JP2006058052A - Bearing device for wheel - Google Patents

Bearing device for wheel Download PDF

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JP2006058052A
JP2006058052A JP2004237932A JP2004237932A JP2006058052A JP 2006058052 A JP2006058052 A JP 2006058052A JP 2004237932 A JP2004237932 A JP 2004237932A JP 2004237932 A JP2004237932 A JP 2004237932A JP 2006058052 A JP2006058052 A JP 2006058052A
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load
wheel
bearing device
wheel bearing
measuring means
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JP4812270B2 (en
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Shogo Suzuki
昭吾 鈴木
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NTN Corp
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NTN Corp
NTN Toyo Bearing Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
    • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
    • F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
    • F16C19/184—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement
    • F16C19/186—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement with three raceways provided integrally on parts other than race rings, e.g. third generation hubs

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  • Rolling Contact Bearings (AREA)
  • Force Measurement Appropriate To Specific Purposes (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a bearing device for a wheel capable of measuring accurately a load applied to the wheel using an inexpensive structure, without leaving any problem about the strength. <P>SOLUTION: This invention is applied to the bearing device for the wheel, wherein a plurality of rows of rolling bodies 3 are interposed in between opposite raceway surfaces 4, 5 of an external member 1 and an internal member 2. The device is provided with a load area measuring means 10 for measuring the load area of the rolling bodies 3, and a load estimation means 11 for estimating the load loaded to the bearing device for the wheel from a measured value by the load area measuring means 10. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

この発明は、車輪の軸受部にかかる荷重を検出する荷重センサを内蔵した車輪用軸受装置に関する。   The present invention relates to a wheel bearing device having a built-in load sensor for detecting a load applied to a bearing portion of the wheel.

従来、自動車の安全走行のために、各車輪の回転速度を検出するセンサを車輪用軸受に設けたものがある。このような車輪用軸受において、温度センサ、振動センサ等のセンサを設置し、回転速度の他に、自動車の運行に役立つ他の状態を検出できるようにしたものも提案されている（例えば特許文献１）。
特開２００３−２７９４２５号公報 2. Description of the Related Art Conventionally, there is a wheel bearing provided with a sensor for detecting the rotational speed of each wheel for safe driving of an automobile. In such wheel bearings, there are also proposed sensors in which sensors such as a temperature sensor and a vibration sensor are installed so that other states useful for driving a car can be detected in addition to the rotational speed (for example, Patent Documents). 1).
JP 2003-279425 A

従来の一般的な自動車の走行安全性確保対策は、各部の車輪の回転速度を検出することで行われているが、車輪の回転速度だけでは十分でなく、その他のセンサ信号を用いてさらに安全面での制御を可能とすることが求められている。そこで、車両走行時に各車輪に作用する荷重から姿勢制御を図ることも考えられる。例えばコーナリングにおいては外側車輪に大きな荷重がかかり、また左右傾斜面走行では片側車輪に、ブレーキングにおいては前輪にそれぞれ荷重が偏るなど、各車輪にかかる荷重は均等ではない。また、積載荷重不均等の場合にも、各車輪にかかる荷重は不均等になる。このため、車輪にかかる荷重を随時検出できれば、その検出結果に基づき、事前にサスペンション等を制御することで、車両走行時の姿勢制御（コーナリング時のローリング防止、ブレーキング時の前輪沈み込み防止、積載荷重不均等による沈み込み防止等）を行うことが可能となる。しかし、車輪に作用する荷重を検出するセンサの適切な設置場所がなく、荷重検出による姿勢制御の実現が難しい。   Conventional measures to ensure driving safety of general automobiles are performed by detecting the rotational speed of the wheels of each part, but the rotational speed of the wheels is not sufficient, and it is further safer by using other sensor signals. It is required to be able to control the surface. Therefore, it is conceivable to control the posture from the load acting on each wheel during vehicle travel. For example, a large load is applied to the outer wheel in cornering, and the load applied to each wheel is not uniform. In addition, even when the load is uneven, the load applied to each wheel is uneven. For this reason, if the load applied to the wheel can be detected at any time, based on the detection result, the suspension and the like are controlled in advance, thereby controlling the posture during vehicle travel (preventing rolling during cornering, preventing the front wheel from sinking during braking, It is possible to prevent subsidence due to uneven load capacity. However, there is no appropriate installation location of a sensor that detects a load acting on the wheel, and it is difficult to realize posture control by load detection.

特許文献１に示した荷重センサを内蔵した車輪用軸受では、ハブ輪の車輪取付フランジと、このフランジに車輪と重ねてボルトで締結されるブレーキロータとに互いに対面する環状凹部を形成し、これら両凹部間に圧電素子を設置することで、車輪に作用するトルクや路面反力等を前記圧電素子により測定している。しかし、このようにハブ輪の車輪取付フランジに環状凹部を形成すると、切り欠き効果によりハブ輪の耐久性が低下するという問題が有る。特に、通常の第３世代型の車輪用軸受装置では、強度上で最も弱い部位がハブ輪の車輪取付フランジであることが多いため、上記したように車輪取付フランジに圧電素子取付けのための環状凹部を形成する設計は極力回避しなければならない。また、圧電素子が取付けられるハブ輪は回転側部材であるため、圧電素子からの出力を外部に取り出すために、構造上の工夫が必要になり、コストアップの原因にもなる。   In the wheel bearing incorporating the load sensor shown in Patent Document 1, an annular recess facing each other is formed on the wheel mounting flange of the hub wheel and the brake rotor that is overlapped with the wheel and fastened with a bolt. By installing a piezoelectric element between the two concave portions, torque, road reaction force, and the like acting on the wheel are measured by the piezoelectric element. However, when the annular recess is formed in the wheel mounting flange of the hub wheel as described above, there is a problem that the durability of the hub wheel is lowered due to the notch effect. In particular, in the ordinary third-generation type wheel bearing device, the weakest part in strength is often the wheel mounting flange of the hub wheel. Therefore, as described above, the ring for mounting the piezoelectric element on the wheel mounting flange. The design to form the recess should be avoided as much as possible. In addition, since the hub wheel to which the piezoelectric element is attached is a rotation side member, in order to take out the output from the piezoelectric element to the outside, structural ingenuity is required, which causes a cost increase.

この発明の目的は、このような課題を解消し、強度上に問題を残すことなく、安価な構造で車輪にかかる荷重を精度良く測定できる車輪用軸受を提供することである。   An object of the present invention is to provide a wheel bearing capable of solving such a problem and accurately measuring a load applied to the wheel with an inexpensive structure without leaving a problem in strength.

この発明の車輪用軸受装置は、内周に複列の軌道面を有する外方部材と、これら軌道面に対向する複列の軌道面を有する内方部材と、対向する軌道面間に介在した複列の転動体とを備え、車体に対して車輪を回転自在に支持する車輪用軸受装置において、前記転動体の負荷域を測定する負荷域測定手段と、この負荷域測定手段の測定値から車輪用軸受装置に負荷される荷重を推定する荷重推測手段とを備えることを特徴とする。
車輪用軸受装置に負荷される荷重が変化すると、転動体荷重の負荷域の分布も変化する。この負荷域を負荷域測定手段が測定し、その測定値から荷重推測手段が車輪用軸受装置に負荷される荷重を推定する。負荷域の測定は、例えば外方部材の外径面で行える。これらのため、強度上に問題を残すことなく、安価な構造で車輪にかかる荷重を精度良く測定できる。 The wheel bearing device of the present invention is interposed between an outer member having a double row raceway surface on the inner periphery, an inner member having a double row raceway surface facing these raceway surfaces, and the opposing raceway surfaces. In a wheel bearing device comprising a double row rolling element and rotatably supporting a wheel with respect to a vehicle body, a load area measuring means for measuring a load area of the rolling element, and a measurement value of the load area measuring means Load estimation means for estimating a load applied to the wheel bearing device.
When the load applied to the wheel bearing device changes, the distribution of the load area of the rolling element load also changes. The load area measuring means measures this load area, and the load estimation means estimates the load applied to the wheel bearing device from the measured value. The load area can be measured, for example, on the outer diameter surface of the outer member. For these reasons, it is possible to accurately measure the load applied to the wheel with an inexpensive structure without leaving a problem in strength.

この発明において、前記負荷域測定手段が、外方部材の変形を測定する歪みゲージにより構成されていても良い。
外方部材は転動体荷重により変形するので、負荷域測定手段である歪みゲージにより外方部材の変形を測定することにより、転動体荷重の負荷域の分布を測定できる。 In this invention, the load area measuring means may be constituted by a strain gauge for measuring deformation of the outer member.
Since the outer member is deformed by the rolling element load, the distribution of the load area of the rolling element load can be measured by measuring the deformation of the outer member by a strain gauge as a load area measuring means.

この発明において、前記負荷域測定手段が、外方部材の変形を測定する圧電素子により構成されていても良い。この構成の場合も、負荷域測定手段である圧電素子が外方部材の変形を測定することで、転動体荷重の負荷域の分布を測定できる。   In the present invention, the load area measuring means may be constituted by a piezoelectric element that measures deformation of the outer member. Also in this configuration, the distribution of the load area of the rolling element load can be measured by measuring the deformation of the outer member by the piezoelectric element as the load area measuring means.

この発明において、前記負荷域測定手段が、車輪用軸受装置に生じる振動値を検出する振動検出手段であっても良い。
転動体は回転中に荷重非負荷域から負荷域に入ると、衝撃荷重を受け微小振動が発生する。この振動源を負荷域測定手段である振動検出手段で測定することにより負荷域を知ることができる。 In this invention, the load area measuring means may be a vibration detecting means for detecting a vibration value generated in the wheel bearing device.
When the rolling element enters the load range from the non-load range during rotation, it receives an impact load and generates minute vibrations. By measuring this vibration source with vibration detecting means which is load area measuring means, the load area can be known.

この発明の車輪用軸受装置は、内周に複列の軌道面を有する外方部材と、これら軌道面に対向する複列の軌道面を有する内方部材と、対向する軌道面間に介在した複列の転動体とを備え、車体に対して車輪を回転自在に支持する車輪用軸受装置において、前記転動体の負荷域を測定する負荷域測定手段と、この負荷域測定手段の測定値から車輪用軸受装置に負荷される荷重を推定する荷重推測手段とを設けたため、強度上に問題を残すことなく、安価な構造で車輪にかかる荷重を精度良く測定することができる。   The wheel bearing device of the present invention is interposed between an outer member having a double row raceway surface on the inner periphery, an inner member having a double row raceway surface facing these raceway surfaces, and the opposing raceway surfaces. In a wheel bearing device comprising a double row rolling element and rotatably supporting a wheel with respect to a vehicle body, a load area measuring means for measuring a load area of the rolling element, and a measurement value of the load area measuring means Since the load estimation means for estimating the load applied to the wheel bearing device is provided, the load applied to the wheel can be accurately measured with an inexpensive structure without leaving a problem in strength.

この発明の第１の実施形態を図１ないし図３と共に説明する。この実施形態の車輪用軸受装置は第３世代型の内輪回転タイプで、かつ駆動輪支持用の車輪用軸受に適用した例である。なお、この発明において、車両に取付けた状態で車両の車幅方向外側寄りとなる側をアウトボード側と言い、車両の中央寄りとなる側をインボード側と呼ぶ。図１では、左側がアウトボード側、右側がインボード側となる。
図１において、この車輪用軸受装置は、内周に複列の軌道面４を有する外方部材１と、これら軌道面４にそれぞれ対向する軌道面５を外周に有する内方部材２と、これら複列の軌道面４，５間に介在させた複列の転動体３とを備える。この軸受装置は、複列のアンギュラ玉軸受とされていて、上記各軌道面４，５は断面円弧状であり、各軌道面４，５は接触角が背面合わせとなるように形成されている。転動体３はボールからなり、各列毎に保持器６で保持されている。 A first embodiment of the present invention will be described with reference to FIGS. The wheel bearing device of this embodiment is an example applied to a wheel bearing for driving wheel support, which is a third generation inner ring rotating type. In the present invention, the side closer to the outer side in the vehicle width direction of the vehicle when attached to the vehicle is referred to as the outboard side, and the side closer to the center of the vehicle is referred to as the inboard side. In FIG. 1, the left side is the outboard side and the right side is the inboard side.
In FIG. 1, this wheel bearing device includes an outer member 1 having double-row raceway surfaces 4 on the inner periphery, an inner member 2 having raceway surfaces 5 on the outer periphery, which respectively face the raceway surfaces 4, A double row rolling element 3 interposed between the double row raceway surfaces 4 and 5. This bearing device is a double-row angular contact ball bearing, each of the raceway surfaces 4 and 5 has an arcuate cross section, and each of the raceway surfaces 4 and 5 is formed so that the contact angle is back to back. . The rolling elements 3 are formed of balls and are held by the cage 6 for each row.

外方部材１は固定側の部材となるものであって、図２のようにナックル（図示せず）に固定するための車体取付フランジ１ａを外周に有し、全体が一体の部材とされている。前記車体取付フランジ１ａは、車体（図示せず）に設置されたナックルに周方向複数箇所のボルト（図示せず）で締結される。なお図１は、図２におけるＡ−Ａ矢視断面図を示す。   The outer member 1 is a member on the fixed side, and has a vehicle body mounting flange 1a for fixing to a knuckle (not shown) on the outer periphery as shown in FIG. Yes. The vehicle body mounting flange 1a is fastened to a knuckle installed in a vehicle body (not shown) with a plurality of bolts (not shown) in the circumferential direction. 1 shows a cross-sectional view taken along line AA in FIG.

内方部材２は回転側の部材となるものであって、車輪取付フランジ２ａを外周に有するハブ輪２Ａと、このハブ輪２Ａのインボード側の端部外径面に嵌合した別体の内輪２Ｂとからなり、ハブ輪２Ａおよび内輪２Ｂに、各列の軌道面５がそれぞれ形成される。ハブ輪２Ａには軸継手の継手部材である等速ジョイント１３の外輪１３ａが連結されている。ハブ輪２Ａは中央穴９を有し、この中央穴９に等速ジョイント外輪１３ａに一体に形成されたステム部１４が挿通される。このステム部１４の先端の雄ねじ部にナット１２を螺合させ、ハブ輪２Ａの中央穴９におけるアウトボード側に形成された段面２ｂにナット１２を押し当てることで、等速ジョイント外輪１３ａがハブ輪２Ａに対してアウトボード側に押し付けられて連結される。また、ステム部１４はハブ輪２Ａの中央穴９にスプライン嵌合される。   The inner member 2 is a member on the rotation side, and a hub wheel 2A having a wheel mounting flange 2a on the outer periphery, and a separate member fitted to the outer diameter surface of the end portion on the inboard side of the hub wheel 2A. The inner race 2B is formed, and the raceway surfaces 5 of each row are formed on the hub race 2A and the inner race 2B, respectively. An outer ring 13a of a constant velocity joint 13 that is a joint member of a shaft joint is connected to the hub wheel 2A. The hub wheel 2A has a center hole 9, and a stem portion 14 formed integrally with the constant velocity joint outer ring 13a is inserted into the center hole 9. The constant velocity joint outer ring 13a is formed by screwing the nut 12 into the male threaded portion at the tip of the stem portion 14 and pressing the nut 12 against the step surface 2b formed on the outboard side in the central hole 9 of the hub wheel 2A. The hub wheel 2A is pressed and connected to the outboard side. The stem portion 14 is spline fitted into the central hole 9 of the hub wheel 2A.

内輪２Ｂは、等速ジョイント外輪１３ａにおけるステム部１４の基端の段面１３ａａが、ナット１２の締め付けで内輪２Ｂのインボード側幅面に押し当てられることにより、ハブ輪２Ａに対して軸方向に締め付け固定される。内外の部材２，１間に形成される環状空間のアウトボード側およびインボード側の各開口端部は、密封装置である接触式のシール７，８で密封されている。   In the inner ring 2B, the stepped surface 13aa at the proximal end of the stem portion 14 of the constant velocity joint outer ring 13a is pressed against the inboard side width surface of the inner ring 2B by tightening the nut 12, so that Tightened and fixed. The open end portions on the outboard side and the inboard side of the annular space formed between the inner and outer members 2 and 1 are sealed with contact-type seals 7 and 8 which are sealing devices.

外方部材１の外径面におけるインボード側の転動体列と対応する軸方向位置であって、周方向の等配位置の上位置（反路面側位置）および下位置（路面側位置）には、転動体列における転動体３の負荷域を測定する負荷域測定手段１０がそれぞれ設けられている。ここでは負荷域測定手段１０として、外方部材１の変形を測定する歪みゲージが用いられている。負荷域測定手段１０の設置位置は外方部材１の外径面であり、その設置によって車輪用軸受装置に強度上の問題が残ることはない。これとは別に、この２つの負荷域測定手段１０の測定値から車輪用軸受装置に負荷される荷重を推測する荷重推測手段１１が設けられている。また、負荷域測定手段１０は固定側の部材である外方部材１に設けられることから、負荷域測定手段１０の出力を荷重推測手段１１に送信するために構造上の工夫が要らず、コストアップを招くことはない。   Axial position corresponding to the inboard-side rolling element row on the outer diameter surface of the outer member 1, at an upper position (opposite road surface position) and a lower position (road surface side position) in the circumferentially equidistant position Are provided with load area measuring means 10 for measuring the load area of the rolling elements 3 in the rolling element row. Here, a strain gauge that measures the deformation of the outer member 1 is used as the load region measuring means 10. The installation position of the load region measuring means 10 is the outer diameter surface of the outer member 1, and the installation does not leave a problem in strength in the wheel bearing device. Separately from this, there is provided a load estimating means 11 for estimating the load applied to the wheel bearing device from the measured values of the two load area measuring means 10. Further, since the load area measuring means 10 is provided on the outer member 1 which is a fixed member, no structural device is required to transmit the output of the load area measuring means 10 to the load estimating means 11, and the cost is reduced. There is no uplift.

図３は、この車輪用軸受装置に負荷される荷重と負荷域との関係を示す説明図である。車輪用軸受装置は、車両に組み込んだ時には一般的に予圧状態にある。外部荷重が無負荷の時には、転動体３は図３（Ａ）のように全周にわたり均一荷重となり（転動体荷重：小）、したがって負荷域は大きい。しかし、外部から荷重負荷されると、負荷域は全周にわたり均一分布ではなくなり、図３（Ｂ）のように上位置側に負荷域が偏る。そして、負荷荷重が大きくなるにつれて、転動体荷重の偏りも大きくなり、負荷域が上位置側に集中する。つまり負荷域が小さくなる。   FIG. 3 is an explanatory diagram showing the relationship between the load applied to the wheel bearing device and the load area. A wheel bearing device is generally in a preload state when incorporated in a vehicle. When the external load is unloaded, the rolling element 3 has a uniform load over the entire circumference as shown in FIG. 3A (rolling element load: small), and therefore the load range is large. However, when a load is applied from the outside, the load area is not uniformly distributed over the entire circumference, and the load area is biased to the upper position side as shown in FIG. As the load load increases, the rolling element load bias increases, and the load area concentrates on the upper position side. That is, the load range is reduced.

次に、上記車輪用軸受装置での荷重推定動作について説明する。転動体荷重により外方部材１は変形するが、図３に示す負荷域が異なると外方部材１の変形も異なる。この車輪用軸受装置では、外方部材１の外径面に負荷域測定手段１０である歪みゲージを設けているので、この負荷域測定手段１０が外方部材１の変形を負荷域の変化として測定する。すなわち、この実施形態では、周方向の等配置位置、つまり上位置と下位置に分けて負荷域測定手段１０を配置しているので、これら２つの負荷域測定手段１０により、負荷域の分布状態を測定することができる。また、これらの負荷域測定手段１０の測定値は荷重推定手段１１に入力されて、荷重推定手段１１はその測定値に基づき車輪用軸受装置に負荷される荷重を推測する。すなわち、概略的に言えば、上記負荷域測定手段１０の測定する負荷域が例えば図３（Ｂ）のものである場合には、荷重推定手段１１は車輪用軸受装置に負荷される荷重が中程度のものと推定する。また、負荷域測定手段１０の測定する負荷域が例えば図３（Ｃ）のものである場合には、荷重推定手段１１は車輪用軸受装置に負荷される荷重が大であると推定する。   Next, the load estimation operation in the wheel bearing device will be described. Although the outer member 1 is deformed by the rolling element load, the deformation of the outer member 1 is different when the load area shown in FIG. 3 is different. In this wheel bearing device, since the strain gauge which is the load area measuring means 10 is provided on the outer diameter surface of the outer member 1, the load area measuring means 10 uses the deformation of the outer member 1 as a change in the load area. taking measurement. That is, in this embodiment, the load area measuring means 10 is arranged separately in the circumferentially equidistant position, that is, the upper position and the lower position, so that the load area distribution state is obtained by these two load area measuring means 10. Can be measured. Further, the measurement values of the load range measurement means 10 are input to the load estimation means 11, and the load estimation means 11 estimates the load applied to the wheel bearing device based on the measurement values. That is, roughly speaking, when the load area measured by the load area measuring means 10 is, for example, that shown in FIG. 3B, the load estimating means 11 has a medium load applied to the wheel bearing device. Estimated to be about. When the load area measured by the load area measuring means 10 is, for example, that shown in FIG. 3C, the load estimating means 11 estimates that the load applied to the wheel bearing device is large.

また、この実施形態では、転動体列（ここではインボード側の転動作体列）と対応する軸方向位置に負荷域測定手段１０を設けているので、負荷域の測定感度が向上する。なお、この実施形態では、２つの負荷域測定手段１０を周方向の等配位置に分配して設けているが、その数を３つ以上として周方向の等配位置に配置することにより、負荷域の測定精度をさらに向上させることができる。   Moreover, in this embodiment, since the load area measuring means 10 is provided in the axial position corresponding to the rolling element row (here, the inboard rolling element row), the measurement sensitivity of the load area is improved. In this embodiment, the two load area measuring means 10 are distributed and provided at the circumferentially equidistant positions. However, the number of the load area measuring means 10 can be three or more and arranged at the circumferentially equidistant positions. The measurement accuracy of the area can be further improved.

このように、この車輪用軸受装置では、転動体３の負荷域を測定する負荷域測定手段１０と、この負荷域測定手段１０の測定値から車輪用軸受装置に負荷される荷重を推定する荷重推測手段１１とを設けているので、車輪用軸受装置に強度上の問題を残すことなく、安価な構造で車輪にかかる荷重を精度良く測定できる。測定した荷重データは、ＡＢＳ（アンチロックブレーキシステム）やＴＣＳ（トラクションコントロールシステム）等の車両安定化のための各種装置のデータに利用することにより、車両の安定走行制御に寄与できる。   Thus, in this wheel bearing device, the load area measuring means 10 for measuring the load area of the rolling element 3 and the load for estimating the load applied to the wheel bearing apparatus from the measurement value of the load area measuring means 10 Since the estimation means 11 is provided, the load applied to the wheel can be accurately measured with an inexpensive structure without leaving a problem in strength in the wheel bearing device. The measured load data can be used for data of various devices for vehicle stabilization such as ABS (anti-lock brake system) and TCS (traction control system), thereby contributing to stable vehicle running control.

図４および図５は、この発明の他の実施形態を示す。この実施形態の車輪用軸受装置は、図１ないし図３に示す第１の実施形態において、転動体３の負荷域を測定する負荷域測定手段１０として、外方部材１の変形を測定する圧電素子を用いている。なお、図４は、図５におけるＢ−Ｂ矢視断面図を示す。また、この実施形態では、外方部材１の外径面の周方向の上位置にのみ負荷域測定手段１０を設けているが、第１の実施形態のように上下に等配して２つ設けても、さらに等配数を増やしても良い。その他の構成は第１の実施形態の場合と同じである。   4 and 5 show another embodiment of the present invention. The wheel bearing device of this embodiment is a piezoelectric device that measures the deformation of the outer member 1 as the load region measuring means 10 that measures the load region of the rolling element 3 in the first embodiment shown in FIGS. An element is used. 4 shows a cross-sectional view taken along the line BB in FIG. Further, in this embodiment, the load region measuring means 10 is provided only at the upper position in the circumferential direction of the outer diameter surface of the outer member 1, but the two are arranged equally above and below as in the first embodiment. Even if it is provided, the number of equal coordinates may be further increased. Other configurations are the same as those in the first embodiment.

なお、上記各実施形態では、負荷域測定手段１０として歪みゲージや圧電素子を用いた場合を示したが、これに限らず負荷域測定手段１０は、車輪用軸受装置に生じる振動値を検出する振動検出手段であっても良い。
すなわち、第１の実施形態の車輪用軸受装置において、転動体３は回転中に荷重非負荷域から負荷域に入ると、衝撃荷重を受け微小振動が発生する。この振動源を振動検出手段で測定することにより負荷域を知ることができ、負荷域の検出により外部からの入力荷重を推測できる。この場合、負荷域測定手段１０である振動検出手段は、外方部材１における周方向の上位置（反路面側の位置）に設けるのが好ましい。
この場合の振動源は、図３の説明図において、負荷域が小さい程（例えば図３（Ｃ）の状態）、検出位置に近づくことになる。また、負荷域が小さい程、転動体荷重が大きくなり、負荷域に転動体３が入った時の振動が大きい。この２つの理由により、上記したように上位置（反路面側の位置）に負荷域測定手段（振動検出手段）１０を配置することで、負荷域が小さくなる程、負荷域測定手段（振動検出手段）１０の検出する振動値が大きくなる。 In each of the above-described embodiments, the case where a strain gauge or a piezoelectric element is used as the load region measuring unit 10 is shown. It may be vibration detection means.
That is, in the wheel bearing device of the first embodiment, when the rolling element 3 enters the load region from the non-load region during rotation, a minute vibration is generated due to the impact load. The load range can be known by measuring the vibration source with the vibration detecting means, and the external input load can be estimated by detecting the load range. In this case, it is preferable that the vibration detection means which is the load region measurement means 10 is provided at the upper position in the circumferential direction (position on the opposite road surface side) of the outer member 1.
The vibration source in this case is closer to the detection position as the load region is smaller in the explanatory diagram of FIG. 3 (for example, the state of FIG. 3C). Further, the smaller the load area, the larger the rolling element load, and the greater the vibration when the rolling element 3 enters the load area. For these two reasons, the load area measuring means (vibration detecting means) 10 is arranged at the upper position (the position on the opposite road surface side) as described above. Means) The vibration value detected by 10 increases.

図６は、この発明のさらに他の実施形態を示す。この実施形態の車輪用軸受装置は複列のアンギュラ玉軸受形式のものであって、第１世代型に分類されるものである。この車輪用軸受装置では、外方部材１および内方部材２は、共にフランジを有せず、内方部材２の内周に別体のハブの軸部が嵌合する。外方部材１は全体が一体のものとされ、内方部材２は、２つの内輪２Ｂ１，２Ｂ２を軸方向に並べたものとされている。外方部材１の外径面におけるインボード側の転動体列に対応する軸方向位置の上位置と下位置に負荷域測定手段１０が設けられている。その他の構成は第１の実施形態の場合と同じである。   FIG. 6 shows still another embodiment of the present invention. The wheel bearing device of this embodiment is of a double row angular ball bearing type and is classified as a first generation type. In this wheel bearing device, both the outer member 1 and the inner member 2 do not have a flange, and the shaft portion of a separate hub is fitted to the inner periphery of the inner member 2. The outer member 1 is integrally formed as a whole, and the inner member 2 is formed by arranging two inner rings 2B1 and 2B2 in the axial direction. Load area measuring means 10 are provided at an upper position and a lower position in the axial position corresponding to the inboard rolling element row on the outer diameter surface of the outer member 1. Other configurations are the same as those in the first embodiment.

図７は、この発明の車輪用軸受装置のさらに他の実施形態を示す。この車輪用軸受装置も複列のアンギュラ玉軸受形式のものであって、第２世代型に分類されるものであり、駆動輪支持用である。この車輪用軸受装置では、第１の実施形態において、内方部材２が、ハブ輪２Ａと、このハブ輪２Ａの外径面に嵌合される内輪２Ｂとからなり、内輪２Ｂは軸方向に並ぶ２つの内輪２Ｂ１，２Ｂ２からなる。その他の構成は第１の実施形態の場合と同じである。   FIG. 7 shows still another embodiment of the wheel bearing device of the present invention. This wheel bearing device is also of the double-row angular ball bearing type, which is classified as the second generation type, and is for driving wheel support. In this wheel bearing device, in the first embodiment, the inner member 2 is composed of a hub wheel 2A and an inner ring 2B fitted to the outer diameter surface of the hub wheel 2A. It consists of two inner rings 2B1 and 2B2 arranged side by side. Other configurations are the same as those in the first embodiment.

図８は、この発明の車輪用軸受装置のさらに他の実施形態を示す。この車輪用軸受装置も複列のアンギュラ玉軸受形式のものであって、第４世代型に分類されるものであり、駆動輪支持用である。この車輪用軸受装置では、第１の実施形態において、内方部材２がハブ輪２Ａと等速ジョイント外輪１３ａとからなり、そのアウトボー側列の軌道面５がハブ輪２Ａの外径面に、インボード側列の軌道面５が等速ジョイント外輪１３ａの外径面にそれぞれ形成されている。また、インボード側のシール８は、外方部材１のインボード側端部と等速ジョイント外輪１３ａとの間の空間を密封する。その他の構成は第１の実施形態の場合と略同じである。   FIG. 8 shows still another embodiment of the wheel bearing device of the present invention. This wheel bearing device is also of the double row angular ball bearing type, which is classified as the fourth generation type, and is for driving wheel support. In this wheel bearing device, in the first embodiment, the inner member 2 is composed of the hub wheel 2A and the constant velocity joint outer ring 13a, and the raceway surface 5 of the outboard side row is on the outer diameter surface of the hub wheel 2A. The track surface 5 of the inboard side row is formed on the outer diameter surface of the constant velocity joint outer ring 13a. The inboard-side seal 8 seals the space between the inboard-side end of the outer member 1 and the constant velocity joint outer ring 13a. Other configurations are substantially the same as those in the first embodiment.

なお、前記各実施形態は、いずれもアンギュラ玉軸受形式の車輪用軸受装置に適用した場合につき説明したが、この発明は複列円すいころ軸受形式の車輪用軸受装置にも適用することができる。   In addition, although each said embodiment demonstrated the case where all were applied to the angular ball bearing type | formula wheel bearing apparatus, this invention is applicable also to the wheel bearing apparatus of a double row tapered roller bearing type | mold.

この発明の第１の実施形態にかかる車輪用軸受装置の断面図である。It is sectional drawing of the wheel bearing apparatus concerning 1st Embodiment of this invention. 図１におけるＣ方向から見た車輪用軸受装置の正面図である。It is a front view of the wheel bearing apparatus seen from the C direction in FIG. 車輪用軸受装置に負荷される転動体荷重と負荷域の関係を示す説明図である。It is explanatory drawing which shows the relationship between the rolling-element load loaded on the bearing apparatus for wheels, and a load area. この発明の他の実施形態にかかる車輪用軸受装置の断面図である。It is sectional drawing of the wheel bearing apparatus concerning other embodiment of this invention. 図４におけるＤ方向から見た車輪用軸受装置の正面図である。It is a front view of the wheel bearing apparatus seen from the D direction in FIG. この発明のさらに他の実施形態にかかる車輪用軸受装置の断面図である。It is sectional drawing of the wheel bearing apparatus concerning other embodiment of this invention. この発明のさらに他の実施形態にかかる車輪用軸受装置の断面図である。It is sectional drawing of the wheel bearing apparatus concerning other embodiment of this invention. この発明のさらに他の実施形態にかかる車輪用軸受装置の断面図である。It is sectional drawing of the wheel bearing apparatus concerning other embodiment of this invention.

符号の説明Explanation of symbols

１…外方部材
２…内方部材
３…転動体
４，５…軌道面
１０…負荷域測定手段
１１…荷重推定手段 DESCRIPTION OF SYMBOLS 1 ... Outer member 2 ... Inner member 3 ... Rolling elements 4, 5 ... Track surface 10 ... Load area measurement means 11 ... Load estimation means

Claims (4)

内周に複列の軌道面を有する外方部材と、これら軌道面に対向する複列の軌道面を有する内方部材と、対向する軌道面間に介在した複列の転動体とを備え、車体に対して車輪を回転自在に支持する車輪用軸受装置において、
前記転動体の負荷域を測定する負荷域測定手段と、この負荷域測定手段の測定値から車輪用軸受装置に負荷される荷重を推定する荷重推測手段とを備えることを特徴とする荷重センサ付車輪用軸受装置。 An outer member having a double-row raceway surface on the inner periphery, an inner member having a double-row raceway surface facing these raceway surfaces, and a double-row rolling element interposed between the opposing raceway surfaces, In the wheel bearing device that supports the wheel rotatably with respect to the vehicle body,
With a load sensor, comprising: a load area measuring means for measuring a load area of the rolling element; and a load estimating means for estimating a load applied to the wheel bearing device from a measurement value of the load area measuring means. Wheel bearing device. 請求項１において、前記負荷域測定手段が、外方部材の変形を測定する歪みゲージにより構成される荷重センサ付車輪用軸受装置。   The bearing device for a wheel with a load sensor according to claim 1, wherein the load area measuring means is constituted by a strain gauge that measures deformation of the outer member. 請求項１において、前記負荷域測定手段が、外方部材の変形を測定する圧電素子により構成される荷重センサ付車輪用軸受装置。   2. The wheel bearing device with a load sensor according to claim 1, wherein the load region measuring means is constituted by a piezoelectric element that measures deformation of the outer member. 請求項１において、前記負荷域測定手段が、車輪用軸受装置に生じる振動値を検出する振動検出手段である荷重センサ付車輪用軸受装置。   2. The wheel bearing device with a load sensor according to claim 1, wherein the load area measuring means is a vibration detecting means for detecting a vibration value generated in the wheel bearing device.
JP2004237932A 2004-08-18 2004-08-18 Wheel bearing device Expired - Fee Related JP4812270B2 (en)

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0961268A (en) * 1995-08-25 1997-03-07 Nippon Seiko Kk Load measuring apparatus for bearing
JP2004093357A (en) * 2002-08-30 2004-03-25 Nsk Ltd Evaluation method and evaluation device
JP2004142577A (en) * 2002-10-24 2004-05-20 Nsk Ltd Rolling bearing unit for wheel

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0961268A (en) * 1995-08-25 1997-03-07 Nippon Seiko Kk Load measuring apparatus for bearing
JP2004093357A (en) * 2002-08-30 2004-03-25 Nsk Ltd Evaluation method and evaluation device
JP2004142577A (en) * 2002-10-24 2004-05-20 Nsk Ltd Rolling bearing unit for wheel

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