces 40, 45, a plurality of balls 50, 51 in the inner side row and the outer side row are provided. The inner side and outer side cages 60 and 65 are arranged so as to roll while being held.
The required preload is applied to the balls 50 and 51 of the inner side row and the outer side row by the caulking force of the caulking portion 18 of the hub shaft 15 described above.

図１と図２に示すように、インナ側列の玉５０のピッチ円直径をＤ１とし、アウタ側列の玉５１のピッチ円直径をＤ２としたときに、「Ｄ１＜Ｄ２」の関係となるように設定されている。
すなわち、この実施例１において、外輪部材３０の嵌合軸部３５の外径寸法を車体側部材の組付孔に嵌合可能な大きさに確保しながら、車輪用転がり軸受装置の軽量化や高剛性化を図るために、インナ側列の玉５０のピッチ円直径Ｄ１よりもアウタ側列の玉５１のピッチ円直径Ｄ２が大きく設定されると共に、インナ側列の玉５０の玉径よりもアウタ側列の玉５１の玉径が小さく設定されている。これに伴って、インナ側列の玉５０の個数よりもアウタ側列の玉５１の個数が多くなっている。 As shown in FIGS. 1 and 2, when the pitch circle diameter of the balls 50 in the inner side row is D1, and the pitch circle diameter of the balls 51 in the outer side row is D2, the relation of “D1 <D2” is established. Is set to
That is, in the first embodiment, the wheel rolling bearing device can be reduced in weight while securing the outer diameter dimension of the fitting shaft portion 35 of the outer ring member 30 to a size that can be fitted into the assembly hole of the vehicle body side member. In order to increase the rigidity, the pitch circle diameter D2 of the balls 51 in the outer side row is set larger than the pitch circle diameter D1 of the balls 50 in the inner side row, and is larger than the ball diameter of the balls 50 in the inner side row. The ball diameter of the balls 51 in the outer side row is set small. Accordingly, the number of balls 51 in the outer side row is larger than the number of balls 50 in the inner side row.

前記「Ｄ１＜Ｄ２」の関係に基づき、アウタ側列の玉５１をピッチ円直径Ｄ２で配列するために、ハブホイール１０のハブ軸１５の外周面に形成されるアウタ側の内輪軌道面２５は、インナ側の内輪軌道面２０よりも大径に形成されている。
そして、図１に示すように、ハブホイール１０の車輪用嵌合部１３の中心孔部からインナ側に向かう凹部１０ａがアウタ側の内輪軌道面２５との間に所要とする肉厚を残してできるだけ大きくかつ深く形成され、これによって、ハブホイール１０の軽量化、ひいては車輪用転がり軸受装置の軽量化が図られるようになっている。 Based on the relationship of “D1 <D2,” the outer side inner ring raceway surface 25 formed on the outer peripheral surface of the hub axle 15 of the hub wheel 10 in order to arrange the balls 51 in the outer side row with the pitch circle diameter D2 is: The inner side raceway surface 20 has a larger diameter than the inner side raceway surface 20.
As shown in FIG. 1, the required thickness is left between the recess 10 a toward the inner side from the center hole of the wheel fitting portion 13 of the hub wheel 10 and the inner ring raceway surface 25 on the outer side. It is formed as large and deep as possible, thereby reducing the weight of the hub wheel 10 and hence the rolling bearing device for the wheel.

また、前記「Ｄ１＜Ｄ２」の関係に基づき、アウタ側列の玉５１をピッチ円直径Ｄ２で配列するために、外輪部材３０の内周面に形成されるアウタ側の外輪軌道面４５は、インナ側の外輪軌道面４０よりも大径に形成されている。
さらに、図２に示すように、外輪部材３０の内周面には、インナ側の外輪軌道面４０とアウタ側の外輪軌道面４５との間に位置する部分においてインナ側の外輪軌道面４０の端縁に連続するインナ側軌道肩部４１と、アウタ側の外輪軌道面４５の端縁に連続するアウタ側軌道肩部４６とがそれぞれ形成されている。
さらに、インナ側軌道肩部４１は、軸線方向に平行する円筒状に形成され、アウタ側軌道肩部４６は、インナ側軌道肩部４１よりも大径で軸線方向に平行する円筒状に形成されている。そして、アウタ側軌道肩部４６とインナ側軌道肩部４１との間には縦断面Ｒ面をなす境界段差部４４が形成されている。 Further, in order to arrange the outer side rows of balls 51 with the pitch circle diameter D2 based on the relationship of “D1 <D2”, the outer side outer ring raceway surface 45 formed on the inner peripheral surface of the outer ring member 30 is: The outer ring raceway surface 40 on the inner side is formed with a larger diameter.
Further, as shown in FIG. 2, the inner ring surface of the outer ring member 30 has an inner side outer ring raceway surface 40 in a portion located between the inner side outer ring raceway surface 40 and the outer side outer ring raceway surface 45. Inner side track shoulders 41 continuing to the end edge and outer side track shoulders 46 continuing to the end edge of the outer side raceway surface 45 of the outer side are formed.
Furthermore, the inner side track shoulder 41 is formed in a cylindrical shape parallel to the axial direction, and the outer side track shoulder 46 is formed in a cylindrical shape having a larger diameter than the inner side track shoulder 41 and parallel to the axial direction. ing. A boundary stepped portion 44 having a longitudinal section R surface is formed between the outer-side track shoulder 46 and the inner-side track shoulder 41.

図３と図４に示すように、外輪部材３０のインナ側の外輪軌道面４０のカウンタボア部４２は、インナ側の外輪軌道面４０に対するインナ側列の玉５０の接触角０°位置Ｐ１から軸方向に平坦な円筒面に形成され、カウンタ肩部がない構造となている。
さらに、インナ側の外輪軌道面４０の軌道肩部４１の内周面には、環状溝４１ａが形成されている。
また、図３と図５に示すように、外輪部材３０のアウタ側の外輪軌道面４５のカウンタボア部４７においても、同様にしてアウタ側の外輪軌道面４５に対するアウタ側列の玉５１の接触角０°位置Ｐ２から軸方向に平坦な円筒面に形成され、カウンタ肩部がない構造となている。
さらに、アウタ側の外輪軌道面４５の軌道肩部４６の内周面には、環状溝４６ａが形成されている。 As shown in FIGS. 3 and 4, the counter bore portion 42 of the inner side outer ring raceway surface 40 of the outer ring member 30 has a contact angle of the ball 50 of the inner side row 50 with respect to the inner side outer ring raceway surface 40 from a position P1. It is formed in a cylindrical surface that is flat in the axial direction, and has no counter shoulder.
Further, an annular groove 41 a is formed on the inner peripheral surface of the track shoulder 41 of the inner side outer ring raceway surface 40.
Further, as shown in FIGS. 3 and 5, in the counter bore portion 47 of the outer ring raceway surface 45 on the outer side of the outer ring member 30, the contact of the balls 51 in the outer side row with the outer ring raceway surface 45 on the outer side is similarly performed. It is formed in a cylindrical surface that is flat in the axial direction from the angle 0 ° position P2, and has no counter shoulder.
Further, an annular groove 46 a is formed on the inner peripheral surface of the track shoulder 46 of the outer ring raceway surface 45 on the outer side.

図１と図４に示すように、インナ側の保持器６０は、インナ側の内輪軌道面２０とインナ側の外輪軌道面４０との環状空間に配置可能に環状に形成された環状部６１と、この環状部６１から周方向に所定間隔を隔てて一体に延出され、かつインナ側列の玉５０を保持するためのポケット６２を区画形成する複数の柱部６３とを備えている。
また、図４に示すように、インナ側の保持器６０の環状部６１の外周面には、インナ側の外輪軌道面４０の軌道肩部４１の環状溝４１ａに係合してインナ側の保持器６０の軸方向への移動を規正する係合部６４が形成されている。
また、係合部６４は、環状部６１の周方向の複数箇所に爪状に配設されてもよく、環状溝４１ａの全周に係合するように環状に形成されてもよい。 As shown in FIGS. 1 and 4, the inner retainer 60 includes an annular portion 61 formed in an annular shape so as to be disposed in an annular space between the inner ring raceway surface 20 on the inner side and the outer ring raceway surface 40 on the inner side. And a plurality of pillar portions 63 that extend integrally from the annular portion 61 at a predetermined interval in the circumferential direction and that define a pocket 62 for holding the ball 50 in the inner side row.
Further, as shown in FIG. 4, the outer peripheral surface of the annular portion 61 of the inner retainer 60 is engaged with the annular groove 41a of the track shoulder 41 of the inner outer raceway surface 40 to hold the inner side. An engaging portion 64 that regulates movement of the device 60 in the axial direction is formed.
Moreover, the engaging part 64 may be arrange | positioned by the nail | claw shape in the multiple places of the circumferential direction of the annular part 61, and may be formed in cyclic | annular form so that it may engage with the perimeter of the annular groove 41a.

図１と図５に示すように、アウタ側の保持器６５は、アウタ側の内輪軌道面２５とアウタ側の外輪軌道面４５との環状空間に配置可能に環状に形成された環状部６６と、この環状部６６から周方向に所定間隔を隔てて一体に延出され、かつアウタ側列の玉５１を保持するためのポケット６７を区画形成する複数の柱部６８とを備えている。
また、アウタ側の保持器６５の環状部６６の外周面には、アウタ側の外輪軌道面４５の軌道肩部４６の環状溝４６ａに係合してアウタ側の保持器６５の軸方向への移動を規正する係合部６９が形成されている。
また、係合部６９は、環状部６６の周方向の複数箇所に爪状に配設されてもよく、環状溝４６ａの全周に係合するように環状に形成されてもよい。 As shown in FIGS. 1 and 5, the outer side retainer 65 includes an annular portion 66 formed in an annular shape so as to be disposed in an annular space between the outer ring raceway surface 25 on the outer side and the outer raceway surface 45 on the outer side. And a plurality of pillars 68 extending integrally from the annular part 66 at a predetermined interval in the circumferential direction and defining a pocket 67 for holding the balls 51 in the outer side row.
Further, the outer circumferential surface of the annular portion 66 of the outer cage 65 is engaged with the annular groove 46a of the race shoulder 46 of the outer raceway surface 45 on the outer side so that the outer cage 65 extends in the axial direction. An engaging portion 69 that regulates the movement is formed.
Further, the engaging portions 69 may be arranged in a claw shape at a plurality of locations in the circumferential direction of the annular portion 66, or may be formed in an annular shape so as to engage with the entire circumference of the annular groove 46a.

この実施例１に係る車輪用転がり軸受装置は上述したように構成される。
したがって、車輪用転がり軸受装置のインナ側列の玉５０のピッチ円直径Ｄ１よりもアウタ側列の玉５１のピッチ円直径Ｄ２を大きく設定することによって、車輪用転がり軸受装置の軽量化や高剛性化を良好に図ることが可能となる。 The wheel rolling bearing device according to the first embodiment is configured as described above.
Accordingly, by setting the pitch circle diameter D2 of the balls 51 in the outer side row larger than the pitch circle diameter D1 of the balls 50 in the inner side row of the wheel rolling bearing device, the weight reduction and high rigidity of the wheel rolling bearing device can be achieved. Can be improved.

また、外輪部材３０のインナ側及びアウタ側の外輪軌道面４０、４５にインナ側列及びアウタ側列の玉５０、５１をそれぞれ組み付ける場合、先ず、図８に示すように、インナ側及びアウタ側の保持器６０、６５の各ポケット６２、６７にインナ側列及びアウタ側列の玉５０、５１をそれぞれ組み付ける。
その後、テーブル上面に、外輪部材３０の一方の外輪軌道面、例えば、アウタ側の外輪軌道面４５のカウンタボア部４７を上側にして配置する。ここで、外輪部材３０のアウタ側の外輪軌道面４５に対し、アウタ側列の玉５１を組み込んだアウタ側の保持器６５を押し込んで組み付ける。
この際、アウタ側の保持器６５の環状部６６に形成された係合部６９は、アウタ側の外輪軌道面４５の軌道肩部４６の内周面に沿って強制的に押し込まれて弾性変形し、環状溝４６ａに達したところで元の形状に弾性復帰することによって環状溝４６ａ内に突入されて係合する。 Further, when assembling the balls 50 and 51 of the inner side row and the outer side row to the outer ring raceway surfaces 40 and 45 on the inner side and the outer side of the outer ring member 30, respectively, first, as shown in FIG. The balls 50 and 51 of the inner side row and the outer side row are assembled to the pockets 62 and 67 of the cages 60 and 65, respectively.
Thereafter, one outer ring raceway surface of the outer ring member 30, for example, the counter bore portion 47 of the outer ring raceway surface 45 on the outer side is arranged on the table upper surface. Here, the outer side retainer 65 in which the outer side row balls 51 are assembled is pushed into the outer side raceway surface 45 of the outer ring member 30 and assembled.
At this time, the engaging portion 69 formed in the annular portion 66 of the outer retainer 65 is forcibly pushed along the inner peripheral surface of the track shoulder 46 of the outer ring raceway surface 45 and elastically deformed. Then, when it reaches the annular groove 46a, it is elastically restored to its original shape, thereby entering and engaging in the annular groove 46a.

次に、テーブル上面に、外輪部材３０のインナ側の外輪軌道面４０のカウンタボア部４２を上側にして配置する。ここで、外輪部材３０のインナ側の外輪軌道面４０に対し、インナ側列の玉５０を組み込んだインナ側の保持器６０を押し込んで組み付ける。
この際、インナ側の保持器６０の環状部６１に形成された係合部６４は、インナ側の外輪軌道面４０の軌道肩部４１の内周面に沿って強制的に押し込まれて弾性変形し、環状溝４１ａに達したところで元の形状に弾性復帰することによって環状溝４１ａ内に突入されて係合する。 Next, the counter bore portion 42 of the outer ring raceway surface 40 on the inner side of the outer ring member 30 is disposed on the upper surface of the table with the counter bore portion 42 on the upper side. Here, the inner side retainer 60 in which the balls 50 in the inner side row are assembled is pushed into the inner side outer ring raceway surface 40 of the outer ring member 30 and assembled.
At this time, the engaging portion 64 formed in the annular portion 61 of the inner cage 60 is forcibly pushed along the inner peripheral surface of the track shoulder portion 41 of the inner outer raceway surface 40 and elastically deformed. Then, when it reaches the annular groove 41a, it is elastically restored to its original shape, thereby entering into and engaging with the annular groove 41a.

前記したように、インナ側及びアウタ側の外輪軌道面４０、４５の軌道肩部４１、４６の内周面に形成された各環状溝４１ａ、４６ａと、インナ側及びアウタ側の保持器６０、６５に形成された係合部６４、６９との係合力によってインナ側及びアウタ側の保持器６０、６５の軸方向への移動を規制することができる。
このため、インナ側及びアウタ側の外輪軌道面４０、４５のそれぞれのカウンタボア部４２、４７を、軸方向に平坦な円筒面（インナ側及びアウタ側の外輪軌道面４０、４５の接触角０°位置Ｐ１、Ｐ２から平行な円筒面）に形成することが可能となり、カウンタ肩部がない構造にすることができる。
言い換えると、カウンタ肩部がない構造であっても、インナ側及びアウタ側の外輪軌道面４０、４５に対しインナ側列及びアウタ側列の玉５０、５１並びにインナ側及びアウタ側の保持器６０、６５が軸方向へ移動して脱落する不具合がない。この結果、外輪部材３０のインナ側及びアウタ側の外輪軌道面４０、４５に対するインナ側列及びアウタ側列の玉５０、５１の組み付けに支障をこたすことがない。 As described above, the annular grooves 41a and 46a formed on the inner peripheral surfaces of the inner and outer outer raceway surfaces 40 and 45, and the inner and outer cages 60 and 46, respectively. The movement of the inner side and outer side cages 60, 65 in the axial direction can be restricted by the engaging force with the engaging portions 64, 69 formed in 65.
For this reason, the counter bore portions 42 and 47 of the inner and outer side outer ring raceway surfaces 40 and 45 are made to be cylindrical surfaces that are flat in the axial direction (the contact angle 0 between the inner side and outer side outer ring raceway surfaces 40 and 45 is 0). (Cylinder surface parallel to the positions P1 and P2), and a structure without a counter shoulder can be obtained.
In other words, even if the structure has no counter shoulder, the inner side and outer side balls 50, 51 and the inner side and outer side cage 60 with respect to the inner side and outer side outer raceway surfaces 40, 45 are used. , 65 moves in the axial direction and does not drop out. As a result, there is no problem in assembling the inner side row and the outer side row balls 50 and 51 to the inner side and outer side outer raceway surfaces 40 and 45 of the outer ring member 30.

また、インナ側及びアウタ側の外輪軌道面４０、４５のそれぞれのカウンタボア部４２、４７にカウンタ肩部がない構造にすると共に、インナ側及びアウタ側の保持器６０、６５の軸方向への移動を規制することによって、従来と比較して、外輪部材３０の鍛造材料の材料費の低減や、旋削加工の手間を軽減することができる。
すなわち、外輪部材３０を鍛造品３０ａから形成する場合、従来のカウンタ肩部の表面を旋削したり研磨するための旋削取り代を確保する必要がなく、図６と図７の二点差線に示すように、旋削取り代３０ｂ、３０ｃを小さくすることが可能となる。
これによって、鍛造品３０ａに対する鍛造材料の材料費の低減や、旋削加工の軽減を図ることができ、コスト低減に効果が大きい。 Further, the counter bore portions 42 and 47 of the inner-side and outer-side outer ring raceway surfaces 40 and 45 have no counter shoulder portions, and the inner-side and outer-side cages 60 and 65 are arranged in the axial direction. By restricting the movement, it is possible to reduce the material cost of the forging material of the outer ring member 30 and the labor of turning as compared with the conventional case.
That is, when the outer ring member 30 is formed from the forged product 30a, there is no need to secure a turning allowance for turning or polishing the surface of the conventional counter shoulder portion, which is shown by a two-dotted line in FIGS. As described above, the turning allowances 30b and 30c can be reduced.
As a result, the material cost of the forging material for the forged product 30a can be reduced and the turning process can be reduced, which is highly effective in reducing the cost.

また、インナ側の保持器６０とアウタ側の保持器６５との係合部６４、６９のうち、少なくとも一方の係合部が環状に形成されて、インナ側の軌道肩部４１の環状溝４１ａ、又はアウタ側の軌道肩部４６の環状溝４６ａの全周に係合するように構成した場合には、軸受内に充填のグリース等の潤滑剤が軸受回転時の遠心力によって小径側から大径側へ流れることを前記環状の係合部６４又は６９と環状溝４１ａ又は４６ａとの係合によって抑制することができる。   Further, at least one of the engaging portions 64 and 69 of the inner side retainer 60 and the outer side retainer 65 is formed in an annular shape, and the annular groove 41a of the inner side track shoulder 41 is formed. In the case where it is configured to engage with the entire circumference of the annular groove 46a of the outer-side raceway shoulder 46, a lubricant such as grease filled in the bearing is increased from the small-diameter side by centrifugal force during rotation of the bearing. The flow to the radial side can be suppressed by the engagement between the annular engaging portion 64 or 69 and the annular groove 41a or 46a.

次に、この発明の実施例２に係る車輪用転がり軸受装置を図９にしたがって説明する。
この実施例２においては、外輪部材３０のインナ側及びアウタ側の外輪軌道面４０、４５のそれぞれの軌道肩部１４１、１４６の間に形成された段差部１４４と、ハブホイール１０のハブ軸１５のインナ側及びアウタ側の内輪軌道面２０、２５の間に形成された段差部１２４とがラビリンス構造を構成するために、僅かな隙間Ｓをもって接近している。
この実施例２のその他の構成は、実施例１と同様に構成されるため、同一構成部分に対し同一符号を付記してその説明は省略する。 Next, a wheel rolling bearing device according to a second embodiment of the present invention will be described with reference to FIG.
In the second embodiment, the stepped portion 144 formed between the respective track shoulder portions 141 and 146 of the outer ring raceway surfaces 40 and 45 on the inner side and the outer side of the outer ring member 30, and the hub shaft 15 of the hub wheel 10. The step portion 124 formed between the inner ring raceway surfaces 20 and 25 on the inner side and the outer side of the inner side and the outer side are close to each other with a slight gap S in order to form a labyrinth structure.
Since the other configuration of the second embodiment is configured in the same manner as the first embodiment, the same components are denoted by the same reference numerals and the description thereof is omitted.

上述したように構成されるこの実施例２において、外輪部材３０のインナ側及びアウタ側の外輪軌道面４０、４５の間の段差部１４４と、内輪部材としてのハブ軸１５のインナ側及びアウタ側の内輪軌道面２０、２５の間の段差部１２４とがラビリンス構造をなすことによって、軸受内に充填のグリース等の潤滑剤が軸受回転時の遠心力によって小径側から大径側へ流れることを抑制することができる。
このため、軸受内に充填のグリース等の潤滑剤の小径側から大径側への流れ抑制する必要がある場合においても、ラビリンス専用の部材を製作して外輪部材３０やハブ軸１５に組み付ける手間を省くことができる。 In the second embodiment configured as described above, the stepped portion 144 between the outer ring raceways 40 and 45 on the inner side and the outer side of the outer ring member 30, and the inner side and outer side of the hub shaft 15 as the inner ring member. The step portion 124 between the inner ring raceway surfaces 20 and 25 forms a labyrinth structure, so that a lubricant such as grease filled in the bearing flows from the small diameter side to the large diameter side due to the centrifugal force when the bearing rotates. Can be suppressed.
For this reason, even when it is necessary to suppress the flow of lubricant such as grease filled in the bearing from the small-diameter side to the large-diameter side, labor for manufacturing the labyrinth dedicated member and assembling it to the outer ring member 30 or the hub shaft 15 is reduced. Can be omitted.

なお、この発明は前記実施例１及び２に限定するものではなく、この発明の要旨を逸脱しない範囲内において、種々なる形態で実施することもできる。   In addition, this invention is not limited to the said Example 1 and 2, In the range which does not deviate from the summary of this invention, it can also be implemented with a various form.

１０ ハブホイール
１５ ハブ軸
２０ インナ側の内輪軌道面
２４ 段差部
２５ アウタ側の内輪軌道面
３０ 外輪部材
４０ インナ側の外輪軌道面
４１ 軌道肩部
４１ａ 環状溝
４４ 段差部
４５ アウタ側の外輪軌道面
４６ 軌道肩部
４６ａ 環状溝
５０ インナ側列の玉
５１ アウタ側列の玉
６０ インナ側の保持器
６４ 係合部
６５ アウタ側の保持器
６９ 係合部 DESCRIPTION OF SYMBOLS 10 Hub wheel 15 Hub axis | shaft 20 Inner side inner ring raceway surface 24 Step part 25 Outer side inner ring raceway surface 30 Outer ring member 40 Inner side outer ring raceway surface 41 Track shoulder part 41a Annular groove 44 Step part 45 Outer side outer ring raceway surface 46 Track shoulder 46a Annular groove 50 Inner side ball 51 Outer side ball 60 Inner side retainer 64 Engagement portion 65 Outer side retainer 69 Engagement portion

Claims (2)

車輪が取り付けられるハブホイールのハブ軸の外周面に、軸方向に所定間隔を隔ててインナ側及びアウタ側の内輪軌道面が形成され、前記ハブ軸の外周に配設される外輪部材の内周面に、軸方向に所定間隔を隔ててインナ側及びアウタ側の外輪軌道面が形成され、前記インナ側及びアウタ側の内輪軌道面と、前記インナ側及びアウタ側の外輪軌道面との間にインナ側列及びアウタ側列の玉がインナ側及びアウタ側の保持器によって保持された状態で転動可能に配列され、前記インナ側列の玉のピッチ円直径をＤ１とし、前記アウタ側列の玉のピッチ円直径をＤ２としたときに、「Ｄ１＜Ｄ２」の関係となるように設定された車輪用転がり軸受装置であって、
前記インナ側及びアウタ側の外輪軌道面のそれぞれのカウンタボア部は、軸方向に平坦な円筒面に形成され、
前記インナ側の外輪軌道面と前記アウタ側の外輪軌道面との間に設けられたそれぞれの軌道肩部の内周面には、環状溝がそれぞれ形成され、
前記インナ側及びアウタ側の保持器には、前記各環状溝に係合して前記外輪部材に対する前記インナ側及びアウタ側の保持器の軸方向への移動を規制する係合部がそれぞれ形成されていることを特徴とする車輪用転がり軸受装置。 An inner ring raceway surface on the inner side and outer side is formed at a predetermined interval in the axial direction on the outer peripheral surface of the hub axle of the hub wheel to which the wheel is attached, and the inner circumference of the outer ring member disposed on the outer circumference of the hub axle. An outer ring raceway surface on the inner side and the outer side is formed on the surface at a predetermined interval in the axial direction, and the inner ring raceway surface on the inner side and the outer side and the outer ring raceway surface on the inner side and the outer side are formed. The balls in the inner side row and the outer side row are arranged so as to be able to roll while being held by the inner side and outer side cages, and the pitch circle diameter of the balls in the inner side row is set to D1, A rolling bearing device for a wheel set to have a relationship of “D1 <D2” when the pitch circle diameter of the balls is D2,
Each counter bore portion of the inner side and outer side outer ring raceway surfaces is formed in a cylindrical surface flat in the axial direction,
An annular groove is formed on the inner peripheral surface of each track shoulder provided between the inner-side outer ring raceway surface and the outer-side outer ring raceway surface,
The inner side and outer side retainers are respectively formed with engaging portions that engage with the respective annular grooves and restrict movement of the inner side and outer side retainers in the axial direction relative to the outer ring member. A rolling bearing device for a wheel characterized by comprising: 請求項１に記載の車輪用転がり軸受装置であって、
インナ側及びアウタ側の外輪軌道面のそれぞれの軌道肩部の間に形成された段差部と、ハブ軸のインナ側及びアウタ側の内輪軌道面の間に形成された段差部とが僅かな隙間をもって接近することによってラビリンス構造をなしていることを特徴とする車輪用転がり軸受装置。 It is a rolling bearing device for wheels according to claim 1,
There is a slight gap between the step formed between the inner and outer outer raceway surfaces of the inner and outer outer raceways and the step formed between the inner and outer raceways of the hub axle. A rolling bearing device for a wheel, characterized in that a labyrinth structure is formed by approaching with a wheel.
JP2011007827A 2011-01-18 2011-01-18 Wheel rolling bearing device Pending JP2012149686A (en)

Priority Applications (1)

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