JP4562461B2 - Wheel bearing device - Google Patents

Wheel bearing device Download PDF

Info

Publication number
JP4562461B2
JP4562461B2 JP2004250386A JP2004250386A JP4562461B2 JP 4562461 B2 JP4562461 B2 JP 4562461B2 JP 2004250386 A JP2004250386 A JP 2004250386A JP 2004250386 A JP2004250386 A JP 2004250386A JP 4562461 B2 JP4562461 B2 JP 4562461B2
Authority
JP
Japan
Prior art keywords
wheel
inner ring
hub
rows
rolling
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
JP2004250386A
Other languages
Japanese (ja)
Other versions
JP2006064146A (en
Inventor
晃司 亀高
晃司 西野
啓 藤村
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
NTN Corp
Original Assignee
NTN Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by NTN Corp filed Critical NTN Corp
Priority to JP2004250386A priority Critical patent/JP4562461B2/en
Publication of JP2006064146A publication Critical patent/JP2006064146A/en
Application granted granted Critical
Publication of JP4562461B2 publication Critical patent/JP4562461B2/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/063—Fixing them on the shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • 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
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
    • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
    • F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
    • F16C19/184—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement
    • F16C19/185—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement with two raceways provided integrally on a part other than a race ring, e.g. a shaft or housing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • 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
    • F16C2326/00—Articles relating to transporting
    • F16C2326/01—Parts of vehicles in general
    • F16C2326/02—Wheel hubs or castors

Landscapes

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

Description

この発明は、ハブ輪に２列の個別の内輪を圧入状態に嵌合させた車輪用軸受装置に関する。   The present invention relates to a wheel bearing device in which two rows of individual inner rings are fitted into a hub ring in a press-fit state.

この種の車輪用軸受装置では、ハブ輪に嵌合したアウトボード側の内輪をハブ輪の外周に形成された段差面に当接させると共に、インボード側の内輪の幅面をナットにより締め付けることで、２列の内輪を軸方向に位置決めしている（例えば特許文献１）。ナット締めの代わりに、ハブ輪のインボード側端に加締部を設けて２列の内輪を位置決めするものもある。
特開２００３−２８７０３６号公報 In this type of wheel bearing device, the inner ring on the outboard side fitted to the hub wheel is brought into contact with the stepped surface formed on the outer periphery of the hub ring, and the width surface of the inner ring on the inboard side is tightened with a nut. Two rows of inner rings are positioned in the axial direction (for example, Patent Document 1). In some cases, instead of nut tightening, a crimping portion is provided at the inboard side end of the hub wheel to position the two rows of inner rings.
JP 2003-287036 A

しかし、上記従来構造では、２列の内輪のハブ輪に対する締代公差が同じであるため、締代を小さくした場合、クリープ発生条件の厳しいアウトボード側の内輪にクリープが発生する。一方、締代を大きくすれば、著しい腐食環境下にあり加締止めとなることもあるインボード側の内輪に、フープ応力が発生し、その腐食による強度低下と相まって、軸受機能を損なう。
特許文献１に開示された車輪用軸受装置では、アウトボード側の内輪の軸方向寸法をインボード側の内輪の軸方向寸法よりも大きくすることで、アウトボード側の内輪でのクリープ発生を防止するようにしている。しかし、この構成では軸受装置の軸方向寸法が大きくなってしまう。 But in the conventional structure, since tightening margin tolerance for the inner ring of the wheel hub of the two rows are the same, the reduction in tightening margin, creep occurs in the inner ring of tough-out board side of creep occurring conditions. On the other hand, if the tightening allowance is increased, hoop stress is generated in the inner ring on the inboard side that is in a significantly corrosive environment and may be caulked, and the bearing function is impaired due to a decrease in strength due to the corrosion.
In the wheel bearing device disclosed in Patent Document 1, the axial dimension of the inner ring on the outboard side is made larger than the axial dimension of the inner ring on the inboard side, thereby preventing the occurrence of creep in the inner ring on the outboard side. Like to do. However, this configuration increases the axial dimension of the bearing device.

この発明の目的は、２列の内輪のうち、クリープ発生条件の厳しいアウトボード側列の内輪ではクリープ発生を防止でき、かつ著しい腐食環境下にあるインボード側列の内輪ではフープ応力の発生の軽減による耐久性確保が図れ、また軸方向寸法も大きくならない車輪用軸受装置を提供することである。   The object of the present invention is to prevent the occurrence of creep in the inner ring of the outboard side row where the creep generation conditions are severe, and the occurrence of hoop stress in the inner ring of the inboard side row in a severe corrosive environment. It is an object of the present invention to provide a wheel bearing device in which durability can be ensured by reduction and the axial dimension is not increased.

この発明の車輪用軸受装置は、ハブ輪の外周に、列毎に個別の２列の内輪を圧入状態に嵌合させた内方部材と、この内方部材の上記各内輪の転走面に対向する２列の転走面を有する外方部材と、これら内外の部材の転走面間に介在した転動体とを備え、車体に対して車輪を回転自在に支持する車輪用軸受装置において、上記ハブ輪の軸部の外径面および上記各内輪の内径面が円筒面であって、両列の内輪の内径面の内径を互いに異ならせ、またはハブ輪の軸部における各内輪嵌合面部分の外径を互いに異ならせることで、後述のハブ輪インボード側端の加締部の未形成状態における上記各内輪のハブ輪に対する締代につき、アウトボード側の内輪の締代の方がインボード側の内輪の締代よりも大きいものとしたことを特徴とする。
この構成によると、両列の内輪の締代に差をつけ、アウトボード側の内輪の締代の方がインボード側の内輪の締代よりも大きいものとしたため、クリープ発生条件の厳しいアウトボード側列の内輪では、大きな締代によってクリープの発生を防止できる。また、著しい腐食環境下にあるインボード側列の内輪では、締代を小さくすることによってフープ応力の発生を軽減でき、フープ応力、および腐食に伴う強度低下による内輪の耐久性低下が防止できる。また、従来例のように、アウトボード側の内輪の軸方向寸法を大きくしないので、軸受装置の軸方向寸法が大きくなることもない。 The wheel bearing device of the present invention has an inner member in which two rows of inner rings are fitted in a press-fit state on the outer periphery of the hub wheel, and a rolling surface of each inner ring of the inner member. an outer member having two opposite rows of rolling surfaces, and a rolling element interposed between the rolling surfaces of the inner and outer members, Te wheel bearing apparatus odor for rotatably supporting a wheel relative to a vehicle body The outer diameter surface of the shaft portion of the hub wheel and the inner diameter surface of each inner ring are cylindrical surfaces, and the inner diameter surfaces of the inner rings of both rows are made different from each other, or each inner ring is fitted to the shaft portion of the hub wheel. by varying the outer diameter of the face portion to each other, every fastening margin with respect to the upper SL wheel hub of each inner ring in an unformed state of the crimp portion of the hub wheel inboard end of the later, the outboard side of the inner ring of the fastening margin This is characterized in that it is larger than the tightening allowance of the inner ring on the inboard side.
According to this configuration, the tightening allowance of the inner rings in both rows is made different, and the tightening allowance of the inner ring on the outboard side is larger than the tightening allowance of the inner ring on the inboard side. In the inner ring of the side row, generation of creep can be prevented by a large tightening allowance. Further, the inner ring of the inboard row under significant corrosive environment, by the reducing the tightening margin can reduce the occurrence of hoop stress, hoop stress, and the inner ring of the durability reduction due the decrease in strength due to corrosion prevention it can. Further, unlike the conventional example, since the axial dimension of the inner ring on the outboard side is not increased, the axial dimension of the bearing device is not increased.

上記ハブ輪のインボード側端の外周に突出する加締部を設け、この加締部でインボード側の内輪の幅面を押し付けることにより、ハブ輪に嵌合した２列の内輪を、ハブ輪の外径面に設けられた段差面と上記加締部との間で軸方向に締め付けたものとする。
この構成のように加締部で内輪を軸方向に固定するようにした場合、加締部に近いインボード側列の内輪は、加締めによるハブ輪軸部の拡径効果でクリープがより発生し難くなる。そのため、２列の内輪の締代に差を付けたことによるアウトボード側列の内輪のクリープ発生防止と、インボード側列の内輪のフープ応力の発生の軽減による耐久性確保の効果がより一層効果的となる。 A caulking portion that protrudes from the outer periphery of the inboard side end of the hub wheel is provided, and by pressing the width surface of the inner ring on the inboard side with the caulking portion, the two rows of inner rings fitted to the hub wheel are connected to the hub wheel. and a stepped surface provided on the outer surface and the crimping portion as that clamped axially between.
When the inner ring is fixed in the axial direction by the crimping portion as in this configuration, the inner ring in the inboard side row near the crimping portion is more likely to creep due to the diameter expansion effect of the hub ring shaft portion due to the crimping. It becomes difficult. Therefore, the effect of securing the durability by reducing the occurrence of hoop stress of the inner ring of the inboard side row and the prevention of creep generation of the inner ring of the inboard side row by making a difference in the tightening allowance of the two rows of inner rings is further enhanced. Become effective.

この発明において、上記転動体が円すいころであり、上記各転走面が円すい面であっても良い。円すいころ軸受タイプの車輪用軸受装置は、荷重条件の厳しいトラックや４輪駆動車等で使用されることが多く、強度の余裕を持たせることが難しい。そのため、この発明における両列の内輪の締代に差をつけたことによるアウトボード側のクリープ発生防止とインボード側のフープ応力の発生軽減の効果がより効果的に発揮される。   In this invention, the rolling element may be a tapered roller, and each rolling surface may be a tapered surface. Tapered roller bearing type wheel bearing devices are often used in trucks, four-wheel drive vehicles, and the like with severe load conditions, and it is difficult to provide sufficient strength. Therefore, the effect of preventing the occurrence of creep on the outboard side and reducing the occurrence of hoop stress on the inboard side due to the difference in the tightening allowances of the inner rings of both rows in the present invention is more effectively exhibited.

この発明の車輪用軸受装置は、ハブ輪の外周に、列毎に個別の２列の内輪を圧入状態に嵌合させた車輪用軸受装置において、上記ハブ輪の軸部の外径面および上記各内輪の内径面が円筒面であって、両列の内輪の内径面の内径を互いに異ならせ、またはハブ輪の軸部における各内輪嵌合面部分の外径を互いに異ならせることで、ハブ輪インボード側端の加締部の未形成状態における上記各内輪のハブ輪に対する締代に差をつけ、アウトボード側の内輪の締代の方がインボード側の内輪の締代よりも大きいものとし、ハブ輪のインボード側端の外周に突出する加締部を設け、この加締部でインボード側の内輪の幅面を押し付けることにより、ハブ輪に嵌合した２列の内輪を、ハブ輪の外径面に設けられた段差面と上記加締部との間で軸方向に締め付けたため、クリープ発生条件の厳しいアウトボード側列の内輪ではクリープ発生を防止でき、かつ著しい腐食環境下にあるインボード側列の内輪ではフープ応力の発生の軽減による耐久性確保が図れる。また、内輪の軸方向寸法を大きくする必要がなく、軸受装置の軸方向寸法が大きくなることもない。
Wheel support bearing assembly of the present invention, the outer periphery of the hub, the inner ring of the respective two rows for each column Te fitted so the wheel support bearing assembly smell pressed state, and the outer diameter surface of the shaft portion of the hub wheel The inner diameter surface of each inner ring is a cylindrical surface, and the inner diameter surfaces of the inner rings in both rows are different from each other, or the outer diameters of the inner ring fitting surface portions in the shaft portion of the hub wheel are different from each other, with a difference in the tightening margin with respect to the upper SL wheel hub of each inner ring in an unformed state of the crimp portion of the hub wheel inboard end, towards the fastening margin of the inner ring of the outboard side than the fastening margin of the inner ring of the inboard side 2 rows of inner rings fitted to the hub ring by providing a caulking part that protrudes on the outer periphery of the inboard side end of the hub wheel, and pressing the width surface of the inner ring on the inboard side with this caulking part Is tightened in the axial direction between the stepped surface provided on the outer diameter surface of the hub wheel and the above-mentioned caulking portion. Because attached, the inner ring of tough outboard side row of creep Condition prevent creep occurs, and attained durable securing by reduction of the generation of hoop stress in the inner ring of the inboard row under substantial corrosion environment. Further, an axial size of the inner ring large Kikusu no need, nor axial dimension of the bearing device is increased.

この発明の参考提案例を図１と共に説明する。この参考提案例の車輪用軸受装置は、複列の円すいころ軸受形式の軸受装置となるものであって、第２．５世代型に分類されるものである。なお、この明細書において、車両に取付けた状態で車両の車幅方向外側寄りとなる側をアウトボード側と言い、車両の中央寄りとなる側をインボード側と呼ぶ。図１では、左側がアウトボード側、右側がインボード側となる。 A reference proposal example of the present invention will be described with reference to FIG. The wheel bearing device of this reference proposal example is a double row tapered roller bearing type bearing device, and is classified into the 2.5th generation type. In this specification, the side closer to the outer side in the vehicle width direction of the vehicle when attached to the vehicle is referred to as the outboard side, and the side closer to the center of the vehicle is referred to as the inboard side. In FIG. 1, the left side is the outboard side and the right side is the inboard side.

この車輪用軸受装置は、駆動輪の支持に適用した例であって、内周に２列の転走面１ａを有する外方部材１と、これら転走面１ａにそれぞれ対向する転走面２ａを有する内方部材２と、これら２列の転走面１ａ，２ａ間に介在した２列の転動体３とを備える。転動体３は円すいころからなり、各列毎に保持器７で保持されている。内外の部材２，１の転走面２ａ，１ａは円すい面である。内外の部材２，１間に形成される環状空間の両端は一対のシール手段１０，１１で密封されている。   This wheel bearing device is an example applied to support of a drive wheel, and has an outer member 1 having two rows of rolling surfaces 1a on the inner periphery, and rolling surfaces 2a respectively facing these rolling surfaces 1a. And two rows of rolling elements 3 interposed between these two rows of rolling surfaces 1a, 2a. The rolling element 3 is formed of a tapered roller and is held by a cage 7 for each row. The rolling surfaces 2a and 1a of the inner and outer members 2 and 1 are conical surfaces. Both ends of the annular space formed between the inner and outer members 2 and 1 are sealed with a pair of sealing means 10 and 11.

外方部材１は固定側の部材となるものであって、外周に車体取付フランジ１ｂを有する一体の部材である。外方部材１は、インボード側端の外周が懸架装置のナックル２１の取付孔に嵌合し、車体取付フランジ１ｂに設けられたボルト孔２２を貫通するボルト２３によってナックル２１に固定されている。   The outer member 1 is a member on the fixed side, and is an integral member having a vehicle body mounting flange 1b on the outer periphery. The outer member 1 is fixed to the knuckle 21 by a bolt 23 whose outer periphery at the inboard side end is fitted into a mounting hole of the knuckle 21 of the suspension device and penetrates a bolt hole 22 provided in the vehicle body mounting flange 1b. .

内方部材２は回転側の部材となるものであって、外周のアウトボード側端に車輪取付フランジ４ａを有するハブ輪４と、このハブ輪４の外周に軸方向に並べてそれぞれ圧入状態に嵌合させた２列の個々の内輪５，６とを有する。これら２列の内輪５，６の外周には、上記各列の転走面２ａが形成されている。ハブ輪４の車輪取付フランジ４ａは、複数のボルト圧入孔２４が設けられ、各孔２４に圧入されたボルト２５により、車輪（図示せず）取付けられる。   The inner member 2 is a member on the rotation side, and has a hub wheel 4 having a wheel mounting flange 4a at the outer end of the outer board and an axial arrangement on the outer periphery of the hub wheel 4 so as to be fitted in a press-fitted state. It has two rows of individual inner rings 5, 6 combined. On the outer circumferences of these two rows of inner rings 5 and 6, the rolling surfaces 2a of each row are formed. The wheel mounting flange 4 a of the hub wheel 4 is provided with a plurality of bolt press-fitting holes 24, and a wheel (not shown) is mounted by a bolt 25 press-fitted into each hole 24.

ハブ輪４の内周孔２６には、等速ジョイント２６の外輪２７のステム部２７ａが挿入され、上記内径孔２６の内面およびステム部２７の外周に設けられたスプライン溝によりスプライン結合される。ステム部２７ａの先端には雄ねじ部２７ａａが設けられ、ナット２８が螺合している。ナット２８は、ハブ輪４のアウトボード側面における内径孔２６の周縁に係合しており、ナット２８を締め付けることにより、等速ジョイント外輪２７の軸方向面２７ｂが内輪６の幅面を軸方向に押し付ける。これにより、両列の内輪５，６が、ハブ輪４の段差面４ｂと等速ジョイント外輪２７の上記軸方向面２７ｂとの間で軸方向に締め付け固定される。上記段差面４ｂは、ハブ輪４の車輪取付フランジ４ａの付近で、インボード側が小径となる面として形成されている。   The stem portion 27 a of the outer ring 27 of the constant velocity joint 26 is inserted into the inner peripheral hole 26 of the hub wheel 4, and splined by spline grooves provided on the inner surface of the inner diameter hole 26 and the outer periphery of the stem portion 27. A male screw portion 27aa is provided at the tip of the stem portion 27a, and a nut 28 is screwed together. The nut 28 is engaged with the peripheral edge of the inner diameter hole 26 on the outboard side surface of the hub wheel 4, and by tightening the nut 28, the axial surface 27 b of the constant velocity joint outer ring 27 extends the width surface of the inner ring 6 in the axial direction. Press. As a result, the inner rings 5 and 6 in both rows are fastened and fixed in the axial direction between the step surface 4 b of the hub wheel 4 and the axial surface 27 b of the constant velocity joint outer ring 27. The step surface 4b is formed in the vicinity of the wheel mounting flange 4a of the hub wheel 4 as a surface having a small diameter on the inboard side.

上記２列の内輪５，６のハブ輪４に対する締代については、互いに差がつけられ、アウトボード側列の内輪５の締代の方が、インボード側列の内輪６の締代よりも大きくされている。この締代の違いは、例えば、両列の内輪５，６の内径面に差を持たせることで生じさせている。なお、ハブ輪４の軸部における各内輪嵌合面部分の外径を異ならせることにより、上記締代の差を付けるようにしても良い。   The tightening allowances of the two rows of inner rings 5 and 6 with respect to the hub wheel 4 are different from each other, and the allowance of the inner ring 5 of the outboard side row is greater than the allowance of the inner ring 6 of the inboard side row. It has been enlarged. This difference in tightening allowance is caused, for example, by giving a difference between the inner diameter surfaces of the inner rings 5 and 6 in both rows. Note that the difference in the tightening allowance may be provided by making the outer diameter of each inner ring fitting surface portion in the shaft portion of the hub wheel 4 different.

上記構成の車輪用軸受装置によると、両列の内輪５，６の締代に差をつけ、アウトボード側の内輪５の締代の方がインボード側の内輪６の締代よりも大きいものとしたため、クリープ発生条件の厳しいアウトボード側列の内輪５では、大きな締代によってクリープの発生を防止できる。また、著しい腐食環境下にあるインボード側列の内輪６では、締代を小さくすることによりってフープ応力の発生を軽減でき、フープ応力、および腐食に伴う強度低下による内輪６の耐久性低下が防止できる。また、従来例のように、アウトボード側の内輪の軸方向寸法を大きくしないので、軸受装置の軸方向寸法が大きくなることもない。   According to the wheel bearing device having the above configuration, the tightening allowance of the inner rings 5 and 6 in both rows is different, and the tightening allowance of the inner ring 5 on the outboard side is larger than that of the inner ring 6 on the inboard side. Therefore, in the inner ring 5 in the outboard side row where the creep generation conditions are severe, the occurrence of creep can be prevented by a large tightening allowance. Further, in the inner ring 6 in the in-board side row under a markedly corrosive environment, the generation of hoop stress can be reduced by reducing the tightening allowance, and the durability of the inner ring 6 is reduced due to the hoop stress and the strength decrease due to corrosion. Can be prevented. Further, unlike the conventional example, since the axial dimension of the inner ring on the outboard side is not increased, the axial dimension of the bearing device is not increased.

なお、上記参考提案例では、ナット２８の締め付けにより、両列の内輪５，６が、ハブ輪４の段差面４ｂと等速ジョイント外輪２７の軸方向面２７ｂとの間で軸方向に締め付け固定されるようにしたが、図２に示すように、ハブ輪４に設けた加締部４ｃで上記軸方向の締め付け固定を行うようにしても良い。すなわち、ハブ輪４のインボード側端に、軸方向に突出する円筒状部分を設けて外径側へ揺動加締で加締めることにより、上記加締部４ｃを形成する。この加締部４ｃをさらに軸方向への加締めることによって、内輪６の幅面を押し付け、両列の内輪５，６を、ハブ輪４の上記段差面４ｂと加締部４ｃとの間で軸方向に締め付ける。
この構成のように加締部４ｃで内輪５，６を軸方向に固定するようにした場合、加締部に近いインボード側列の内輪６は、加締めによるハブ輪軸部の拡径効果でクリープがより発生し難くなる。そのため、２列の内輪５，６の締代に差を付けたことによるアウトボード側列の内輪５のクリープ発生防止と、インボード側列の内輪６のフープ応力の発生の軽減による耐久性確保の効果がより一層効果的となる。 In the reference proposal example , the nuts 28 are tightened so that the inner rings 5 and 6 in both rows are tightened and fixed in the axial direction between the stepped surface 4 b of the hub wheel 4 and the axial surface 27 b of the constant velocity joint outer ring 27. However, as shown in FIG. 2, the axial fastening may be performed by a caulking portion 4 c provided on the hub wheel 4. That is, the caulking portion 4c is formed by providing a cylindrical portion protruding in the axial direction at the inboard side end of the hub wheel 4 and caulking to the outer diameter side by swing caulking. By further crimping the caulking portion 4c in the axial direction, the width surface of the inner ring 6 is pressed, and the inner rings 5 and 6 in both rows are pivoted between the stepped surface 4b of the hub wheel 4 and the caulking portion 4c. Tighten in the direction.
When the inner rings 5 and 6 are fixed in the axial direction by the caulking portion 4c as in this configuration, the inner ring 6 in the inboard side row close to the caulking portion is due to the diameter expansion effect of the hub wheel shaft portion by caulking. Creep is less likely to occur. Therefore, it is possible to prevent creep of the inner ring 5 in the outboard side row by making a difference in the tightening allowance of the two rows of inner rings 5 and 6, and to ensure durability by reducing occurrence of hoop stress in the inner ring 6 in the inboard side row. The effect becomes even more effective.

図３はこの発明の他の実施形態を示す。この実施形態の車輪用軸受装置は、複列のアンギュラ玉軸受形式としたものである。すなわち、図１に示した参考提案例である複列の円すいころ軸受形式の車輪用軸受装置における転動体３を、円すいころからボールに置き換えたものである。また、この実施形態では、ハブ輪４のインボード側端に突出させた円筒状部分を外周側へ揺動加締した加締部４ｃで、インボード側の内輪６の幅面を押し付けるようにしている。その他の構成は参考提案例と同様である。
この構成の場合も、２列の内輪５，６をハブ輪４の加締部４ｃで軸方向に締めつける構成としたため、アウトボード側列の内輪５のクリープ発生防止と、インボード側列の内輪６のフープ応力の発生軽減による耐久性確保の効果がより一層効果的なものとなる。 FIG. 3 shows another embodiment of the present invention. The wheel bearing device of this embodiment is a double-row angular contact ball bearing type. That, in which the rolling elements 3, replacing the tapered rollers to the ball in the wheel support bearing assembly of the tapered roller bearing type double row is a reference proposed example shown in FIG. Further, in this embodiment, the width surface of the inner ring 6 on the inboard side is pressed by the caulking portion 4c obtained by swinging and caulking the cylindrical portion projected to the inboard side end of the hub wheel 4 to the outer peripheral side. Yes. Other configurations are the same as those of the reference proposal example .
Also in this configuration, the inner rings 5 and 6 in the two rows are tightened in the axial direction by the caulking portion 4c of the hub wheel 4, so that the occurrence of creep of the inner ring 5 in the outboard side row can be prevented and the inner ring in the inboard side row can be prevented. The effect of ensuring durability by reducing the occurrence of the hoop stress of 6 becomes even more effective.

なお、図３のアンギュラ玉軸受形式の実施形態において、図１の例と同様に、等速ジョイント外輪２７のステム部２７ａにねじ込んだナット２８の締め付けにより、ナット５，６を固定しても良い。これの構成の場合も、上記と同様なクリープ発生防止、フープ応力の発生の軽減による耐久性確保の効果が得られる。   In the embodiment of the angular ball bearing type in FIG. 3, the nuts 5 and 6 may be fixed by tightening the nut 28 screwed into the stem portion 27a of the constant velocity joint outer ring 27 as in the example of FIG. . In the case of this configuration, the same effect of ensuring durability by preventing the occurrence of creep and reducing the occurrence of hoop stress can be obtained.

図４は、この発明を第１世代型で円すいころ軸受形式の車輪用軸受装置に適用した例である。この例は、図１に示す参考提案例において、外方部材１は車体取付フランジ１ｂを有せず、外径面が円筒面とされ、ナックル２１の軸受取付孔２１ａに圧入嵌合して取付けられる。圧入した外方部材１は、ナックル２１の軸受取付孔２１ａの内端の段差面２１ｂと、軸受取付孔２１ａの内径面の止め輪溝２１ｃに嵌合した止め輪３１とにより軸方向に固定される。その外の構成は図１に示す参考提案例と同じである。
この構成の場合も、参考提案例と同様なクリープ発生防止、フープ応力の発生の軽減による耐久性確保の効果が得られる。 FIG. 4 shows an example in which the present invention is applied to a first generation type tapered roller bearing type wheel bearing device. This example, in Reference proposed example shown in FIG. 1, the outer member 1 will not have a body mounting flange 1b, an outer diameter surface is a cylindrical surface, press-fitted into the bearing mounting hole 21a of the knuckle 21 mounted It is done. The press-fitted outer member 1 is fixed in the axial direction by a stepped surface 21b at the inner end of the bearing mounting hole 21a of the knuckle 21 and a retaining ring 31 fitted in a retaining ring groove 21c on the inner diameter surface of the bearing mounting hole 21a. The The other configuration is the same as the reference proposal example shown in FIG.
In the case of this configuration, the same effect of ensuring durability by preventing the occurrence of creep and reducing the occurrence of hoop stress can be obtained as in the case of the reference proposal example .

図５は、この発明を第１世代型でアンギュラ玉軸受形式の車輪用軸受装置に適用した参考提案例である。この例は、図４に示す参考提案例において、転動体３をボールとし、転走面１ａ，２ａを円弧状の断面としてアンギュラ玉軸受形式としたものである。その他の構成，効果は図４に示す参考提案例と同様である。 FIG. 5 shows an example of a reference proposal in which the present invention is applied to a first generation type angular ball bearing type wheel bearing device. In this example of reference proposal shown in FIG. 4, the rolling element 3 is a ball, and the rolling surfaces 1a and 2a are arc-shaped cross sections to form an angular ball bearing. Other configurations and effects are the same as those of the reference proposal example shown in FIG.

この発明の参考提案例にかかる車輪用軸受装置の断面図である。It is sectional drawing of the wheel bearing apparatus concerning the reference proposal example of this invention. この発明の実施形態にかかる車輪用軸受装置の断面図である。It is a sectional view of a wheel bearing device according to implementation embodiments of the present invention. この発明の他の実施形態にかかる車輪用軸受装置の断面図である。It is sectional drawing of the wheel bearing apparatus concerning other embodiment of this invention. この発明の他の参考提案例にかかる車輪用軸受装置の断面図である。It is sectional drawing of the wheel bearing apparatus concerning the other reference proposal example of this invention. この発明のさらに他の参考提案例にかかる車輪用軸受装置の断面図である。It is sectional drawing of the wheel bearing apparatus concerning the further another reference proposal example of this invention.

符号の説明Explanation of symbols

１…外方部材
１ａ…転走面
２…内方部材
２ａ…転走面
３…転動体
４…ハブ輪
４ａ…加締部
５，６…内輪
２７…等速ジョイント外輪 DESCRIPTION OF SYMBOLS 1 ... Outer member 1a ... Rolling surface 2 ... Inner member 2a ... Rolling surface 3 ... Rolling body 4 ... Hub wheel 4a ... Clamping part 5, 6 ... Inner ring 27 ... Constant velocity joint outer ring

Claims (2)

ハブ輪の外周に、列毎に個別の２列の内輪を圧入状態に嵌合させた内方部材と、この内方部材の上記各内輪の転走面に対向する２列の転走面を有する外方部材と、これら内外の部材の転走面間に介在した転動体とを備え、車体に対して車輪を回転自在に支持する車輪用軸受装置において、
ハブ輪のインボード側端の外周に突出する加締部を設け、この加締部でインボード側の内輪の幅面を押し付けることにより、ハブ輪に嵌合した２列の内輪を、ハブ輪の外径面に設けられた段差面と上記加締部との間で軸方向に締め付けたものであり、上記ハブ輪の軸部の外径面および上記各内輪の内径面が円筒面であって、両列の内輪の内径面の内径を互いに異ならせ、またはハブ輪の軸部における各内輪嵌合面部分の外径を互いに異ならせることで、上記加締部の未形成状態における、上記各内輪のハブ輪に対する締代につき、アウトボード側の内輪の締代の方がインボード側の内輪の締代よりも大きいものとしたことを特徴とする車輪用軸受装置。 On the outer periphery of the hub wheel, there are an inner member in which two rows of inner rings are fitted in a press-fitted state for each row, and two rows of rolling surfaces facing the rolling surface of each inner ring of the inner member. the outer member and, a rolling element interposed between the rolling surfaces of the inner and outer members, a wheel bearing apparatus odor for rotatably supporting a wheel relative to a vehicle body having Te,
The crimp portions projecting to the outer periphery of the inboard end of the hub wheel is provided, by pressing the width surface of the inner ring of the inboard side with the crimping portion, the inner ring of the second column fitted to the wheel hub, the wheel hub between the stepped surface and the crimping portion provided on the outer diameter surface it is as hereinbefore tighten axially outer surface and the inner races of the inner diameter surface of the shaft portion of the hub wheel in the cylindrical surface of the By changing the inner diameters of the inner diameter surfaces of the inner rings of the two rows from each other, or by changing the outer diameters of the inner ring fitting surface portions in the shaft portion of the hub ring from each other, The wheel bearing device according to claim 1, wherein the inner ring on the outboard side is larger than the inner ring on the inboard side . 請求項１において、上記転動体が円すいころであり、上記各転走面が円すい面である車輪用軸受装置。   The wheel bearing device according to claim 1, wherein the rolling elements are tapered rollers, and each rolling surface is a tapered surface.
JP2004250386A 2004-08-30 2004-08-30 Wheel bearing device Active JP4562461B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2004250386A JP4562461B2 (en) 2004-08-30 2004-08-30 Wheel bearing device

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2004250386A JP4562461B2 (en) 2004-08-30 2004-08-30 Wheel bearing device

Publications (2)

Publication Number Publication Date
JP2006064146A JP2006064146A (en) 2006-03-09
JP4562461B2 true JP4562461B2 (en) 2010-10-13

Family

ID=36110802

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2004250386A Active JP4562461B2 (en) 2004-08-30 2004-08-30 Wheel bearing device

Country Status (1)

Country Link
JP (1) JP4562461B2 (en)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007327564A (en) * 2006-06-08 2007-12-20 Ntn Corp Bearing device for wheel
JP2008002536A (en) * 2006-06-21 2008-01-10 Ntn Corp Bearing device for wheel
JP4948063B2 (en) * 2006-07-14 2012-06-06 Ｎｔｎ株式会社 Wheel bearing device
DE602007010417D1 (en) 2007-02-23 2010-12-23 Ntn Toyo Bearing Co Ltd Bearing device for a wheel
JP2013092246A (en) 2011-10-27 2013-05-16 Jtekt Corp Wheel bearing device

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0617827A (en) * 1992-07-03 1994-01-25 Koyo Seiko Co Ltd Abnormality announcement device
JPH09133139A (en) * 1995-11-10 1997-05-20 Nippon Seiko Kk Double row angular contact ball bearing
JP2003028150A (en) * 2001-07-18 2003-01-29 Koyo Seiko Co Ltd Bearing device
JP2004169761A (en) * 2002-11-18 2004-06-17 Nsk Ltd Double row tapered rolling bearing with combined seal ring

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0617827A (en) * 1992-07-03 1994-01-25 Koyo Seiko Co Ltd Abnormality announcement device
JPH09133139A (en) * 1995-11-10 1997-05-20 Nippon Seiko Kk Double row angular contact ball bearing
JP2003028150A (en) * 2001-07-18 2003-01-29 Koyo Seiko Co Ltd Bearing device
JP2004169761A (en) * 2002-11-18 2004-06-17 Nsk Ltd Double row tapered rolling bearing with combined seal ring

Also Published As

Publication number Publication date
JP2006064146A (en) 2006-03-09

Similar Documents

Publication Publication Date Title
JP4562461B2 (en) Wheel bearing device
JP4519003B2 (en) Wheel bearing device
JP4606883B2 (en) Wheel bearing device
JP5200418B2 (en) Bearing unit
JP2008039106A (en) Bearing device for wheel
JP2006112532A (en) Bearing for wheel
JP4948063B2 (en) Wheel bearing device
JP4519004B2 (en) Wheel bearing device
JP2007327565A (en) Bearing device for wheel
JP4519005B2 (en) Wheel bearing device
JP2009058077A (en) Wheel bearing unit
JP2006105343A (en) Bearing device for wheel
JP2008247274A (en) Wheel bearing device
JP4467480B2 (en) Wheel bearing device and caulking method thereof
JP4986512B2 (en) Wheel bearing device
JP4553676B2 (en) Wheel bearing device
JP2006336759A (en) Bearing device for wheel
JP5143442B2 (en) Drive wheel bearing device
JP2006118626A (en) Bearing device for wheel
JP2006153149A (en) Bearing device for wheel
JP2007327507A (en) Wheel bearing device
JP2008057717A (en) Bearing device for wheel
JP2008014448A (en) Wheel bearing device and its manufacturing method
JP2007327564A (en) Bearing device for wheel
JP2008018759A (en) Bearing device for wheel

Legal Events

Date Code Title Description
A621 Written request for application examination

Free format text: JAPANESE INTERMEDIATE CODE: A621

Effective date: 20070413

A977 Report on retrieval

Free format text: JAPANESE INTERMEDIATE CODE: A971007

Effective date: 20090528

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20090602

A521 Request for written amendment filed

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20090730

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20100216

A521 Request for written amendment filed

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20100402

TRDD Decision of grant or rejection written
A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

Effective date: 20100727

A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

A61 First payment of annual fees (during grant procedure)

Free format text: JAPANESE INTERMEDIATE CODE: A61

Effective date: 20100727

FPAY Renewal fee payment (event date is renewal date of database)

Free format text: PAYMENT UNTIL: 20130806

Year of fee payment: 3

R150 Certificate of patent or registration of utility model

Ref document number: 4562461

Country of ref document: JP

Free format text: JAPANESE INTERMEDIATE CODE: R150

Free format text: JAPANESE INTERMEDIATE CODE: R150

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250