JPH1137146A - Rolling bearing unit for wheels - Google Patents
Rolling bearing unit for wheelsInfo
- Publication number
- JPH1137146A JPH1137146A JP9191433A JP19143397A JPH1137146A JP H1137146 A JPH1137146 A JP H1137146A JP 9191433 A JP9191433 A JP 9191433A JP 19143397 A JP19143397 A JP 19143397A JP H1137146 A JPH1137146 A JP H1137146A
- Authority
- JP
- Japan
- Prior art keywords
- inner ring
- peripheral surface
- diameter
- wheel
- rolling bearing
- 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.)
- Pending
Links
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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
- F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
- F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
- F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
- F16D2003/22303—Details of ball cages
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/80—Technologies aiming to reduce greenhouse gasses emissions common to all road transportation technologies
- Y02T10/86—Optimisation of rolling resistance, e.g. weight reduction
Landscapes
- Support Of The Bearing (AREA)
- Rolling Contact Bearings (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】この発明に係る車輪用転がり
軸受ユニットは、ＦＦ車（前置エンジン前輪駆動車）又
は４ＷＤ車（四輪駆動車）の前輪を、懸架装置に対して
回転自在に支持する為に利用する。BACKGROUND OF THE INVENTION A wheel rolling bearing unit according to the present invention rotatably supports a front wheel of an FF vehicle (front-engine front wheel drive vehicle) or a 4WD vehicle (four-wheel drive vehicle) with respect to a suspension device. Use to do.
【０００２】[0002]
【従来の技術】車輪を懸架装置に対して回転自在に支持
する為に、外輪と内輪とを転動体を介して回転自在に組
み合わせた車輪用転がり軸受ユニットが、各種使用され
ている。又、操舵輪であると同時に駆動輪でもあるＦＦ
車或は４ＷＤ車の前輪を支持する為の車輪用転がり軸受
ユニットは、等速ジョイントと組み合わせて、車輪に付
与された舵角に拘らず、駆動軸の回転を上記車輪に対し
て円滑に（等速性を確保して）伝達する必要がある。こ
の様な等速ジョイントと組み合わせて、しかも比較的小
型且つ軽量に構成できる車輪用転がり軸受ユニットとし
て従来から、特開平７−３１７７５４号公報に記載され
たものが知られている。2. Description of the Related Art In order to rotatably support a wheel with respect to a suspension device, various types of rolling bearing units for wheels are used in which an outer ring and an inner ring are rotatably combined via rolling elements. In addition, the FF which is both a steering wheel and a driving wheel
A rolling bearing unit for wheels for supporting the front wheels of a car or a 4WD car is combined with a constant velocity joint to smoothly rotate the drive shaft with respect to the wheels irrespective of the steering angle given to the wheels ( It must be transmitted (with constant velocity). A rolling bearing unit for a wheel which can be configured to be relatively small and lightweight in combination with such a constant velocity joint is disclosed in Japanese Patent Application Laid-Open No. 7-317754.
【０００３】図４は、この公報に記載された従来構造を
示している。車両への組み付け状態で、懸架装置に支持
した状態で回転しない外輪１（外輪相当部材）は、外周
面にこの懸架装置に支持する為の第一の取付フランジ２
を、内周面に複列の外輪軌道２７、２７を、それぞれ有
する。上記外輪１の内側には、第一、第二の内輪部材
３、４を組み合わせて成るハブ５（内輪相当部材）を配
置している。このうちの第一の内輪部材３は、外周面の
一端寄り（図４の左寄り）部分に車輪を支持する為の第
二の取付フランジ６を、同じく他端寄り（図４の右寄
り）部分に第一の内輪軌道７を、それぞれ設けた円筒状
に形成している。これに対して、上記第二の内輪部材４
は、一端部（図４の左端部）を、上記第一の内輪部材３
を外嵌固定する為の円筒部８とし、他端部（図４の右端
部）を等速ジョイント２２の外輪となるハウジング部９
とし、中間部外周面に第二の内輪軌道１０を設けてい
る。そして、上記各外輪軌道２７、２７と上記第一、第
二の内輪軌道７、１０との間にそれぞれ複数個ずつの転
動体１１、１１を設ける事により、上記外輪１の内側に
上記ハブ５を、回転自在に設けている。FIG. 4 shows a conventional structure described in this publication. An outer ring 1 (an outer ring-equivalent member) that does not rotate in a state of being mounted on a vehicle and supported by a suspension device has a first mounting flange 2 on its outer peripheral surface for supporting the suspension device.
Are provided on the inner peripheral surface of the outer ring raceways 27, 27, respectively. Inside the outer ring 1, a hub 5 (an inner ring equivalent member) formed by combining the first and second inner ring members 3 and 4 is arranged. The first inner ring member 3 has a second mounting flange 6 for supporting the wheel at one end (leftward in FIG. 4) of the outer peripheral surface, and a second mounting flange 6 at the other end (rightward in FIG. 4). The first inner raceway 7 is formed in a cylindrical shape provided for each. On the other hand, the second inner ring member 4
Is connected to one end (the left end in FIG. 4) of the first inner ring member 3.
Is a cylindrical portion 8 for externally fitting and fixing, and the other end portion (right end portion in FIG. 4) is a housing portion 9 serving as an outer ring of the constant velocity joint 22.
The second inner raceway 10 is provided on the outer peripheral surface of the intermediate portion. By providing a plurality of rolling elements 11, 11 between the outer raceways 27, 27 and the first and second inner raceways 7, 10, respectively, the hub 5 is provided inside the outer race 1. Are rotatably provided.
【０００４】又、上記第一の内輪部材３の内周面と上記
第二の内輪部材４の外周面との互いに整合する位置に
は、それぞれ係止溝１２、１３を形成すると共に、止め
輪１４を、これら両係止溝１２、１３に掛け渡す状態で
設けて、上記第一の内輪部材３が上記第二の内輪部材４
から抜け出るのを防止している。更に、上記第二の内輪
部材４の一端面（図４の左端面）外周縁部と、上記第一
の内輪部材３の内周面に形成した段部１５の内周縁部と
に溶接１６を施して、上記第一、第二の内輪部材３、４
同士を結合固定している。[0004] Locking grooves 12 and 13 are formed at positions where the inner peripheral surface of the first inner ring member 3 and the outer peripheral surface of the second inner ring member 4 are aligned with each other, and a retaining ring is provided. 14 is provided in such a manner as to extend over both locking grooves 12, 13, so that the first inner ring member 3 is connected to the second inner ring member 4.
Prevents getting out of. Further, a weld 16 is attached to the outer peripheral edge of one end face (left end face in FIG. 4) of the second inner ring member 4 and the inner peripheral edge of a step 15 formed on the inner peripheral face of the first inner ring member 3. The first and second inner ring members 3, 4
They are connected and fixed.
【０００５】更に、上記外輪１の両端開口部と上記ハブ
５の中間部外周面との間には、ステンレス鋼板等の金属
製で略円筒状のカバー１９ａ、１９ｂと、ゴム、エラス
トマー等の弾性材製で円環状のシールリング２０ａ、２
０ｂとを設けている。これらカバー１９ａ、１９ｂ及び
シールリング２０ａ、２０ｂは、上記複数の転動体１
１、１１を設置した部分と外部とを遮断し、この部分に
存在するグリースが外部に漏出するのを防止すると共
に、この部分に雨水、塵芥等の異物が侵入する事を防止
する。又、上記第二の内輪部材４の中間部内側には、こ
の第二の内輪部材４の内側を塞ぐ隔板部２１を設けて、
この第二の内輪部材４の剛性を確保すると共に、この第
二の内輪部材４の先端（図４の左端）開口からこの第二
の内輪部材４の内側に入り込んだ異物が、前記ハウジン
グ部９の内側に設けた等速ジョイント２２部分にまで達
する事を防止している。Further, between the openings at both ends of the outer race 1 and the outer peripheral surface of the intermediate portion of the hub 5, a substantially cylindrical cover 19a, 19b made of a metal such as a stainless steel plate, and an elastic material such as rubber or elastomer are provided. Annular seal ring 20a, 2
0b. The covers 19a and 19b and the seal rings 20a and 20b
The portion in which the components 1 and 11 are installed and the outside are shut off to prevent the grease existing in this portion from leaking out, and to prevent foreign matters such as rainwater and dust from entering this portion. Further, inside the intermediate portion of the second inner ring member 4, a partition plate portion 21 for closing the inside of the second inner ring member 4 is provided,
The rigidity of the second inner race member 4 is ensured, and foreign matter that has entered the inside of the second inner race member 4 from the opening (the left end in FIG. 4) of the second inner race member 4 is removed by the housing portion 9. Is prevented from reaching the constant velocity joint 22 provided inside.
【０００６】又、上記等速ジョイント２２は、上記ハウ
ジング部９と、内輪１７と、保持器２３と、複数個の玉
１８とから成る。このうちの内輪１７は、エンジンによ
りトランスミッションを介して回転駆動される、図示し
ない駆動軸の先端部に固定される。この内輪１７の外周
面には、断面円弧形の内側係合溝２４を６本、円周方向
に亙り等間隔に、それぞれ円周方向に対し直角方向に形
成している。又、上記ハウジング部９の内周面で上記内
側係合溝２４と対向する位置には、やはり断面円弧形の
外側係合溝２５を６本、円周方向に対し直角方向に形成
している。又、上記保持器２３は、断面円弧状で全体を
円環状に形成しており、上記内輪１７の外周面とハウジ
ング部９の内周面との間に挟持している。この保持器２
３の円周方向６個所位置で、上記内側、外側両係合溝２
４、２５に整合する位置には、それぞれポケット２６を
形成し、これら各ポケット２６の内側にそれぞれ１個ず
つ、合計６個の上記玉１８を保持している。これら各玉
１８は、それぞれ上記各ポケット２６に保持された状態
で、上記内側、外側両係合溝２４、２５に沿い転動自在
である。The constant velocity joint 22 comprises the housing 9, the inner race 17, a retainer 23, and a plurality of balls 18. The inner ring 17 is fixed to a distal end of a drive shaft (not shown) that is rotationally driven by the engine via a transmission. Six inner engagement grooves 24 having an arc-shaped cross section are formed on the outer peripheral surface of the inner ring 17 at regular intervals in the circumferential direction, and are respectively perpendicular to the circumferential direction. Six outer engaging grooves 25, also having a circular cross section, are formed at positions on the inner peripheral surface of the housing portion 9 facing the inner engaging grooves 24 in a direction perpendicular to the circumferential direction. I have. The retainer 23 has an arcuate cross section and is formed in an annular shape as a whole, and is held between the outer peripheral surface of the inner ring 17 and the inner peripheral surface of the housing portion 9. This cage 2
3, the inner and outer engaging grooves 2
Pockets 26 are formed at positions corresponding to 4 and 25, respectively, and a total of six balls 18 are held inside each pocket 26, one for each. Each of the balls 18 is free to roll along the inner and outer engagement grooves 24 and 25 while being held in the respective pockets 26.
【０００７】上述の様に構成する車輪用転がり軸受ユニ
ットを車両に組み付ける際には、第一の取付フランジ２
により外輪１を懸架装置に支持し、第二の取付フランジ
６により駆動輪でもある前輪を第一の内輪部材３に固定
する。又、エンジンによりトランスミッションを介して
回転駆動される、図示しない駆動軸の先端部を、等速ジ
ョイントを構成する内輪１７の内側にスプライン係合さ
せる。自動車の走行時には、上記内輪１７の回転を、複
数の玉１８を介して第二の内輪部材４を含むハブ５に伝
達し、上記前輪を回転駆動する。When assembling the rolling bearing unit for a wheel configured as described above to a vehicle, the first mounting flange 2
, The outer wheel 1 is supported by the suspension device, and the front wheel, which is also a driving wheel, is fixed to the first inner wheel member 3 by the second mounting flange 6. Further, a tip end of a drive shaft (not shown), which is rotationally driven by the engine via a transmission, is spline-engaged inside the inner race 17 constituting a constant velocity joint. When the automobile is running, the rotation of the inner wheel 17 is transmitted to the hub 5 including the second inner wheel member 4 via the plurality of balls 18 to rotate the front wheel.
【０００８】[0008]
【発明が解決しようとする課題】図４に示した従来の車
輪用転がり軸受ユニットの場合、装置の小型・軽量化を
図る事が難しい。この理由は、次の通りである。上述し
た従来の車輪用転がり軸受ユニットに一体に組み込む等
速ジョイント２２に設ける内側、外側両係合溝２４、２
５と玉１８との数は、通常、それぞれ６個ずつとしてい
る。この様な等速ジョイント２２を一体に組み込んだ従
来の車輪用転がり軸受ユニットの場合、この等速ジョイ
ント２２を構成する上記両係合溝２４、２５と各玉１８
の転動面との転がり疲れ寿命を確保しつつ、必要とする
トルクの伝達を可能にする都合上、上記等速ジョイント
２２を構成する各玉１８の外径寸法を、或る程度大きく
する必要がある。この為、上記従来の車輪用転がり軸受
ユニットの場合には、上記各玉１８の外接円の直径の大
きさに基づいて決定される上記各外側係合溝２５の外接
円の直径が、上記ハブ５の中間部外周面に複列に設けた
第一、第二の内輪軌道７、１０のうち、第二の内輪部材
４の外周面に形成した第二の内輪軌道１０の直径よりも
大きくなる。In the case of the conventional rolling bearing unit for a wheel shown in FIG. 4, it is difficult to reduce the size and weight of the device. The reason is as follows. The inner and outer engagement grooves 24, 2 provided in the constant velocity joint 22 integrated into the above-described conventional wheel rolling bearing unit.
The number of balls 5 and balls 18 is usually six each. In the case of a conventional rolling bearing unit for a wheel in which such a constant velocity joint 22 is integrally incorporated, the two engagement grooves 24 and 25 and each ball 18 constituting the constant velocity joint 22 are formed.
The outer diameter of each ball 18 constituting the above constant velocity joint 22 needs to be increased to a certain extent in order to make it possible to transmit the required torque while securing the rolling fatigue life with the rolling surface. There is. For this reason, in the case of the above-mentioned conventional rolling bearing unit for a wheel, the diameter of the circumscribed circle of each of the outer engagement grooves 25 determined based on the diameter of the circumscribed circle of each of the balls 18 is the hub diameter. 5 is larger than the diameter of the second inner raceway 10 formed on the outer peripheral surface of the second inner race member 4 among the first and second inner raceways 7 and 10 provided in a double row on the outer peripheral surface of the intermediate portion 5. .
【０００９】この為、上記従来の車輪用転がり軸受ユニ
ットの場合、上記外輪１とこの外輪１の内周面に設けた
複列の外輪軌道２７、２７と上記ハブ５の中間部とこの
ハブ５の中間部外周面に設けた第一、第二の内輪軌道
７、１０とこれら第一、第二の内輪軌道７、１０と上記
各外輪軌道２７、２７との間にそれぞれ複数個ずつ設け
た転動体１１、１１とから成る転がり軸受部分と、上記
等速ジョイント２２部分とを、図４に示す様に、軸方向
に亙り互いに直列に配置している。ところが、この様に
転がり軸受部分と等速ジョイント２２部分とを直列に配
置した場合、車輪用転がり軸受ユニット全体としての軸
方向寸法が大きくなり、その分、装置全体の重量が嵩
む。車輪用転がり軸受ユニットの重量の増大は、自動車
のばね下荷重の増大につながる為、この車輪用転がり軸
受ユニットの小型・軽量化が望まれる。Therefore, in the case of the above-mentioned conventional rolling bearing unit for a wheel, the outer ring 1, double-row outer ring tracks 27, 27 provided on the inner peripheral surface of the outer ring 1, an intermediate portion of the hub 5, and the hub 5 The first and second inner ring raceways 7 and 10 provided on the outer peripheral surface of the intermediate portion, and a plurality of first and second inner raceways 7 and 10 are provided between the first and second inner raceways 7 and 10 and the outer raceways 27 and 27, respectively. As shown in FIG. 4, the rolling bearing portion composed of the rolling elements 11 and the constant velocity joint 22 are arranged in series with each other in the axial direction. However, when the rolling bearing portion and the constant velocity joint 22 are arranged in series as described above, the axial dimension of the entire wheel rolling bearing unit increases, and the weight of the entire device increases accordingly. Since an increase in the weight of the wheel rolling bearing unit leads to an increase in unsprung load of the automobile, it is desired to reduce the size and weight of the wheel rolling bearing unit.
【００１０】車輪用転がり軸受ユニットの軸方向寸法を
小さくすべく、上記第二の内輪軌道１０の直径を上記各
外側係合溝２５の外接円の直径よりも大きくする事によ
り、この第二の内輪軌道１０と上記各外側係合溝２５の
一部とを直径方向に亙り互いに重畳させる事も考えられ
る。ところが、単に上記第二の内輪軌道１０の直径を大
きくした場合には、車輪用転がり軸受ユニットの軸方向
寸法を小さくできる代わりに、直径方向寸法が徒に大き
くなり、その分、装置全体の重量も嵩む為、車輪用転が
り軸受ユニットの小型・軽量化を実現できない。本発明
の車輪用転がり軸受ユニットは、上述の様な事情に鑑み
て、車輪用転がり軸受ユニットの小型・軽量化を図るべ
く発明したものである。In order to reduce the axial dimension of the wheel rolling bearing unit, the diameter of the second inner raceway 10 is made larger than the diameter of the circumscribed circle of each of the outer engagement grooves 25, so that the second inner raceway 10 has a second diameter. It is also conceivable that the inner raceway 10 and a part of each of the outer engagement grooves 25 overlap with each other in the diametric direction. However, if the diameter of the second inner raceway 10 is simply increased, the axial dimension of the wheel rolling bearing unit can be reduced, but the diameter dimension is increased, and the weight of the entire apparatus is correspondingly increased. Therefore, the size and weight of the rolling bearing unit for wheels cannot be reduced. The rolling bearing unit for a wheel according to the present invention has been invented in view of the above-described circumstances to reduce the size and weight of the rolling bearing unit for a wheel.
【００１１】[0011]
【課題を解決するための手段】本発明の車輪用転がり軸
受ユニットは、前述した従来の車輪用転がり軸受ユニッ
トと同様に、外周面に懸架装置に支持する為の第一の取
付フランジを、内周面に複列の外輪軌道を、それぞれ有
し、使用時にも回転しない外輪相当部材と、外周面の一
端寄り部分に車輪を支持する為の第二の取付フランジ
を、同じく中間部に複列の内輪軌道を、それぞれ設け、
他端部を等速ジョイントの外輪となるハウジング部とし
た、使用時に回転する内輪相当部材と、上記各外輪軌道
と上記各内輪軌道との間にそれぞれ複数個ずつ転動自在
に設けられた転動体とを備える。又、このうちの等速ジ
ョイントは、駆動軸の端部に固定される内輪と、この内
輪の外周面の円周方向等間隔位置に、それぞれ円周方向
に対し直角方向に形成された断面円弧形の複数の内側係
合溝と、上記ハウジング部の内周面で上記内側係合溝と
対向する位置に、円周方向に対し直角方向に形成された
断面円弧形の複数の外側係合溝と、上記内輪の外周面と
ハウジング部の内周面との間に挟持され、上記内側、外
側両係合溝に整合する位置にそれぞれポケットを形成し
た保持器と、これら各ポケットの内側に保持された状態
で、上記内側、外側両係合溝に沿う転動を自在とされ
た、複数個の玉とから成る。特に、本発明の車輪用転が
り軸受ユニットに於いては、上記内側、外側両係合溝と
玉との数はそれぞれ７個以上であり、上記複数の外側係
合溝の外接円の直径は、上記複列の内輪軌道のうちの上
記ハウジング部側の内輪軌道の直径よりも小さく、これ
ら外側係合溝の一部とハウジング部側の内輪軌道の少な
くとも一部とは直径方向に亙り互いに重畳している。According to the rolling bearing unit for a wheel of the present invention, a first mounting flange for supporting a suspension device on an outer peripheral surface is provided inside the rolling bearing unit, similarly to the above-described conventional rolling bearing unit for a wheel. A double row outer ring raceway on the peripheral surface, a member equivalent to the outer ring that does not rotate even during use, and a second mounting flange for supporting the wheel at a portion near one end of the outer peripheral surface, a double row at the middle portion as well. The inner ring track of
The other end portion is a housing portion serving as an outer ring of a constant velocity joint. An inner ring-equivalent member that rotates at the time of use, and a plurality of rolling members rotatably provided between the outer ring tracks and the inner ring tracks, respectively. A moving body. Further, the constant velocity joint is formed of an inner ring fixed to the end of the drive shaft and a cross-sectional circle formed at equal circumferential positions on the outer peripheral surface of the inner ring in a direction perpendicular to the circumferential direction. A plurality of arcuate inner engaging grooves, and a plurality of outer engaging members formed in a direction perpendicular to the circumferential direction at positions facing the inner engaging grooves on the inner peripheral surface of the housing portion. A retainer formed between the mating groove and the outer peripheral surface of the inner race and the inner peripheral surface of the housing portion and having pockets formed at positions matching the inner and outer engagement grooves, respectively; And a plurality of balls that are allowed to roll freely along the inner and outer engagement grooves while being held. In particular, in the rolling bearing unit for a wheel of the present invention, the number of the inner and outer engagement grooves and the number of balls are each seven or more, and the diameter of the circumcircle of the plurality of outer engagement grooves is: The diameter of the inner raceway on the housing part side of the double row inner raceway is smaller than a diameter of the inner raceway, and a part of these outer engagement grooves and at least a part of the inner raceway on the housing part side overlap with each other in the diameter direction. ing.
【００１２】[0012]
【作用】上述の様に構成する本発明の車輪用転がり軸受
ユニットの場合には、等速ジョイントを構成する内側、
外側両係合溝と玉との数をそれぞれ７個以上としている
ので、車輪用転がり軸受ユニットの使用に伴う、内輪相
当部材と外輪相当部材との間でのトルク伝達時に、上記
各玉に加わる負荷の大きさを前述した従来構造の場合よ
りも小さくできる。従って、その分だけ、上記各玉の外
径を小さくして、環状に配置したこれら各玉の外接円の
直径、並びに上記複数の外側係合溝の外接円の直径を小
さくできる。そして、これら各外接円の直径を、上記複
列の内輪軌道のうちのハウジング部側の内輪軌道の直径
よりも小さくして、上記ハウジング部側の内輪軌道の直
径寸法を徒に大きくする事なく、このハウジング部側の
内輪軌道の少なくとも一部と上記外側係合溝の一部と
を、直径方向に亙り互いに重畳させる事ができる。そし
て、この様に重畳させた分、車輪用転がり軸受ユニット
の軸方向寸法を小さくして、装置全体の小型・軽量化を
図れる。In the case of the wheel rolling bearing unit of the present invention configured as described above, the inside of the constant velocity joint,
Since the number of the outer outer engagement grooves and the number of the balls are set to 7 or more, each of the balls is added to the above-mentioned balls when torque is transmitted between the inner ring-equivalent member and the outer ring-equivalent member due to the use of the wheel rolling bearing unit. The magnitude of the load can be made smaller than in the case of the conventional structure described above. Therefore, the outer diameter of each of the balls can be reduced by that much, and the diameter of the circumscribed circle of each of the balls and the diameter of the circumscribed circle of the plurality of outer engagement grooves can be reduced. And the diameter of each of these circumscribed circles is made smaller than the diameter of the inner raceway on the housing part side of the double row inner raceways, without increasing the diameter dimension of the inner raceway on the housing part side. At least a part of the inner raceway on the housing portion side and a part of the outer engagement groove can be overlapped with each other in the diametrical direction. The axial dimension of the rolling bearing unit for a wheel is reduced by the amount of the overlap, and the entire device can be reduced in size and weight.
【００１３】[0013]
【発明の実施の形態】図１は、本発明の実施の形態の第
１例を示している。尚、本例の特徴は、車輪用転がり軸
受の小型・軽量化を図るべく、この車輪用転がり軸受に
一体に組み込む等速ジョイント２２ａ部分の構造を工夫
した点にある。その他の部分の構造及び作用は、前述の
図４に示した従来構造とほぼ同様であるから、同等部分
には同一符号を付して重複する説明を省略若しくは簡略
にし、以下、本発明の特徴部分並びに上記従来構造と異
なる部分を中心に説明する。FIG. 1 shows a first embodiment of the present invention. The feature of the present embodiment lies in that the structure of the constant velocity joint 22a integrated with the wheel rolling bearing is devised in order to reduce the size and weight of the wheel rolling bearing. The structure and operation of the other parts are almost the same as those of the conventional structure shown in FIG. 4 described above. The following description focuses on parts and parts different from the above-described conventional structure.
【００１４】第一の内輪部材３ａと共にハブ５ａ（内輪
相当部材）を構成する、第二の内輪部材４ａは、軸方向
一端部（図１の左端部）に小径の雄ねじ部２８を、同じ
く中間部に雄セレーション部２９を、それぞれ形成して
いる。そして、この雄セレーション部２９に上記第一の
内輪部材３ａを外嵌すると共に、この第一の内輪部材３
ａの内周面と上記第二の内輪部材４ａの中間部外周面と
をセレーション係合させている。尚、上記雄ねじ部２８
の外径は、上記雄セレーション部２９の外径よりも小さ
くしている。そして、この様な雄ねじ部２８にナット３
０を螺合し、更に緊締する事により、上記第一、第二の
内輪部材３ａ、４ａ同士を結合すると共に、外輪１（外
輪相当部材）の内周面に設けた複列の外輪軌道２７、２
７と上記第一、第二の内輪部材３ａ、４ａの外周面に設
けた第一、第二の内輪軌道７、１０との間にそれぞれ複
数個ずつ転動自在に設けた、各転動体１１、１１に、適
切な予圧を付与している。A second inner ring member 4a, which forms a hub 5a (an inner ring equivalent member) together with the first inner ring member 3a, has a small-diameter male screw portion 28 at one end in the axial direction (left end in FIG. 1) and an intermediate portion. A male serration portion 29 is formed in each portion. Then, the first inner ring member 3a is externally fitted to the male serration portion 29, and the first inner ring member 3
and the inner peripheral surface of the second inner race member 4a is in serration engagement with the inner peripheral surface of the second inner race member 4a. The male screw 28
Is smaller than the outer diameter of the male serration portion 29. Then, nut 3 is attached to such male screw portion 28.
The first and second inner ring members 3a and 4a are connected to each other by screwing and further tightening the outer ring track 27 in a double row provided on the inner peripheral surface of the outer ring 1 (an outer ring equivalent member). , 2
Each rolling element 11 is provided between the first and second inner ring members 3a, 4a, and a plurality of rolling elements 11 respectively provided between the first and second inner ring raceways 7, 10 provided on the outer peripheral surfaces of the first and second inner ring members 3a, 4a. , 11 are given an appropriate preload.
【００１５】尚、上記第一の内輪部材３ａの軸方向他端
面（図１の右端面）と、上記第二の内輪部材４ａの中間
部外周面に設けた段部３１とは、上述の様なナット３０
による予圧付与後に於いても、完全には当接しない（少
なくとも微小な隙間が存在するか、又は極く低い当接圧
で接触するのみである）。又、上記第二の内輪部材４ａ
の他端部（図１の右端部）を構成する等速ジョイント２
２ａのハウジング部９ａの外周面には、このハウジング
部２２ａの端部開口を塞ぐ筒状のブーツ（図示せず）の
一端部を係止する為の係止溝３２を、全周に亙り形成し
ている。The other end surface in the axial direction of the first inner ring member 3a (the right end surface in FIG. 1) and the step 31 provided on the outer peripheral surface of the intermediate portion of the second inner ring member 4a are as described above. Nut 30
Even after the application of the preload by (1), there is no complete contact (at least there is a small gap or the contact is made only with a very low contact pressure). The second inner ring member 4a
Constant velocity joint 2 forming the other end (right end in FIG. 1)
A locking groove 32 for locking one end of a cylindrical boot (not shown) for closing an end opening of the housing portion 22a is formed on the outer peripheral surface of the housing portion 9a of the 2a over the entire circumference. doing.
【００１６】又、上記等速ジョイント２２ａは、内輪１
７の外周面に形成する内側係合溝２４及び上記ハウジン
グ部９ａの内周面に形成する外側係合溝２５と、これら
内側、外側両係合溝２４、２５同士の間部分に設ける玉
１８との数を、それぞれ７個以上（例えば、それぞれ９
〜１２個）とする事により、車輪用転がり軸受ユニット
の使用時に、上記各玉１８に加わる負荷の大きさを、前
述した従来構造の場合よりも小さくしている。そして、
この様に各玉１８に加わる負荷の大きさを小さくした分
だけ、上記各玉１８の外径を小さくして、環状に配置さ
れたこれら複数の玉１８の外接円の直径並びに上記各外
側係合溝２５の外接円の直径を、上記第二の内輪軌道１
０の直径よりも小さくしている。そして、この第二の内
輪軌道１０と上記外側係合溝２５の一部（図１の左部）
とを、直径方向に亙り互いに重畳させている。The constant velocity joint 22a is connected to the inner race 1
7 and an outer engaging groove 25 formed in the inner peripheral surface of the housing portion 9a, and a ball 18 provided in a portion between the inner and outer engaging grooves 24, 25. Is 7 or more (for example, 9
-12), the magnitude of the load applied to each of the balls 18 during use of the wheel rolling bearing unit is made smaller than in the case of the conventional structure described above. And
In this way, the outer diameter of each of the balls 18 is reduced by an amount corresponding to the reduction in the load applied to each of the balls 18, and the diameter of the circumscribed circle of each of the plurality of balls 18 arranged in an annular shape and each of the outer engagement members is reduced. The diameter of the circumscribed circle of the groove 25 is determined by the second inner raceway 1
0 is smaller than the diameter. The second inner raceway 10 and a part of the outer engagement groove 25 (left part in FIG. 1).
Are overlapped with each other over the diameter direction.
【００１７】上述の様に構成する本例の車輪用転がり軸
受ユニットにより、車輪を懸架装置に対して回転自在に
支持する作用自体は、前述した従来車輪用転がり軸受ユ
ニットの場合と同様である。特に、本例の場合には、上
記各外側係合溝２５の外接円の直径を上記第二の内輪軌
道１０の直径よりも小さくする事により、この第二の内
輪軌道１０と上記外側係合溝２５の一部とを、直径方向
に亙り互いに重畳させている。従って、この様に重畳さ
せた分、車輪用転がり軸受ユニットの軸方向寸法を小さ
くして、装置全体の小型・軽量化を図れる。The operation itself of rotatably supporting the wheel with respect to the suspension device by the wheel rolling bearing unit of the present embodiment configured as described above is the same as that of the above-described conventional wheel rolling bearing unit. In particular, in the case of this example, the diameter of the circumscribed circle of each of the outer engagement grooves 25 is made smaller than the diameter of the second inner raceway 10, so that the second inner raceway 10 and the outer engagement raceway 25 can be engaged. A part of the groove 25 is overlapped with each other in the diameter direction. Therefore, the axial dimension of the wheel rolling bearing unit can be reduced by the amount of the overlap, and the size and weight of the entire apparatus can be reduced.
【００１８】次に、図２は、本発明の実施の形態の第２
例を示している。本例の車輪用転がり軸受ユニットを構
成する第一の内輪部材３ｂの内周面には、一端寄り（図
２の左端寄り）部分の大径部３３と、他端寄り（図２の
右端寄り）部分の小径部３４と、これら大径部３３と小
径部３４とを連続させる連続部３５とを設けている。こ
の連続部３５は、上記小径部３４から大径部３３に向か
うに従って漸次内径が大きくなるテーパ面状に形成して
いる。この様な連続部３５には、セレーション溝を形成
し、更に高周波焼き入れ等の焼き入れ硬化処理を施して
いる。更に、上記連続部３５の大径側端部と上記大径部
３３との間には、段部３６を設けている。Next, FIG. 2 shows a second embodiment of the present invention.
An example is shown. On the inner peripheral surface of the first inner ring member 3b constituting the wheel rolling bearing unit of the present example, a large-diameter portion 33 near one end (near the left end in FIG. 2) and a large diameter portion 33 near the other end (near the right end in FIG. 2). ) Portion, and a continuous portion 35 for connecting the large diameter portion 33 and the small diameter portion 34 to each other. The continuous portion 35 is formed in a tapered shape whose inner diameter gradually increases from the small diameter portion 34 to the large diameter portion 33. In such a continuous portion 35, a serration groove is formed, and a hardening treatment such as induction hardening is performed. Further, a step 36 is provided between the large-diameter end of the continuous portion 35 and the large-diameter portion 33.
【００１９】一方、上記第一の内輪部材３ｂと共にハブ
５ｂ（内輪相当部材）を構成する、第二の内輪部材４ｂ
の一端寄り部分には、上記小径部３４の内側にがたつき
なく挿入自在な円筒部８ａを設けている。等速ジョイン
ト２２ａを構成する為のハウジング部９ａ、並びに上記
円筒部８ａの基半部（図２の右半部）で上記小径部３４
の内側に内嵌する部分には、高周波焼き入れ等の焼き入
れ硬化処理を施している。これに対して、上記円筒部８
ａの先半部（図２の左半部）には、この様な焼き入れ硬
化処理を施さず、生のままとしている。この様な円筒部
８ａの外周面は、上記第一、第二の内輪部材３ｂ、４ｂ
を結合する以前の状態では、単一円筒面状（ストレート
形状）としている。On the other hand, a second inner ring member 4b, which forms a hub 5b (an inner ring equivalent member) together with the first inner ring member 3b.
Is provided with a cylindrical portion 8a which can be inserted into the small diameter portion 34 without rattling. The housing 9a for forming the constant velocity joint 22a and the small diameter portion 34 at the base half (the right half in FIG. 2) of the cylindrical portion 8a.
Is hardened by induction hardening or the like. On the other hand, the cylindrical portion 8
The first half (a left half in FIG. 2) of a is not subjected to such quenching and hardening treatment and is left raw. The outer peripheral surface of such a cylindrical portion 8a is connected to the first and second inner ring members 3b and 4b.
Prior to the connection, the shape is a single cylindrical surface (straight shape).
【００２０】上述の様に構成される第一、第二の内輪部
材３ｂ、４ｂ同士を結合固定してハブ５ｂとするには、
先ず、第二の内輪部材４ｂの円筒部８ａに第一の内輪部
材３ｂの小径部３４をがたつきなく外嵌し、この小径部
３４の先端面（図２の右端面）を、上記円筒部８ａの基
端部外周に設けた段部３１に突き当てる。そして、上記
第一の内輪部材３ｂをこの段部３１に突き当てたまま、
上記円筒部８ａの先半部を直径方向外方に向け強くかし
め広げ、更に上記円筒部８ａの先端部を、上記段部３６
に向け更にかしめ広げて、この段部３６を抑え付ける。
上記円筒部８ａの先半部は生のままであるので、直径方
向外方へのかしめ広げ作業に伴い、前記連続部３５に形
成したセレーション溝が、上記円筒部８ａの先半部外周
面に食い込む。この状態で上記第一、第二の内輪部材３
ｂ、４ｂ同士は、上記円筒部８ａの先半部外周面と連続
部３５との間で、円周方向に亙り凹凸係合する。従っ
て、上記第一、第二の内輪部材３ｂ、４ｂ同士の間で、
大きなトルクを伝達自在となる。In order to connect and fix the first and second inner ring members 3b and 4b having the above-described structure to form a hub 5b,
First, the small diameter portion 34 of the first inner ring member 3b is fitted around the cylindrical portion 8a of the second inner ring member 4b without looseness, and the distal end surface (the right end surface in FIG. 2) of the small diameter portion 34 is attached to the cylindrical portion 8a. It abuts against a step 31 provided on the outer periphery of the base end of the portion 8a. Then, while the first inner ring member 3b is in contact with the step portion 31,
The first half of the cylindrical portion 8a is strongly swaged outward in the diametrical direction, and the distal end of the cylindrical portion 8a is
Then, the stepped portion 36 is pressed down.
Since the first half of the cylindrical portion 8a is raw, the serration groove formed in the continuous portion 35 is formed on the outer peripheral surface of the first half of the cylindrical portion 8a in accordance with the diametrically outward expanding operation. Dig into it. In this state, the first and second inner ring members 3
The b and 4b are engaged with each other in the circumferential direction between the outer peripheral surface of the first half of the cylindrical portion 8a and the continuous portion 35. Therefore, between the first and second inner ring members 3b and 4b,
Large torque can be transmitted freely.
【００２１】尚、上記第一の内輪部材３ｂをこの段部３
１に突き当てた状態で各転動体１１、１１に適正な予圧
が付与される様に、上記段部３１等の位置を規制してい
る。又、上記円筒部８ａの先端縁と、上記第一の内輪部
材３ｂの内周面の一部で第二の取付フランジ６の内径側
に位置する部分との間には、溶接３７を施す事により、
上記円筒部８ａの先半部でセレーション溝と係合した部
分の内径が小さくなる事を防止している。尚、上記溶接
３７には、第一、第二の内輪部材３ｂ、４ｂ同士の間で
のトルク伝達の役目を持たせる必要はない。従って、上
記第一の内輪部材３ｂの外周面他端寄り（図２の右端寄
り）部分に形成した第一の内輪軌道７に熱による影響が
生じない様に、小さな肉盛溶接、或は円周方向に亙り間
欠的なスポット溶接を施せば足りる。It should be noted that the first inner ring member 3b is
The position of the step 31 and the like is regulated so that an appropriate preload is applied to each of the rolling elements 11 in a state where the rolling elements 11 abut against each other. A weld 37 is provided between the distal end edge of the cylindrical portion 8a and a portion of the inner peripheral surface of the first inner ring member 3b located on the inner diameter side of the second mounting flange 6. By
The inner diameter of the portion of the first half of the cylindrical portion 8a engaged with the serration groove is prevented from being reduced. It is not necessary for the welding 37 to have a role of transmitting torque between the first and second inner ring members 3b, 4b. Therefore, a small build-up weld or a circle is formed so that the first inner raceway 7 formed near the other end of the outer peripheral surface of the first inner race member 3b (close to the right end in FIG. 2) is not affected by heat. It is sufficient to perform intermittent spot welding in the circumferential direction.
【００２２】上述の様に構成する本発明の車輪用転がり
軸受ユニットの場合には、上記円筒部８ａの先半部外周
面とセレーション溝との係合に基づき、上記第一、第二
の両内輪部材３ｂ、４ｂ同士を、相対回転を確実に防止
した状態で結合できる。又、上記円筒部８ａの先半部で
セレーション溝と係合した部分の内径が小さくなる事
は、上記円筒部８ａの先端縁と第一の内輪部材３ｂの内
周面との間に施した溶接３７により防止する。従って、
長期間に亙る使用によっても、上記第一、第二の両内輪
部材３ｂ、４ｂ同士を、相対回転を確実に防止した状態
で結合したままに保持できて、等速ジョイント２２ａを
介しての前輪の回転駆動を確実に行なえる。少ない部品
点数にも拘らず、第一、第二の内輪部材３ｂ、４ｂ同士
を、大きなトルクを伝達自在として確実に結合すべく、
これら両内輪部材３ｂ、４ｂの結合構造を変えた以外の
構成及び作用は、上述した第１例の場合と同様である。In the case of the rolling bearing unit for a wheel of the present invention configured as described above, the first and second rolling bearing units are formed based on the engagement between the outer peripheral surface of the first half of the cylindrical portion 8a and the serration grooves. The inner ring members 3b and 4b can be connected to each other in a state where relative rotation is reliably prevented. The reduction of the inner diameter of the portion engaged with the serration groove in the first half of the cylindrical portion 8a is performed between the leading edge of the cylindrical portion 8a and the inner peripheral surface of the first inner ring member 3b. It is prevented by welding 37. Therefore,
Even when used for a long period of time, the first and second inner ring members 3b and 4b can be held in a state where they are connected to each other in a state where relative rotation is reliably prevented, and the front wheel via the constant velocity joint 22a can be held. Can be reliably driven. Despite the small number of parts, the first and second inner ring members 3b and 4b are connected to each other with a high torque being transmitted freely.
The configuration and operation other than changing the coupling structure of the inner ring members 3b and 4b are the same as those of the first example described above.
【００２３】次に、図３は、本発明の実施の形態の第３
例を示している。本例の場合、等速ジョイント２２ｂの
外輪となるハウジング部９ｂは、第一の内輪部材３ｃの
他端部（図３の右端部）に一体に設けている。又、上記
第一の内輪部材３ｃは、軸方向中間部で第一の内輪軌道
７から外れた位置に小径段部３８を、同じく他端寄り部
分に上記小径段部３８よりも小径の雄ねじ部３９を、そ
れぞれ形成している。そして、このうちの小径段部３８
に、上記第一の内輪部材３ｃと共にハブ５ｃ（内輪相当
部材）を構成する、第二の内輪部材４０を外嵌してい
る。第二の内輪軌道１０は、この第二の内輪部材４０の
外周面に形成している。又、この第二の内輪部材４０の
軸方向寸法は、上記小径段部３８の軸方向寸法よりも大
きい。従って、上記第二の内輪部材４０を上記小径段部
３８に外嵌した状態でこの第二の内輪部材４０の他端部
（図３の右端部）は、上記小径段部３８の上記雄ねじ部
３９側の端縁（図３の右端縁）から突出する。FIG. 3 shows a third embodiment of the present invention.
An example is shown. In the case of this example, the housing portion 9b serving as the outer ring of the constant velocity joint 22b is provided integrally with the other end (the right end in FIG. 3) of the first inner ring member 3c. The first inner race member 3c has a small-diameter stepped portion 38 at a position deviated from the first inner raceway 7 at an intermediate portion in the axial direction, and a male screw portion having a smaller diameter than the small-diameter stepped portion 38 at a portion near the other end. 39 are formed respectively. And the small diameter step portion 38 of these
In addition, a second inner ring member 40 that constitutes a hub 5c (an inner ring equivalent member) together with the first inner ring member 3c is externally fitted. The second inner raceway 10 is formed on the outer peripheral surface of the second inner race member 40. The axial dimension of the second inner ring member 40 is larger than the axial dimension of the small-diameter stepped portion 38. Therefore, in a state where the second inner ring member 40 is externally fitted to the small-diameter step portion 38, the other end (the right end in FIG. 3) of the second inner ring member 40 is connected to the male screw portion of the small-diameter step portion 38. It protrudes from the edge on the 39 side (the right edge in FIG. 3).
【００２４】そして、上述の様に第二の内輪部材４０を
上記小径段部３８に外嵌した状態で、上記雄ねじ部３９
にナット４１を螺合し、更に緊締する事により、上記第
一、第二の内輪部材３ｃ、４０同士を結合すると共に、
外輪１（外輪相当部材）の内周面に設けた複列の外輪軌
道２７、２７と上記第一、第二の内輪部材３ｃ、４０の
外周面に設けた第一、第二の内輪軌道７、１０との間に
それぞれ複数個ずつ転動自在に設けた、各転動体１１、
１１に、適切な予圧を付与している。尚、上記第二の内
輪部材４０の軸方向一端面（図３の左端面）と、上記小
径段部３８の一端部（図３の左端部）に形成された段差
面とは、上述の様なナット４１による予圧付与後に於い
ても、完全には当接しない（少なくとも微小な隙間が存
在するか、又は極く低い当接圧で接触するのみであ
る）。Then, as described above, with the second inner ring member 40 fitted to the small-diameter step 38, the male screw 39
The first and second inner ring members 3c and 40 are connected to each other by screwing a nut 41
Double-row outer raceways 27, 27 provided on the inner peripheral surface of the outer race 1 (member corresponding to the outer race) and first and second inner raceways 7 provided on the outer peripheral surfaces of the first and second inner race members 3c, 40. , Each of which is provided with a plurality of rolling elements between the rolling elements 11,
11, an appropriate preload is applied. Note that the one end surface in the axial direction (the left end surface in FIG. 3) of the second inner ring member 40 and the step surface formed in the one end portion (the left end portion in FIG. 3) of the small diameter step portion 38 are as described above. Even after the preload is applied by the nut 41, it does not completely contact (there is at least a minute gap or only a very low contact pressure).
【００２５】上述の様に構成する本例の車輪用転がり軸
受ユニットの場合、等速ジョイント２２ｂを構成するハ
ウジング部９ｂと車輪を支持する為の第二の取付フラン
ジ６とを、上記第一の内輪部材３ｃに一体に設けてい
る。この為、上記第二の取付フランジ６に取り付けた車
輪を、図示しない駆動軸から上記ハウジング部９ｂに伝
達された回転駆動力により直接回転させる事ができる。
従って、長期間に亙る使用によっても、上記ハブ５ｃの
耐久性が損なわれる事を防止して、大きなトルクを伝達
自在にできる。又、上記ナット４１による上記各転動体
１１、１１への予圧付与は、上記回転駆動力の伝達部分
と独立した部分で行なっている。この為、伝達すべき回
転駆動力の大きさに拘らず、適正な予圧付与を行なえ
る。ハブ５ｃの構造を変えた以外の構成及び作用は、前
述した第１例の場合と同様である。In the case of the rolling bearing unit for a wheel of the present embodiment configured as described above, the housing 9b forming the constant velocity joint 22b and the second mounting flange 6 for supporting the wheel are connected to the first flange. It is provided integrally with the inner ring member 3c. Therefore, the wheels mounted on the second mounting flange 6 can be directly rotated by the rotational driving force transmitted from the drive shaft (not shown) to the housing portion 9b.
Therefore, even if the hub 5c is used for a long period of time, the durability of the hub 5c is prevented from being impaired, and a large torque can be transmitted freely. The application of preload to the rolling elements 11 by the nut 41 is performed in a portion independent of the portion for transmitting the rotational driving force. Therefore, an appropriate preload can be applied regardless of the magnitude of the rotational driving force to be transmitted. The configuration and operation other than changing the structure of the hub 5c are the same as those of the first example described above.
【００２６】[0026]
【発明の効果】本発明は、以上に述べた通り構成され作
用するので、車輪用転がり軸受ユニットの小型・軽量化
を図って、この車輪用転がり軸受ユニットを組み込んだ
自動車の性能向上を図れる。Since the present invention is constructed and operates as described above, it is possible to reduce the size and weight of the wheel rolling bearing unit and to improve the performance of a vehicle incorporating the wheel rolling bearing unit.
【図１】本発明の実施の形態の第１例を示す部分断面
図。FIG. 1 is a partial cross-sectional view showing a first example of an embodiment of the present invention.
【図２】同第２例を示す部分断面図。FIG. 2 is a partial sectional view showing the second example.
【図３】同第３例を示す部分断面図。FIG. 3 is a partial sectional view showing the third example.
【図４】従来構造の１例を示す部分断面図。FIG. 4 is a partial cross-sectional view showing one example of a conventional structure.
１ 外輪 ２ 第一の取付フランジ ３、３ａ、３ｂ、３ｃ 第一の内輪部材 ４、４ａ、４ｂ 第二の内輪部材 ５、５ａ、５ｂ、５ｃ ハブ ６ 第二の取付フランジ ７ 第一の内輪軌道 ８、８ａ 円筒部 ９、９ａ、９ｂ ハウジング部 １０ 第二の内輪軌道 １１ 転動体 １２ 係止溝 １３ 係止溝 １４ 止め輪 １５ 段部 １６ 溶接 １７ 内輪 １８ 玉 １９ａ、１９ｂ カバー ２０ａ、２０ｂ シールリング ２１ 隔板部 ２２、２２ａ、２２ｂ 等速ジョイント ２３ 保持器 ２４ 内側係合溝 ２５ 外側係合溝 ２６ ポケット ２７ 外輪軌道 ２８ 雄ねじ部 ２９ 雄セレーション部 ３０ ナット ３１ 段部 ３２ 係止溝 ３３ 大径部 ３４ 小径部 ３５ 連続部 ３６ 段部 ３７ 溶接 ３８ 小径段部 ３９ 雄ねじ部 ４０ 第二の内輪部材 ４１ ナット Reference Signs List 1 outer ring 2 first mounting flange 3, 3a, 3b, 3c first inner ring member 4, 4a, 4b second inner ring member 5, 5a, 5b, 5c hub 6 second mounting flange 7 first inner ring track 8, 8a Cylindrical part 9, 9a, 9b Housing part 10 Second inner raceway 11 Rolling element 12 Locking groove 13 Locking groove 14 Retaining ring 15 Step 16 Welding 17 Inner ring 18 Ball 19a, 19b Cover 20a, 20b Seal ring DESCRIPTION OF SYMBOLS 21 Separating plate part 22, 22a, 22b Constant velocity joint 23 Cage 24 Inner engaging groove 25 Outer engaging groove 26 Pocket 27 Outer ring raceway 28 Male screw part 29 Male serration part 30 Nut 31 Step part 32 Lock groove 33 Large diameter part 34 Small-diameter portion 35 Continuous portion 36 Step portion 37 Welding 38 Small-diameter step portion 39 Male thread portion 40 Second inner ring member 41 Nut
Claims (1)
取付フランジを、内周面に複列の外輪軌道を、それぞれ
有し、使用時にも回転しない外輪相当部材と、外周面の
一端寄り部分に車輪を支持する為の第二の取付フランジ
を、同じく中間部に複列の内輪軌道を、それぞれ設け、
他端部を等速ジョイントの外輪となるハウジング部とし
た、使用時に回転する内輪相当部材と、上記各外輪軌道
と上記各内輪軌道との間にそれぞれ複数個ずつ転動自在
に設けられた転動体とを備え、上記等速ジョイントは、
駆動軸の端部に固定される内輪と、この内輪の外周面の
円周方向等間隔位置に、それぞれ円周方向に対し直角方
向に形成された断面円弧形の複数の内側係合溝と、上記
ハウジング部の内周面で上記内側係合溝と対向する位置
に、円周方向に対し直角方向に形成された断面円弧形の
複数の外側係合溝と、上記内輪の外周面とハウジング部
の内周面との間に挟持され、上記内側、外側両係合溝に
整合する位置にそれぞれポケットを形成した保持器と、
これら各ポケットの内側に保持された状態で、上記内
側、外側両係合溝に沿う転動を自在とされた、複数個の
玉とから成る車輪用転がり軸受ユニットに於いて、上記
内側、外側両係合溝と玉との数はそれぞれ７個以上であ
り、上記複数の外側係合溝の外接円の直径は、上記複列
の内輪軌道のうちの上記ハウジング部側の内輪軌道の直
径よりも小さく、これら外側係合溝の一部とハウジング
部側の内輪軌道の少なくとも一部とは直径方向に亙り互
いに重畳している事を特徴とする車輪支持用転がり軸受
ユニット。An outer ring-equivalent member which has a first mounting flange for supporting the suspension on the outer peripheral surface, a double row outer ring raceway on the inner peripheral surface, and which does not rotate even during use, A second mounting flange for supporting the wheel at a portion closer to one end, and a double row inner ring track also provided at the middle portion, respectively,
The other end portion is a housing portion serving as an outer ring of a constant velocity joint. An inner ring-equivalent member that rotates at the time of use, and a plurality of rolling members rotatably provided between the outer ring tracks and the inner ring tracks, respectively. And a moving body, wherein the constant velocity joint is
An inner ring fixed to the end of the drive shaft, and a plurality of inner engaging grooves having an arc-shaped cross-section formed at equal circumferential positions on the outer peripheral surface of the inner ring, respectively, in a direction perpendicular to the circumferential direction. A plurality of outer engaging grooves having an arc-shaped cross section formed in a direction perpendicular to the circumferential direction at positions on the inner peripheral surface of the housing portion facing the inner engaging grooves, and an outer peripheral surface of the inner ring. A retainer sandwiched between the inner peripheral surface of the housing portion and pockets formed at positions matching the inner and outer engagement grooves,
In the wheel rolling bearing unit made up of a plurality of balls, which can freely roll along the inner and outer engagement grooves while being held inside these pockets, The number of both engagement grooves and balls is 7 or more, and the diameter of the circumscribed circle of the plurality of outer engagement grooves is larger than the diameter of the inner raceway on the housing portion side of the double row inner raceways. A part of the outer engagement groove and at least a part of the inner raceway on the housing portion side overlap each other in a diametrical direction.
Priority Applications (6)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP9191433A JPH1137146A (en) | 1997-07-16 | 1997-07-16 | Rolling bearing unit for wheels |
| EP03007209A EP1326027B1 (en) | 1997-07-16 | 1998-07-15 | Constant velocity joint for wheels |
| EP98305640A EP0892187B1 (en) | 1997-07-16 | 1998-07-15 | Constant velocity ratio joint |
| DE69833340T DE69833340T2 (en) | 1997-07-16 | 1998-07-15 | Rolling bearing unit and constant velocity joint for wheels |
| DE69828467T DE69828467T2 (en) | 1997-07-16 | 1998-07-15 | Constant velocity joint for wheels |
| US09/116,527 US6368223B1 (en) | 1997-07-16 | 1998-07-16 | Rolling bearing unit and constant velocity joint for wheels |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP9191433A JPH1137146A (en) | 1997-07-16 | 1997-07-16 | Rolling bearing unit for wheels |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH1137146A true JPH1137146A (en) | 1999-02-09 |
Family
ID=16274543
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP9191433A Pending JPH1137146A (en) | 1997-07-16 | 1997-07-16 | Rolling bearing unit for wheels |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH1137146A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002205504A (en) * | 2001-01-12 | 2002-07-23 | Toyoda Mach Works Ltd | Driving wheel supporting device |
| US7232374B2 (en) | 2000-09-20 | 2007-06-19 | Ntn Corporation | Wheel bearing device |
-
1997
- 1997-07-16 JP JP9191433A patent/JPH1137146A/en active Pending
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7232374B2 (en) | 2000-09-20 | 2007-06-19 | Ntn Corporation | Wheel bearing device |
| US7465233B2 (en) | 2000-09-20 | 2008-12-16 | Ntn Corporation | Wheel bearing device |
| US8007366B2 (en) | 2000-09-20 | 2011-08-30 | Ntn Corporation | Wheel bearing device |
| JP2002205504A (en) * | 2001-01-12 | 2002-07-23 | Toyoda Mach Works Ltd | Driving wheel supporting device |
| JP4696362B2 (en) * | 2001-01-12 | 2011-06-08 | 株式会社ジェイテクト | Drive wheel support device |
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