JP2006153097A - Bearing unit for wheel - Google Patents

Bearing unit for wheel Download PDF

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Publication number
JP2006153097A
JP2006153097A JP2004342812A JP2004342812A JP2006153097A JP 2006153097 A JP2006153097 A JP 2006153097A JP 2004342812 A JP2004342812 A JP 2004342812A JP 2004342812 A JP2004342812 A JP 2004342812A JP 2006153097 A JP2006153097 A JP 2006153097A
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Japan
Prior art keywords
wheel
bearing
knuckle
outer ring
annular groove
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Pending
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JP2004342812A
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Japanese (ja)
Inventor
Shogo Suzuki
昭吾 鈴木
Tateo Adachi
健郎 安達
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NTN Corp
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NTN Corp
NTN Toyo Bearing Co Ltd
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Priority to JP2004342812A priority Critical patent/JP2006153097A/en
Publication of JP2006153097A publication Critical patent/JP2006153097A/en
Pending legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/067—Fixing them in a 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
    • F16C19/02—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
    • F16C19/22—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

Abstract

<P>PROBLEM TO BE SOLVED: To provide a bearing unit for a wheel which is mounted on a light alloy knuckle being lightweight and can prevent reduction of preload caused by temperature rise and bearing creep. <P>SOLUTION: The bearing unit for a wheel fitted between the knuckle made of light alloy and a small-diameter stepped section of a hub wheel provides an outer ring 20 forming a double row outer raceway surface 12a at its inner periphery. A circular groove 21 is formed on an outer periphery of the outer ring 20, a resin band 22 made of heat-resistant synthetic resin is filled up into the circular groove 21 by injection molding, and a groove width L1 of the circular groove 21 is set up to be larger than a formed zone L2 of the outer raceway surface 12a (L1≥L2). Thus, even though the knuckle thermally expands more than the bearing unit for a wheel due to difference in a coefficient of linear expansion at the time of temperature rise, reduction of an interference fit is restrained, and missing of the preload and generation of the bearing creep are prevented, and a distortion for a curvature of the outer raceway surface 12a is prevented so that at least the formed zone L2 of the outer raceway surface 12a is restrained from expanding. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

本発明は、自動車等の車輪を、懸架装置を構成するナックルに対して回転自在に支承する車輪用軸受装置、詳しくは、軽合金製のナックルに取り付けられる車輪用軸受の改良に関するものである。   The present invention relates to a wheel bearing device for rotatably supporting a wheel of an automobile or the like with respect to a knuckle constituting a suspension device, and more particularly to an improvement of a wheel bearing attached to a light alloy knuckle.

従来の車輪用軸受装置５０は、図８に示すように、ブレーキロータ５７と共に車輪（図示せず）を固定するハブ輪５１と、そのハブ輪５１を回転自在に支持し、外輪５２および一対の内輪５３を有する車輪用軸受５４と、この車輪用軸受５４を車体（懸架装置）に支持するナックル５５と、ハブ輪５１と連結してドライブシャフト（図示せず）の動力をこのハブ輪５１に伝達する等速自在継手５６を主要部として構成している。   As shown in FIG. 8, the conventional wheel bearing device 50 includes a hub wheel 51 that fixes a wheel (not shown) together with the brake rotor 57, and rotatably supports the hub wheel 51. A wheel bearing 54 having an inner ring 53, a knuckle 55 that supports the wheel bearing 54 on a vehicle body (suspension device), and a hub wheel 51 connected to drive power of a drive shaft (not shown) to the hub wheel 51. A constant velocity universal joint 56 for transmission is configured as a main part.

従来からこの車輪用軸受装置５０を構成する部品、特にナックル５５には、線膨張係数がハブ輪５１等と同種の可鍛鋳鉄等の鉄系金属が採用されてきたが、近年、装置の軽量化を狙ってアルミ合金やマグネシウム合金等の軽合金製のものを採用する傾向がある。しかしながら、ナックル５５をこうした軽合金で形成した場合、ナックル５５と外輪５２の線膨張係数の違いにより、例えば、走行時の温度上昇によってナックル５５と外輪５２との嵌合シメシロが少なくなったり、あるいは解放される恐れがあった。その結果、組立時の軸受予圧が維持できなくなる、所謂予圧抜けといった不具合が発生した。   Conventionally, ferrous metals such as malleable cast iron having the same linear expansion coefficient as that of the hub wheel 51 and the like have been employed for the components constituting the wheel bearing device 50, in particular, the knuckle 55. There is a tendency to adopt a light alloy such as an aluminum alloy or a magnesium alloy for the purpose of making it easier. However, when the knuckle 55 is formed of such a light alloy, due to the difference in the linear expansion coefficient between the knuckle 55 and the outer ring 52, for example, the fitting squeezing between the knuckle 55 and the outer ring 52 decreases due to the temperature rise during traveling, or There was a fear of being released. As a result, a problem such as so-called preload loss occurred in which the bearing preload during assembly cannot be maintained.

さらに、外輪５２がクリープを起こし、焼付いたり、短寿命を誘発する恐れがあった。ここで、クリープとは、嵌合シメシロ不足や嵌合面の加工精度不良等により軸受が周方向に微動して嵌合面が鏡面化し、場合によってはかじりを伴い焼付きや溶着する現象をいう。   Further, the outer ring 52 may creep and may seize or induce a short life. Here, creep refers to a phenomenon in which the bearing surface slightly moves in the circumferential direction due to a lack of mating squealing or poor mating surface processing accuracy, and the mating surface becomes a mirror surface, and in some cases, seizure or welding occurs with galling. .

こうした問題を回避するために従来の車輪用軸受装置５０において、温度上昇時の軸受予圧を確保するために初期の予圧量を高く設定すると共に、クリープを防止するために、温度上昇時のシメシロ低下量を見込んで初期のシメシロを大きく設定していた。なお、係る先行技術は文献公知発明に係るものでないため、記載すべき先行技術文献情報はない。   In order to avoid such a problem, in the conventional wheel bearing device 50, the initial preload amount is set high in order to ensure the bearing preload at the time of temperature rise, and in order to prevent creep, the squeezing drop at the time of temperature rise is reduced. In anticipation of the amount, the initial shimeshiro was set large. Note that there is no prior art document information to be described because the prior art is not related to a known literature invention.

しかしながら、予圧抜けを防止するために車輪用軸受５４の初期予圧量を高く設定すると、当然のことながら車輪用軸受５４に余分な荷重を常時負荷することになって軸受寿命が短くなる。また、温度変化によって予圧量が大きく変化するに伴い軸受剛性が変動し、車両の走行安定性に悪影響を及ぼす。さらには、クリープを防止するために初期のシメシロを大きく設定すると、車輪用軸受５４を圧入する時にナックル５５をかじる恐れがあるため、ナックル５５を予め加熱した状態で車輪用軸受５４を圧入する必要がある。これでは組立工数がアップしてコスト高騰を招来することになる。   However, if the initial preload amount of the wheel bearing 54 is set high in order to prevent the preload from being lost, as a matter of course, an extra load is always applied to the wheel bearing 54 and the bearing life is shortened. Further, the bearing rigidity varies as the preload amount greatly changes due to temperature change, which adversely affects the running stability of the vehicle. Furthermore, if the initial squeeze is set large in order to prevent creep, the knuckle 55 may be squeezed when the wheel bearing 54 is press-fitted. Therefore, it is necessary to press-fit the wheel bearing 54 with the knuckle 55 heated in advance. There is. This increases the number of assembly steps and causes a cost increase.

本発明は、このような事情に鑑みてなされたもので、軽量化を図った軽合金製ナックルに装着され、温度上昇による予圧低下と軸受クリープを防止した車輪用軸受装置を提供することを目的としている。   The present invention has been made in view of such circumstances, and an object of the present invention is to provide a wheel bearing device that is attached to a light alloy knuckle that is reduced in weight and prevents preload reduction and bearing creep due to temperature rise. It is said.

係る目的を達成すべく、本発明のうち請求項１に記載の発明は、一端部に車輪取付フランジを一体に有し、この車輪取付フランジから軸方向に延びる小径段部が形成されたハブ輪と、懸架装置を構成し、軽合金からなるナックルと前記ハブ輪の小径段部との間に嵌合された車輪用軸受とからなり、この車輪用軸受が、内周に複列の外側転走面が形成された外輪と、この外輪に内挿され、外周に前記複列の外側転走面に対向する内側転走面がそれぞれ形成された一対の内輪と、前記両転走面間に転動自在に収容された複列の転動体とを備え、前記ナックルに対して前記ハブ輪が回転自在に支承された車輪用軸受装置において、前記外輪の外周に環状溝が形成され、この環状溝に耐熱性の合成樹脂からなる樹脂バンドが射出成形によって充填されると共に、当該環状溝が、前記転動体の投影幅略中央に位置するように設定されている。   In order to achieve such an object, the invention according to claim 1 of the present invention is a hub wheel in which a wheel mounting flange is integrally formed at one end portion and a small-diameter step portion extending in the axial direction is formed from the wheel mounting flange. And a wheel bearing comprising a knuckle made of a light alloy and a small-diameter step portion of the hub wheel. The wheel bearing has a double-row outward rotation on the inner periphery. An outer ring formed with a running surface, a pair of inner rings inserted into the outer ring and formed with inner rolling surfaces opposed to the outer rolling surfaces of the double row on the outer periphery, and between the two rolling surfaces A wheel bearing device in which the hub wheel is rotatably supported with respect to the knuckle, and an annular groove is formed on an outer periphery of the outer ring. A resin band made of heat-resistant synthetic resin is filled in the groove by injection molding. Together, the annular groove is set so as to be positioned to the projection width substantially the center of the rolling element.

このように、軽合金からなるナックルとハブ輪の小径段部との間に嵌合された車輪用軸受が、内周に複列の外側転走面が形成された外輪と、この外輪に内挿され、外周に前記複列の外側転走面に対向する内側転走面がそれぞれ形成された一対の内輪と、前記両転走面間に転動自在に収容された複列の転動体とを備え、ナックルに対してハブ輪が回転自在に支承された車輪用軸受装置において、前記外輪の外周に環状溝が形成され、この環状溝に耐熱性の合成樹脂からなる樹脂バンドが射出成形によって充填されると共に、当該環状溝が、転動体の投影幅略中央に位置するように設定されているので、温度上昇時、ナックルと車輪用軸受との線膨張係数の違いによりナックルが車輪用軸受以上に熱膨張したとしても、嵌合シメシロの低下を抑制し、軸受クリープの発生を防止することができると共に、初期に設定した軸受予圧が低下するのを防止することができ、軸受剛性の変動を抑えて車両の走行安定性を確実に保つことができる。   As described above, the wheel bearing fitted between the knuckle made of light alloy and the small-diameter step portion of the hub wheel has an outer ring in which a double row outer raceway surface is formed on the inner periphery, and an inner ring in the outer ring. A pair of inner rings formed on the outer periphery, each of which has an inner rolling surface facing the outer rolling surface of the double row, and a double row of rolling elements housed so as to roll between the rolling surfaces. An annular groove is formed in the outer periphery of the outer ring, and a resin band made of a heat-resistant synthetic resin is formed by injection molding in the annular groove. In addition to being filled, the annular groove is set so as to be positioned approximately in the center of the projected width of the rolling element, so that when the temperature rises, the knuckle may become a wheel bearing due to the difference in linear expansion coefficient between the knuckle and the wheel bearing. Even if it expands more than this, it suppresses the decrease in mating , It is possible to prevent the occurrence of bearing creep, can bearing preload initially set to prevent the decrease can be kept reliably running stability of the vehicle by suppressing the fluctuation of the bearing rigidity.

好ましくは、請求項２に記載の発明のように、前記環状溝が、少なくとも前記外側転走面の幅方向全域に形成されていれば、温度上昇時、環状溝に充填された樹脂バンドにより、少なくともこの外側転走面の形成域が膨張するのを抑制し、外側転走面の母線形状が崩れるのを防止することができる。したがって、初期に設定した予圧量が変化するのを防止して軸受剛性の変動を抑え、所望の耐久性を確保することができる。   Preferably, as in the invention according to claim 2, if the annular groove is formed at least in the entire width direction of the outer rolling surface, by the resin band filled in the annular groove when the temperature rises, It is possible to suppress at least the formation region of the outer rolling surface from expanding and prevent the bus bar shape of the outer rolling surface from collapsing. Therefore, it is possible to prevent a change in the preload amount set in the initial stage, suppress a variation in bearing rigidity, and secure desired durability.

また、請求項３に記載の発明のように、前記外輪の外周に単一の環状溝が形成され、この環状溝が、前記複列の外側転走面を跨いで前記外輪の外周の幅中央部に形成されていても良い。   Further, as in the invention according to claim 3, a single annular groove is formed on the outer periphery of the outer ring, and the annular groove straddles the outer raceway surface of the double row, and the width center of the outer periphery of the outer ring. It may be formed in the part.

また、請求項４に記載の発明のように、前記樹脂バンドがポリアミド系の合成樹脂からなり、その線膨張係数が８〜１６×１０−５／℃に設定されていれば、ナックルの線膨張係数よりも大きく、ナックルが車輪用軸受以上に熱膨張したとしても、この樹脂バンドがナックルの熱膨張以上に膨張してその変化に追従することができる。 Further, as in the invention described in claim 4, if the resin band is made of a polyamide-based synthetic resin and the linear expansion coefficient is set to 8 to 16 × 10 −5 / ° C., the linear expansion of the knuckle Even if the knuckle is larger than the coefficient and thermally expands more than the wheel bearing, the resin band can expand more than the thermal expansion of the knuckle and follow the change.

また、請求項５に記載の発明は、前記樹脂バンドが、成形後に研削加工により所定の外径寸法に形成されているので、ナックルとのシメシロが安定し、予圧抜けと軸受クリープを一層効果的に防止することができると共に、圧入時、シメシロ過大による樹脂バンドの欠損もない。   In the invention according to claim 5, since the resin band is formed to have a predetermined outer diameter by grinding after molding, the squeezing with the knuckle is stabilized, and preload loss and bearing creep are more effective. In addition, at the time of press-fitting, there is no loss of the resin band due to excessive shishiro.

本発明に係る車輪用軸受装置は、一端部に車輪取付フランジを一体に有し、この車輪取付フランジから軸方向に延びる小径段部が形成されたハブ輪と、懸架装置を構成し、軽合金からなるナックルと前記ハブ輪の小径段部との間に嵌合された車輪用軸受とからなり、この車輪用軸受が、内周に複列の外側転走面が形成された外輪と、この外輪に内挿され、外周に前記複列の外側転走面に対向する内側転走面がそれぞれ形成された一対の内輪と、前記両転走面間に転動自在に収容された複列の転動体とを備え、前記ナックルに対して前記ハブ輪が回転自在に支承された車輪用軸受装置において、前記外輪の外周に環状溝が形成され、この環状溝に耐熱性の合成樹脂からなる樹脂バンドが射出成形によって充填されると共に、当該環状溝が、転動体の投影幅略中央に位置するように設定されているので、温度上昇時、ナックルと車輪用軸受との線膨張係数の違いによりナックルが車輪用軸受以上に熱膨張したとしても、嵌合シメシロの低下を抑制し、軸受クリープの発生を防止することができると共に、初期に設定した軸受予圧が低下するのを防止することができ、軸受剛性の変動を抑えて車両の走行安定性を確実に保つことができる。   A wheel bearing device according to the present invention comprises a hub wheel integrally formed with a wheel mounting flange at one end and a small-diameter step portion extending in the axial direction from the wheel mounting flange, and a suspension device. A wheel bearing fitted between a knuckle comprising the hub wheel and a small-diameter step portion of the hub wheel, and the wheel bearing comprises an outer ring having a double row outer raceway formed on the inner periphery, and A pair of inner rings inserted into the outer ring and formed with inner rolling surfaces facing the outer rolling surfaces of the double row on the outer periphery, and a double row of rolls accommodated between the rolling surfaces. In a wheel bearing device comprising a rolling element, wherein the hub wheel is rotatably supported with respect to the knuckle, an annular groove is formed on an outer periphery of the outer ring, and a resin made of a heat-resistant synthetic resin in the annular groove The band is filled by injection molding and the annular groove is rolling Therefore, even if the knuckle expands more than the wheel bearing due to the difference in the linear expansion coefficient between the knuckle and the wheel bearing when the temperature rises, It is possible to suppress the decrease and prevent the occurrence of bearing creep, and also to prevent the initial bearing preload from decreasing, and to keep the running stability of the vehicle by suppressing the fluctuation of the bearing rigidity. be able to.

一端部に車輪取付フランジを一体に有し、この車輪取付フランジから軸方向に延びる小径段部が形成されたハブ輪と、懸架装置を構成し、軽合金からなるナックルと前記ハブ輪の小径段部との間に嵌合された車輪用軸受とからなり、この車輪用軸受が、内周に複列の外側転走面が形成された外輪と、この外輪に内挿され、外周に前記複列の外側転走面に対向する内側転走面がそれぞれ形成された一対の内輪と、前記両転走面間に転動自在に収容された複列の転動体とを備え、前記ナックルに対して前記ハブ輪が回転自在に支承された車輪用軸受装置において、前記外輪の外周に環状溝が形成され、この環状溝に耐熱性の合成樹脂からなる樹脂バンドが射出成形によって充填されると共に、当該環状溝が、少なくとも前記外側転走面の幅方向全域に形成されている。   A hub wheel having a wheel mounting flange integrally formed at one end and a small-diameter step portion extending in the axial direction from the wheel mounting flange, a suspension device, a knuckle made of a light alloy, and a small-diameter step of the hub wheel A wheel bearing fitted between the outer ring and the wheel bearing. A pair of inner rings each formed with an inner rolling surface facing the outer rolling surface of the row, and a double row rolling element that is slidably accommodated between the both rolling surfaces, with respect to the knuckle In the wheel bearing device in which the hub wheel is rotatably supported, an annular groove is formed on the outer periphery of the outer ring, and a resin band made of a heat-resistant synthetic resin is filled in the annular groove by injection molding. The annular groove is at least the entire width direction of the outer rolling surface. It is formed in.

以下、本発明の実施の形態を図面に基づいて詳細に説明する。
図１は、本発明に係る車輪用軸受装置の第１の実施形態を示す縦断面図、図２は、その車輪用軸受を示す縦断面図、図３は、温度変化と軸受予圧の変化の関係を示すグラフである。なお、以下の説明では、車両に組み付けた状態で、車両の外側寄りとなる側をアウトボード側（図面左側）、中央寄り側をインボード側（図面右側）という。 Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
1 is a longitudinal sectional view showing a first embodiment of a wheel bearing device according to the present invention, FIG. 2 is a longitudinal sectional view showing the wheel bearing, and FIG. 3 is a graph showing changes in temperature and bearing preload. It is a graph which shows a relationship. In the following description, the side closer to the outside of the vehicle in the state assembled to the vehicle is referred to as the outboard side (left side in the drawing), and the side closer to the center is referred to as the inboard side (right side in the drawing).

図１に示す車輪用軸受装置は、ハブ輪１と、このハブ輪１に圧入され、ナックル２に対してハブ輪１を回転自在に支承する車輪用軸受３とを主たる構成としている。ハブ輪１はＳ５３Ｃ等の炭素０．４０〜０．８０ｗｔ％を含む中炭素鋼で形成され、アウトボード側の端部に車輪ＷおよびブレーキロータＢを取り付けるための車輪取付フランジ４と、この車輪取付フランジ４から軸方向に延びる円筒状の小径段部５が形成されている。車輪取付フランジ４には車輪ＷおよびブレーキロータＢを締結するハブボルト４ａが周方向等配に植設されている。また、ハブ輪１の内周面にはトルク伝達用のセレーション（またはスプライン）６が形成されると共に、小径段部５の外周面には後述する車輪用軸受３が圧入されている。   The wheel bearing device shown in FIG. 1 mainly includes a hub wheel 1 and a wheel bearing 3 that is press-fitted into the hub wheel 1 and rotatably supports the hub wheel 1 with respect to the knuckle 2. The hub wheel 1 is formed of medium carbon steel containing carbon of 0.40 to 0.80 wt% such as S53C, and the wheel mounting flange 4 for mounting the wheel W and the brake rotor B to the end on the outboard side, and the wheel A cylindrical small diameter step portion 5 extending in the axial direction from the mounting flange 4 is formed. Hub bolts 4 a that fasten the wheels W and the brake rotor B are planted on the wheel mounting flange 4 at equal intervals in the circumferential direction. Further, a serration (or spline) 6 for torque transmission is formed on the inner peripheral surface of the hub wheel 1, and a wheel bearing 3 described later is press-fitted on the outer peripheral surface of the small diameter step portion 5.

ハブ輪１の小径段部５に圧入された車輪用軸受３は、等速自在継手７を構成する外側継手部材８の肩部９とハブ輪１とで挟持された状態で固定されている。外側継手部材８は、肩部９から軸方向に延びるステム部１０が一体に形成されている。このステム部１０の外周には、ハブ輪１のセレーション６に係合するセレーション（またはスプライン）１０ａとねじ部１０ｂが形成されている。そして、エンジンからのトルクが図示しないドライブシャフトおよび等速自在継手７、およびこのステム部１０のセレーション１０ａを介してハブ輪１に伝達される。   The wheel bearing 3 press-fitted into the small-diameter step portion 5 of the hub wheel 1 is fixed in a state of being sandwiched between the shoulder portion 9 of the outer joint member 8 constituting the constant velocity universal joint 7 and the hub wheel 1. The outer joint member 8 is integrally formed with a stem portion 10 extending in the axial direction from the shoulder portion 9. A serration (or spline) 10 a that engages the serration 6 of the hub wheel 1 and a screw portion 10 b are formed on the outer periphery of the stem portion 10. Torque from the engine is transmitted to the hub wheel 1 via a drive shaft and a constant velocity universal joint 7 (not shown) and a serration 10 a of the stem portion 10.

ここで、ステム部１０のセレーション１０ａには、軸線に対して所定の角度傾斜した捩れ角が設けられ、外側継手部材８の肩部９が車輪用軸受３に当接するまでステム部１０がハブ輪１に圧入嵌合されている。これにより、セレーション６、１０ａの嵌合部に予圧が付与され、周方向のガタが殺されている。また、ステム部１０の端部に形成されたねじ部１０ｂに固定ナット１１が所定の締付トルクで締結されることにより、所望の軸受予圧を得ることができるように設定されている。すなわち、車輪用軸受３が、ハブ輪１に対して軸受クリープを防止し、かつ所望の予圧量になるように、所定のシメシロで圧入されている。一方、ナックル２は、アルミ合金等の軽合金で形成されている。これにより、従来の鋳鉄等に比べ、剛性不足を補うために各部を肉厚に設計したとしてもその重量は半減し、軽量化が達成できる。そして、このナックル２に車輪用軸受３が所定のシメシロで圧入されている。   Here, the serration 10a of the stem portion 10 is provided with a torsion angle inclined at a predetermined angle with respect to the axis, and the stem portion 10 is a hub wheel until the shoulder portion 9 of the outer joint member 8 contacts the wheel bearing 3. 1 is press-fit. Thereby, preload is given to the fitting part of serrations 6 and 10a, and the play of the peripheral direction is killed. Further, the fixing nut 11 is fastened with a predetermined tightening torque to the screw portion 10b formed at the end portion of the stem portion 10, so that a desired bearing preload can be obtained. That is, the wheel bearing 3 is press-fitted with a predetermined squeezing force so as to prevent bearing creep with respect to the hub wheel 1 and to obtain a desired preload amount. On the other hand, the knuckle 2 is formed of a light alloy such as an aluminum alloy. Thereby, compared with conventional cast iron etc., even if each part is designed to be thick in order to make up for lack of rigidity, the weight is reduced by half, and weight reduction can be achieved. A wheel bearing 3 is press-fitted into the knuckle 2 with a predetermined scissors.

車輪用軸受３は、図２に拡大して示すように、外輪１２と、この外輪１２に内挿された一対の内輪１３、１３と、内外輪１３、１２間に収容された複列のボール１４、１４とを備えた複列アンギュラ玉軸受からなる。外輪１２はＳＵＪ２等の高炭素クロム軸受鋼からなり、内周には複列の外側転走面１２ａ、１２ａが一体に形成されている。内輪１３はＳＵＪ２等の高炭素クロム軸受鋼からなり、その外周には複列の外側転走面１２ａ、１２ａに対向する内側転走面１３ａ、１３ａが形成されている。そして、複列のボール１４、１４がこれら転走面１２ａ、１３ａ間にそれぞれ収容され、保持器１５、１５によって転動自在に保持されている。また、車輪用軸受３の端部にはシール１６、１７が装着され、軸受内部に封入された潤滑グリースの漏洩と、外部から雨水やダスト等が軸受内部に侵入するのを防止している。   As shown in an enlarged view in FIG. 2, the wheel bearing 3 includes an outer ring 12, a pair of inner rings 13 and 13 inserted in the outer ring 12, and double-row balls accommodated between the inner and outer rings 13 and 12. 14 and 14 are double row angular contact ball bearings. The outer ring 12 is made of high carbon chrome bearing steel such as SUJ2, and double row outer rolling surfaces 12a and 12a are integrally formed on the inner periphery. The inner ring 13 is made of high carbon chrome bearing steel such as SUJ2, and inner rolling surfaces 13a and 13a facing the double row outer rolling surfaces 12a and 12a are formed on the outer periphery thereof. The double-row balls 14 and 14 are accommodated between the rolling surfaces 12a and 13a, respectively, and are held by the cages 15 and 15 so as to be able to roll. Further, seals 16 and 17 are attached to the end portion of the wheel bearing 3 to prevent leakage of lubricating grease sealed inside the bearing and prevent rainwater and dust from entering the bearing from the outside.

外輪１２の外周には一対の環状溝１８、１８が形成されている。これら環状溝１８、１８は、ボール１４の投影幅略中央の位置、すなわち、複列の外側転走面１２ａ、１２ａの溝底位置にそれぞれ設定されている。これにより、最小肉厚部となる溝底域の膨張を抑制し、予圧抜けと軸受クリープを効果的に防止することができる。また、これらの環状溝１８、１８には、ＰＡ（ポリアミド）１１をベースとした耐熱性の熱可塑性合成樹脂が射出成形により充填され、樹脂バンド１９が形成されている。   A pair of annular grooves 18 and 18 are formed on the outer periphery of the outer ring 12. These annular grooves 18 and 18 are respectively set at positions approximately in the center of the projected width of the ball 14, that is, at the groove bottom positions of the double row outer rolling surfaces 12a and 12a. Thereby, expansion of the groove bottom region which becomes the minimum thickness portion can be suppressed, and preload loss and bearing creep can be effectively prevented. The annular grooves 18 and 18 are filled with a heat-resistant thermoplastic synthetic resin based on PA (polyamide) 11 by injection molding to form a resin band 19.

樹脂バンド１９の材質は前記ＰＡ１１に限らず、アルミ合金等の軽合金からなるナックル２の線膨張係数（２〜２．３×１０−５／℃）よりも大きく、線膨張係数が８〜１６×１０−５／℃の範囲の合成樹脂なら良い。例えばＰＡ６６、さらにこれらの熱可塑性合成樹脂にＧＦ（グラスファイバー）等の強化繊維を１０〜３０ｗｔ％の範囲で含有させたものを例示することができる。 The material of the resin band 19 is not limited to the PA 11 and is larger than the linear expansion coefficient (2 to 2.3 × 10 −5 / ° C.) of the knuckle 2 made of a light alloy such as an aluminum alloy, and the linear expansion coefficient is 8 to 16 A synthetic resin in the range of × 10 −5 / ° C. may be used. For example, PA66 and those obtained by adding reinforcing fibers such as GF (glass fiber) in the range of 10 to 30 wt% to these thermoplastic synthetic resins can be exemplified.

図３は、従来の車輪用軸受と本実施形態に係る車輪用軸受のそれぞれ外輪のみをアルミ合金からなるナックル２に圧入した状態で、温度変化と軸受予圧の変化、すなわち、外輪の外側転走面の寸法変化の関係を比較測定した結果を示している。この図でも明確なように、従来のものでは、温度上昇に比例してリニアに軸受予圧が低下しているが、本実施形態に係る車輪用軸受においては、軸受予圧は８０℃近傍までは漸次低下するも、それ以降は所定の予圧量を維持することが判る。   FIG. 3 shows a change in temperature and a change in bearing preload, that is, outer rolling of the outer ring, in a state where only the outer ring of each of the conventional wheel bearing and the wheel bearing according to the present embodiment is press-fitted into the knuckle 2 made of an aluminum alloy. The result of the comparative measurement of the relationship of the dimensional change of the surface is shown. As is clear from this figure, in the conventional one, the bearing preload decreases linearly in proportion to the temperature rise. However, in the wheel bearing according to this embodiment, the bearing preload gradually increases up to about 80 ° C. Although it decreases, it can be seen that the predetermined preload amount is maintained thereafter.

本実施形態はこのような構成を備えているので、温度上昇時、ナックル２と車輪用軸受３の線膨張係数の違いにより、ナックル２が車輪用軸受３以上に熱膨張したとしても、嵌合シメシロの低下を抑制し、軸受クリープの発生を防止することができると共に、初期に設定した軸受予圧が低下するのを防止することができ、軸受剛性の変動を抑えて車両の走行安定性を確実に保つことができる。   Since this embodiment is provided with such a configuration, even when the knuckle 2 thermally expands beyond the wheel bearing 3 due to the difference in linear expansion coefficient between the knuckle 2 and the wheel bearing 3 when the temperature rises, the fitting is possible. It is possible to prevent the occurrence of bearing creep and prevent the occurrence of bearing creep, as well as to prevent a decrease in the initial bearing preload, and to prevent fluctuations in bearing rigidity, ensuring vehicle running stability. Can be kept in.

なお、外輪１２の環状溝１８に樹脂バンド１９が射出成形された後は、センタレス研削盤等で樹脂バンド１９の外周面が研削加工され、所定の外径寸法に形成される。これにより、ナックル２とのシメシロが安定し、予圧抜けと軸受クリープを一層効果的に防止することができると共に、圧入時、シメシロ過大により樹脂バンド１９が欠損することもない。なお、樹脂バンド１９の成形後、外輪１２の外周面と樹脂バンド１９とを一体に研削加工するようにしても良い。   In addition, after the resin band 19 is injection-molded in the annular groove 18 of the outer ring 12, the outer peripheral surface of the resin band 19 is ground by a centerless grinding machine or the like to be formed with a predetermined outer diameter. As a result, the squealing with the knuckle 2 can be stabilized, preload loss and bearing creep can be more effectively prevented, and the resin band 19 is not lost due to excessive squeezing during press-fitting. Note that after the resin band 19 is molded, the outer peripheral surface of the outer ring 12 and the resin band 19 may be ground integrally.

図４は、本発明に係る車輪用軸受の第２の実施形態を示す縦断面図である。本実施形態は、前述した第１の実施形態（図２）と外輪の構成のみが異なるだけで、その他同一の部品また同一の部位には同じ符号を付してその詳細な説明を省略する。   FIG. 4 is a longitudinal sectional view showing a second embodiment of the wheel bearing according to the present invention. This embodiment is different from the first embodiment (FIG. 2) only in the configuration of the outer ring, and the same reference numerals are assigned to the same parts or the same parts, and the detailed description thereof is omitted.

本実施形態では、外輪２０の外周に一対の環状溝２１、２１が形成され、これら環状溝２１、２１は、その溝幅Ｌ１が外側転走面１２ａの形成域Ｌ２よりも大きく、少なくとも外側転走面１２ａの幅方向全域にそれぞれ形成されている（Ｌ１≧Ｌ２）。これにより、温度上昇時、この環状溝２１に充填された樹脂バンド２２により、少なくともこの外側転走面１２ａの形成域Ｌ２が膨張するのを抑制し、外側転走面１２ａの曲率が崩れるのを防止することができる。したがって、初期に設定した予圧量が変化するのを防止して軸受剛性の変動を抑え、所望の耐久性を確保することができる。   In the present embodiment, a pair of annular grooves 21 and 21 are formed on the outer periphery of the outer ring 20, and the annular grooves 21 and 21 have a groove width L1 larger than the formation area L2 of the outer rolling surface 12a, and at least outward rolling. Each is formed in the entire width direction of the running surface 12a (L1 ≧ L2). Thereby, when the temperature rises, at least the formation region L2 of the outer rolling surface 12a is prevented from expanding by the resin band 22 filled in the annular groove 21, and the curvature of the outer rolling surface 12a is destroyed. Can be prevented. Therefore, it is possible to prevent a change in the preload amount set in the initial stage, suppress a variation in bearing rigidity, and secure desired durability.

図５は、本発明に係る車輪用軸受の第３の実施形態を示す縦断面図である。本実施形態は前述した実施形態と外輪の構成のみが異なるだけで、その他同一の部品また同一の部位には同じ符号を付してその詳細な説明を省略する。   FIG. 5 is a longitudinal sectional view showing a third embodiment of the wheel bearing according to the present invention. This embodiment is different from the above-described embodiment only in the configuration of the outer ring, and the same reference numerals are given to the same parts or the same parts, and the detailed description thereof is omitted.

本実施形態では、外輪２３の外周に単一の環状溝２４が形成されている。この環状溝２４は、複列の外側転走面１２ａ、１２ａを跨いで、外輪２３の外周中央部に形成されている。そして、少なくとも複列の外側転走面１２ａ、１２ａの幅方向全域に形成されている。これにより、温度上昇時、この環状溝２４に充填された樹脂バンド２５により、すくなくともこれら複列の外側転走面１２ａ、１２ａの形成域全域に亙って膨張するのを抑制し、複列の外側転走面１２ａ、１２ａの曲率が崩れるのを防止することができる。   In the present embodiment, a single annular groove 24 is formed on the outer periphery of the outer ring 23. The annular groove 24 is formed in the center of the outer periphery of the outer ring 23 so as to straddle the double row outer rolling surfaces 12a, 12a. And it forms in the width direction whole region of the outer side rolling surfaces 12a and 12a of double row at least. Thereby, when the temperature rises, the resin band 25 filled in the annular groove 24 suppresses expansion over the entire region where the outer rolling surfaces 12a and 12a of the double rows are at least formed. It can prevent that the curvature of the outer side rolling surfaces 12a and 12a collapse | crumbles.

図６は、本発明に係る車輪用軸受の第４の実施形態を示す縦断面図である。なお、この実施形態は、前述した実施形態と軸受の構成が異なる。   FIG. 6 is a longitudinal sectional view showing a fourth embodiment of the wheel bearing according to the present invention. In addition, this embodiment differs in the structure of a bearing from embodiment mentioned above.

この車輪用軸受２６は、外輪２７と一対の内輪２８、２８と複列の円すいころ２９、２９とを備えた複列円すいころ軸受からなる。外輪２７の内周面には、テーパ状に形成された複列の外側転走面２７ａ、２７ａが一体に形成されている。一方、一対の内輪２８、２８の外周面には、外側転走面２７ａ、２７ａに対向する内側転走面２８ａ、２８ａがそれぞれ形成されている。そして、複列の円すいころ２９、２９がこれら転走面２７ａ、２８ａ間にそれぞれ収容され、内輪２８の大径側に形成された大鍔２８ｂに案内され、保持器３０、３０により転動自在に保持されている。車輪用軸受２６の端部にはシール３１、３１が装着され、軸受内部に封入された潤滑グリースの漏洩と、外部からの雨水やダスト等が軸受内部に侵入するのを防止している。   The wheel bearing 26 includes a double-row tapered roller bearing including an outer ring 27, a pair of inner rings 28 and 28, and double-row tapered rollers 29 and 29. Double-row outer rolling surfaces 27 a and 27 a formed in a tapered shape are integrally formed on the inner peripheral surface of the outer ring 27. On the other hand, inner rolling surfaces 28a, 28a facing the outer rolling surfaces 27a, 27a are formed on the outer peripheral surfaces of the pair of inner rings 28, 28, respectively. Double-row tapered rollers 29 and 29 are respectively accommodated between the rolling surfaces 27a and 28a, guided to a large flange 28b formed on the large diameter side of the inner ring 28, and freely rollable by cages 30 and 30. Is held in. Seals 31, 31 are attached to the end of the wheel bearing 26 to prevent leakage of lubricating grease sealed inside the bearing and intrusion of rainwater and dust from the outside into the bearing.

本実施形態では、外輪２７の外周に一対の環状溝３２、３２が形成されている。これら環状溝３２、３２は、その溝幅Ｌ３が円すいころ２９の投影幅略中央の位置、すなわち、複列の外側転走面２７ａ、２７ａの形成域Ｌ４の略中央位置にそれぞれ設定されている。これにより、前述した実施形態と同様、予圧抜けと軸受クリープを効果的に防止することができる。さらに、その溝幅Ｌ３が外側転走面２７ａの形成域Ｌ４よりも大きく、少なくとも外側転走面２７ａの幅方向全域に形成されている（Ｌ３≧Ｌ４）。これにより、温度上昇時、この環状溝３２に充填された樹脂バンド３３により、すくなくともこの外側転走面２７ａの形成域Ｌ４が膨張するのを抑制し、外側転走面２７ａの母線形状が崩れるのを防止することができる。したがって、初期に設定した予圧量が変化するのを防止して軸受剛性の変動を抑え、所望の耐久性を確保することができる。   In the present embodiment, a pair of annular grooves 32, 32 are formed on the outer periphery of the outer ring 27. The annular grooves 32 and 32 have a groove width L3 set at a position approximately in the center of the projected width of the tapered roller 29, that is, approximately in the center position of the formation region L4 of the double row outer rolling surfaces 27a and 27a. . Thereby, preload loss and bearing creep can be effectively prevented as in the embodiment described above. Further, the groove width L3 is larger than the formation area L4 of the outer rolling surface 27a, and is formed at least in the entire width direction of the outer rolling surface 27a (L3 ≧ L4). Thereby, when the temperature rises, the resin band 33 filled in the annular groove 32 suppresses at least the formation region L4 of the outer rolling surface 27a from expanding, and the bus bar shape of the outer rolling surface 27a is broken. Can be prevented. Therefore, it is possible to prevent a change in the preload amount set in the initial stage, suppress a variation in bearing rigidity, and secure desired durability.

図７は、本発明に係る車輪用軸受の第５の実施形態を示す縦断面図である。本実施形態は前述した第４の実施形態（図６）と外輪の構成のみが異なるだけで、その他同一の部品また同一の部位には同じ符号を付してその詳細な説明を省略する。   FIG. 7 is a longitudinal sectional view showing a fifth embodiment of the wheel bearing according to the present invention. This embodiment is different from the above-described fourth embodiment (FIG. 6) only in the configuration of the outer ring, and the same reference numerals are given to the same parts or the same parts, and the detailed description thereof is omitted.

本実施形態では、外輪３４の外周に単一の環状溝３５が形成されている。この環状溝３５は、複列の外側転走面２７ａ、２７ａを跨いで、外輪３４の外周中央部に形成されている。そして、少なくとも複列の外側転走面２７ａ、２７ａの幅方向全域に形成されている。これにより、温度上昇時、この環状溝３５に充填された樹脂バンド３６により、すくなくともこれら複列の外側転走面２７ａ、２７ａの形成域全域に亙って膨張するのを抑制し、複列の外側転走面２７ａ、２７ａの母線形状が崩れるのを防止することができる。   In the present embodiment, a single annular groove 35 is formed on the outer periphery of the outer ring 34. The annular groove 35 is formed in the center of the outer periphery of the outer ring 34 so as to straddle the double row outer rolling surfaces 27a, 27a. And it forms in the width direction whole region at least of the double row outer side rolling surfaces 27a and 27a. Thereby, when the temperature rises, the resin band 36 filled in the annular groove 35 suppresses expansion over the entire region where the outer rolling surfaces 27a, 27a of the double rows are at least formed. It can prevent that the bus-line shape of the outer side rolling surfaces 27a and 27a collapse | crumbles.

以上、本発明の実施の形態について説明を行ったが、本発明はこうした実施の形態に何等限定されるものではなく、あくまで例示であって、本発明の要旨を逸脱しない範囲内において、さらに種々なる形態で実施し得ることは勿論のことであり、本発明の範囲は、特許請求の範囲の記載によって示され、さらに特許請求の範囲に記載の均等の意味、および範囲内のすべての変更を含む。   The embodiment of the present invention has been described above, but the present invention is not limited to such an embodiment, and is merely an example, and various modifications can be made without departing from the scope of the present invention. Of course, the scope of the present invention is indicated by the description of the scope of claims, and further, the equivalent meanings described in the scope of claims and all modifications within the scope of the scope of the present invention are included. Including.

本発明に係る車輪用軸受装置は、懸架装置を構成するナックルが、鋼よりも線膨張係数が大きなアルミ合金等の軽合金からなる構造の車輪用軸受装置に適用できる。   The wheel bearing device according to the present invention can be applied to a wheel bearing device having a structure in which the knuckle constituting the suspension device is made of a light alloy such as an aluminum alloy having a larger linear expansion coefficient than steel.

本発明に係る車輪用軸受装置の第１の実施形態を示す縦断面図である。It is a longitudinal section showing a 1st embodiment of a bearing device for wheels concerning the present invention. 同上、車輪用軸受を示す縦断面図である。It is a longitudinal cross-sectional view which shows a wheel bearing same as the above. 従来の車輪用軸受と本実施形態に係る車輪用軸受の温度変化と軸受予圧の変化の関係を比較測定した結果を示すグラフである。It is a graph which shows the result of having comparatively measured the relationship between the temperature change of the conventional wheel bearing and the wheel bearing which concerns on this embodiment, and the change of a bearing preload. 本発明に係る車輪用軸受の第２の実施形態を示す縦断面図である。It is a longitudinal cross-sectional view which shows 2nd Embodiment of the wheel bearing which concerns on this invention. 本発明に係る車輪用軸受の第３の実施形態を示す縦断面図である。It is a longitudinal cross-sectional view which shows 3rd Embodiment of the wheel bearing which concerns on this invention. 本発明に係る車輪用軸受の第４の実施形態を示す縦断面図である。It is a longitudinal cross-sectional view which shows 4th Embodiment of the wheel bearing which concerns on this invention. 本発明に係る車輪用軸受の第５の実施形態を示す縦断面図である。It is a longitudinal cross-sectional view which shows 5th Embodiment of the wheel bearing which concerns on this invention. 従来の車輪用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 wheel bearing apparatus.

符号の説明Explanation of symbols

１・・・・・・・・・・・・・・・・・ハブ輪
２・・・・・・・・・・・・・・・・・ナックル
３、２６・・・・・・・・・・・・・・車輪用軸受
４・・・・・・・・・・・・・・・・・車輪取付フランジ
４ａ・・・・・・・・・・・・・・・・ハブボルト
５・・・・・・・・・・・・・・・・・小径段部
６、１０ａ・・・・・・・・・・・・・セレーション
７・・・・・・・・・・・・・・・・・等速自在継手
８・・・・・・・・・・・・・・・・・外側継手部材
９・・・・・・・・・・・・・・・・・肩部
１０・・・・・・・・・・・・・・・・ステム部
１０ｂ・・・・・・・・・・・・・・・ねじ部
１１・・・・・・・・・・・・・・・・固定ナット
１２、２０、２３、２７、３４・・・・外輪
１２ａ、２７ａ・・・・・・・・・・・外側転走面
１３、２８・・・・・・・・・・・・・内輪
１３ａ、２８ａ・・・・・・・・・・・内側転走面
１４・・・・・・・・・・・・・・・・ボール
１５、３０・・・・・・・・・・・・・保持器
１６、１７、３１・・・・・・・・・・シール
１８、２１、２４、３２、３５・・・・環状溝
１９、２２、２５、３３、３６・・・・樹脂バンド
２８ｂ・・・・・・・・・・・・・・・大鍔
２９・・・・・・・・・・・・・・・・円すいころ
５０・・・・・・・・・・・・・・・・車輪用軸受装置
５１・・・・・・・・・・・・・・・・ハブ輪
５２・・・・・・・・・・・・・・・・外輪
５３・・・・・・・・・・・・・・・・内輪
５４・・・・・・・・・・・・・・・・車輪用軸受
５５・・・・・・・・・・・・・・・・ナックル
５６・・・・・・・・・・・・・・・・等速自在継手
５７、Ｂ・・・・・・・・・・・・・・ブレーキロータ
Ｗ・・・・・・・・・・・・・・・・・車輪
Ｌ１、Ｌ３・・・・・・・・・・・・・環状溝の幅寸法
Ｌ２、Ｌ４・・・・・・・・・・・・・外側転走面の形成域 1 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Hub wheel 2 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Knuckle 3, 26 ・ ・ ・ ・ ・ ・ ・ ・······· Wheel bearing 4 ·············· Wheel mounting flange 4a ... ··············· Small diameter step 6, 10a ... Serration 7 ...・ ・ ・ ・ Constant velocity universal joint 8 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Outer joint member 9 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Shoulder 10・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Stem 10b ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Thread 11 ... Fixing nuts 12, 20, 23, 27, 34 ... Outer rings 12a, 27a ... Side rolling surfaces 13, 28 ... Inner rings 13a, 28a ... Inner rolling surfaces 14 ...・ ・ ・ ・ ・ ・ Ball 15, 30 ・ ・ ・ ・ ・ ・ ・ ・ Cage 16, 17, 31 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Seal 18, 21, 24, 32, 35 .......... Annular grooves 19, 22, 25, 33, 36 .... Resin band 28b .....・ ・ ・ ・ ・ ・ Taper roller 50 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Wheel bearing device 51 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Hub wheel 52 ... outer ring 53 ... inner ring 54 ...・ Wheel bearings 55 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Knuckle 56 ・ ・... Constant velocity universal joint 57, B ... Brake rotor W ...・ ・ ・ ・ Wheels L1, L3 ・ ・ ・ ・ ・ ・ ・ ・ Width dimension L2, L4 of the annular groove ・ ・ ・ ・ ・ ・ ・ ・ Formation area of outer rolling surface

Claims (5)

一端部に車輪取付フランジを一体に有し、この車輪取付フランジから軸方向に延びる小径段部が形成されたハブ輪と、
懸架装置を構成し、軽合金からなるナックルと前記ハブ輪の小径段部との間に嵌合された車輪用軸受とからなり、
この車輪用軸受が、内周に複列の外側転走面が形成された外輪と、この外輪に内挿され、外周に前記複列の外側転走面に対向する内側転走面がそれぞれ形成された一対の内輪と、
前記両転走面間に転動自在に収容された複列の転動体とを備え、
前記ナックルに対して前記ハブ輪が回転自在に支承された車輪用軸受装置において、
前記外輪の外周に環状溝が形成され、この環状溝に耐熱性の合成樹脂からなる樹脂バンドが射出成形によって充填されると共に、当該環状溝が、前記転動体の投影幅略中央に位置するように設定されていることを特徴とする車輪用軸受装置。 A hub wheel integrally having a wheel mounting flange at one end, and a small-diameter step portion extending in the axial direction from the wheel mounting flange;
Comprising a suspension device, comprising a knuckle made of a light alloy and a wheel bearing fitted between a small diameter step portion of the hub wheel,
This wheel bearing has an outer ring having a double row outer raceway formed on the inner circumference, and an inner raceway that is inserted in the outer ring and faces the outer raceway of the double row on the outer circumference. A pair of inner rings,
A double row rolling element housed between the rolling surfaces so as to roll freely,
In the wheel bearing device in which the hub wheel is rotatably supported with respect to the knuckle,
An annular groove is formed on the outer periphery of the outer ring, and a resin band made of a heat-resistant synthetic resin is filled into the annular groove by injection molding, and the annular groove is positioned at substantially the center of the projected width of the rolling element. A bearing device for a wheel, characterized in that it is set to. 前記環状溝が、少なくとも前記外側転走面の幅方向全域に形成されている請求項１に記載の車輪用軸受装置。   The wheel bearing device according to claim 1, wherein the annular groove is formed at least in the entire width direction of the outer rolling surface. 前記外輪の外周に単一の環状溝が形成され、この環状溝が、前記複列の外側転走面を跨いで前記外輪の外周の幅中央部に形成されている請求項２に記載の車輪用軸受装置。   3. The wheel according to claim 2, wherein a single annular groove is formed on an outer periphery of the outer ring, and the annular groove is formed at a width center portion of the outer periphery of the outer ring across the double row outer raceway. Bearing device. 前記樹脂バンドがポリアミド系の合成樹脂からなり、その線膨張係数が８〜１６×１０−５／℃に設定されている請求項１乃至３いずれかに記載の車輪用軸受装置。 4. The wheel bearing device according to claim 1, wherein the resin band is made of a polyamide-based synthetic resin, and a linear expansion coefficient thereof is set to 8 to 16 × 10 −5 / ° C. 4. 前記樹脂バンドが、成形後に研削加工により所定の外径寸法に形成されている請求項１乃至４いずれかに記載の車輪用軸受装置。   The wheel bearing device according to any one of claims 1 to 4, wherein the resin band is formed to have a predetermined outer diameter by grinding after molding.
JP2004342812A 2004-11-26 2004-11-26 Bearing unit for wheel Pending JP2006153097A (en)

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016115515A1 (en) * 2016-08-22 2018-02-22 Dt Swiss Ag Hub and hub series
JP2018048724A (en) * 2016-09-23 2018-03-29 Ntn株式会社 Bearing device for wheel

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0333221U (en) * 1989-08-10 1991-04-02
JP2003343590A (en) * 2002-05-24 2003-12-03 Ntn Corp Creep preventive bearing
JP2004211820A (en) * 2003-01-06 2004-07-29 Ntn Corp Bearing device for wheel

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0333221U (en) * 1989-08-10 1991-04-02
JP2003343590A (en) * 2002-05-24 2003-12-03 Ntn Corp Creep preventive bearing
JP2004211820A (en) * 2003-01-06 2004-07-29 Ntn Corp Bearing device for wheel

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016115515A1 (en) * 2016-08-22 2018-02-22 Dt Swiss Ag Hub and hub series
JP2018048724A (en) * 2016-09-23 2018-03-29 Ntn株式会社 Bearing device for wheel

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