JP2005055379A - Ball bearing unit for load measurement - Google Patents

Ball bearing unit for load measurement Download PDF

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JP2005055379A
JP2005055379A JP2003288475A JP2003288475A JP2005055379A JP 2005055379 A JP2005055379 A JP 2005055379A JP 2003288475 A JP2003288475 A JP 2003288475A JP 2003288475 A JP2003288475 A JP 2003288475A JP 2005055379 A JP2005055379 A JP 2005055379A
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Prior art keywords
revolution speed
speed detection
bearing unit
load
rolling bearing
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JP2003288475A
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Japanese (ja)
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Mamoru Aoki
護 青木
Masamitsu Watabe
将充 渡部
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NSK Ltd
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NSK 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
    • F16C41/00—Other accessories, e.g. devices integrated in the bearing not relating to the bearing function as such
    • F16C41/007—Encoders, e.g. parts with a plurality of alternating magnetic poles
    • 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
    • F16C19/52—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions
    • F16C19/522—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions related to load on the bearing, e.g. bearings with load sensors or means to protect the bearing against overload
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/38—Ball cages
    • F16C33/41—Ball cages comb-shaped
    • F16C33/412—Massive or moulded comb cages, e.g. snap ball cages
    • F16C33/414—Massive or moulded comb cages, e.g. snap ball cages formed as one-piece cages, i.e. monoblock comb cages
    • F16C33/416—Massive or moulded comb cages, e.g. snap ball cages formed as one-piece cages, i.e. monoblock comb cages made from plastic, e.g. injection moulded comb cages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
    • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
    • F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
    • F16C19/184—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement
    • F16C19/186—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement with three raceways provided integrally on parts other than race rings, e.g. third generation hubs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2326/00—Articles relating to transporting
    • F16C2326/01—Parts of vehicles in general
    • F16C2326/02—Wheel hubs or castors

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)
  • Force Measurement Appropriate To Specific Purposes (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a structure capable of manufacturing at low cost and also capable of correctly measuring the load on the ball bearing. <P>SOLUTION: The retainers 21a and 21b for retaining the double row balls 8a, and 8b are attached with encoders 26a, 26b, and the revolution speed detection sensors 24a, and 24b are oppositely facing to the encoders 26a, and 26b. The revolution speeds of balls 8a, 8b are freely detected. Based on the revolution speeds of the balls 8a, and 8b of both the rows, the load is calculated. Between both the revolution speed detection sensors 24a, and 24b, a magnetic substance 27 is provided so as to correctly detect the revolution speed of each of row balls 8a, and 8b. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

この発明は、例えば自動車、鉄道車両、各種搬送車等の移動体の車輪に負荷されるアキシアル荷重又はラジアル荷重を測定し、この移動体の運行の安定性確保を図る為に利用する、荷重測定用転がり軸受ユニットの改良に関する。   The present invention measures, for example, an axial load or a radial load applied to the wheels of a moving body such as an automobile, a railway vehicle, and various transport vehicles, and is used for ensuring the stability of operation of the moving body. The present invention relates to an improvement of a rolling bearing unit.

例えば自動車の車輪は懸架装置に対し、複列アンギュラ型の転がり軸受ユニットにより回転自在に支持する。又、自動車の走行安定性を確保する為に、アンチロックブレーキシステム（ＡＢＳ）やトラクションコントロールシステム（ＴＣＳ）、更にはビークルスタビリティコントロールシステム（ＶＳＣ）等の車両用走行安定装置が使用されている。この様な各種車両用走行安定装置を制御する為には、車輪の回転速度、車体に加わる各方向の加速度等の信号が必要になる。そして、より高度の制御を行なう為には、車輪を介して上記転がり軸受ユニットに加わるアキシアル荷重やラジアル荷重の大きさを知る事が好ましい場合がある。   For example, an automobile wheel is rotatably supported by a double row angular rolling bearing unit with respect to a suspension device. In order to ensure the running stability of automobiles, vehicle running stabilizers such as an antilock brake system (ABS), a traction control system (TCS), and a vehicle stability control system (VSC) are used. . In order to control such various vehicle running stabilizers, signals such as the rotational speed of the wheels and the acceleration in each direction applied to the vehicle body are required. In order to perform more advanced control, it may be preferable to know the magnitude of the axial load or radial load applied to the rolling bearing unit via the wheel.

この様な事情に鑑みて特許文献１、２には、図６、７に示す様な転がり軸受ユニットの荷重測定装置が記載されている。このうちの図６はアキシアル荷重を測定する為の、図７はラジアル荷重を測定する為の、それぞれ荷重測定用転がり軸受ユニットを示している。このうちの図６に示した従来構造の第１例では、回転輪であり内輪相当部材であるハブ１の外端部（軸方向に関して外とは、自動車への組み付け状態で車体の幅方向外側を言い、各図の左側）外周面に、車輪を支持する為の回転側フランジ２を固設している。又、上記ハブ１の中間部乃至内端部（軸方向に関して内とは、自動車への組み付け状態で車体の幅方向中央側を言い、各図の右側）外周面には、それぞれが回転側軌道である複列の内輪軌道３、３を形成している。   In view of such circumstances, Patent Documents 1 and 2 describe a load measuring device for a rolling bearing unit as shown in FIGS. Of these, FIG. 6 shows a rolling bearing unit for measuring the load, and FIG. 7 shows a rolling bearing unit for measuring the load for measuring the radial load. Among these, in the first example of the conventional structure shown in FIG. 6, the outer end of the hub 1 which is a rotating wheel and a member corresponding to the inner ring (the outside in the axial direction is the outside in the width direction of the vehicle body when assembled to the automobile The rotation side flange 2 for supporting the wheel is fixed to the outer peripheral surface of the left side of each figure. Further, the intermediate part or inner end part of the hub 1 (inside with respect to the axial direction means the center side in the width direction of the vehicle body in the assembled state in the automobile, and the right side in each figure), the outer peripheral surface has a rotation side track. The double-row inner ring raceways 3 and 3 are formed.

一方、上記ハブ１の周囲にこのハブ１と同心に配置された、静止輪であり外輪相当部材である外輪４の外周面には、この外輪４を懸架装置を構成するナックル５に支持固定する為の、固定側フランジ６を固設している。又、上記外輪４の内周面には、それぞれが静止側軌道である複列の外輪軌道７、７を形成している。そして、これら各外輪軌道７、７と上記各内輪軌道３、３との間に、それぞれが転動体である複数の玉８、８を、それぞれ複数個ずつ転動自在に設ける事により、上記外輪４の内径側に上記ハブ１を回転自在に支持している。   On the other hand, the outer ring 4 is supported and fixed to the knuckle 5 constituting the suspension device on the outer peripheral surface of the outer ring 4 which is a stationary wheel and is a member equivalent to the outer ring, which is arranged around the hub 1 and concentrically with the hub 1. For this purpose, a fixed side flange 6 is fixed. Further, on the inner peripheral surface of the outer ring 4, double-row outer ring raceways 7 and 7, each of which is a stationary side raceway, are formed. Then, a plurality of balls 8, 8 each of which is a rolling element are provided between the outer ring raceways 7, 7 and the inner ring raceways 3, 3, respectively, so that each of the balls can roll freely. The hub 1 is rotatably supported on the inner diameter side of 4.

更に、上記固定側フランジ６の内側面複数個所で、この固定側フランジ６を上記ナックル５に結合する為のボルト９を螺合する為のねじ孔１０を囲む部分には、それぞれ荷重センサ１１を添設している。上記外輪４を上記ナックル５に支持固定した状態でこれら各荷重センサ１１は、このナックル５の外側面と上記固定側フランジ６の内側面との間で挟持される。   Further, load sensors 11 are respectively provided at portions on the inner side surface of the fixed side flange 6 around screw holes 10 for screwing bolts 9 for connecting the fixed side flange 6 to the knuckle 5. It is attached. Each load sensor 11 is sandwiched between the outer surface of the knuckle 5 and the inner surface of the fixed flange 6 in a state where the outer ring 4 is supported and fixed to the knuckle 5.

この様な従来から知られている転がり軸受ユニットの荷重測定装置の第１例の場合、図示しない車輪と上記ナックル５との間にアキシアル荷重が加わると、上記ナックル５の外側面と上記固定側フランジ６の内側面とが、上記各荷重センサ１１を、軸方向両面から強く押し付け合う。従って、これら各荷重センサ１１の測定値を合計する事で、上記車輪と上記ナックル５との間に加わるアキシアル荷重を求める事ができる。又、図示はしないが、特許文献３には、一部の剛性を低くした外輪相当部材の振動周波数から転動体の公転速度を求め、更に、転がり軸受に加わるアキシアル荷重を測定する方法が記載されている。   In the case of a first example of such a conventionally known load measuring device for a rolling bearing unit, when an axial load is applied between a wheel (not shown) and the knuckle 5, the outer surface of the knuckle 5 and the fixed side The inner surface of the flange 6 strongly presses each load sensor 11 from both sides in the axial direction. Therefore, the axial load applied between the wheel and the knuckle 5 can be obtained by summing up the measured values of the load sensors 11. Although not shown, Patent Document 3 describes a method of obtaining the revolution speed of the rolling element from the vibration frequency of a member corresponding to an outer ring having a reduced rigidity, and measuring the axial load applied to the rolling bearing. ing.

又、図７に示した従来構造の第２例では、懸架装置に支持される、静止輪であり外輪相当部材である外輪４ａの内径側に、車輪を結合固定する、回転輪であり内輪相当部材であるハブ１ａを支持している。このハブ１ａは、車輪を固定する為の回転側フランジ２ａをその外端部に有するハブ本体１２と、このハブ本体１２の内端部に外嵌されてナット１３により抑え付けられた内輪１４とを備える。そして、上記外輪４ａの内周面に形成した、それぞれが静止側軌道である複列の外輪軌道７、７と、上記ハブ１ａの外周面に形成した、それぞれが回転側軌道である複列の内輪軌道３、３との間に、それぞれが転動体である玉８、８を複数個ずつ配置して、上記外輪４ａの内径側での上記ハブ１ａの回転を自在としている。   Further, in the second example of the conventional structure shown in FIG. 7, the rotating wheel is equivalent to the inner ring, and is fixed to the inner diameter side of the outer ring 4a, which is a stationary wheel and is an outer ring equivalent member, supported by the suspension device. The hub 1a which is a member is supported. The hub 1a includes a hub body 12 having a rotation side flange 2a for fixing a wheel at an outer end thereof, and an inner ring 14 that is externally fitted to the inner end portion of the hub body 12 and is held down by a nut 13. Is provided. And the double-row outer ring raceways 7 and 7 each formed on the inner peripheral surface of the outer ring 4a are stationary side tracks, and the double-row outer ring raceways formed on the outer peripheral surface of the hub 1a. A plurality of balls 8, 8 each of which is a rolling element are arranged between the inner ring raceways 3, 3 so that the hub 1a can freely rotate on the inner diameter side of the outer ring 4a.

上記外輪４ａの軸方向中間部で複列の外輪軌道７、７の間部分に、この外輪４ａを直径方向に貫通する取付孔１５を、この外輪４ａの上端部にほぼ鉛直方向に形成している。そして、この取付孔１５内に、荷重測定用のセンサである、円杆状（棒状）の変位センサ１６を装着している。この変位センサ１６は非接触式で、先端面（下端面）に設けた検出面は、ハブ１ａの軸方向中間部に外嵌固定したセンサリング１７の外周面に近接対向させている。上記変位センサ１６は、上記検出面と上記センサリング１７の外周面との距離が変化した場合に、その変化量に対応した信号を出力する。   A mounting hole 15 that diametrically penetrates the outer ring 4a is formed in a substantially vertical direction at an upper end portion of the outer ring 4a in a portion between the double row outer ring raceways 7 and 7 at an intermediate portion in the axial direction of the outer ring 4a. Yes. In the mounting hole 15, a circular (rod-shaped) displacement sensor 16, which is a load measuring sensor, is mounted. This displacement sensor 16 is a non-contact type, and the detection surface provided on the front end surface (lower end surface) is closely opposed to the outer peripheral surface of the sensor ring 17 that is externally fitted and fixed to the axially intermediate portion of the hub 1a. When the distance between the detection surface and the outer peripheral surface of the sensor ring 17 changes, the displacement sensor 16 outputs a signal corresponding to the amount of change.

上述の様に構成する従来から知られている転がり軸受ユニットの荷重測定装置の第２例の場合、上記変位センサ１６の検出信号に基づいて、転がり軸受ユニットに加わる荷重を求める事ができる。即ち、車両の懸架装置に支持した上記外輪４ａは、この車両の重量により下方に押されるのに対して、車輪を支持固定したハブ１ａは、そのままの位置に止まろうとする。この為、上記重量が嵩む程、上記外輪４ａやハブ１ａ、並びに転動体９ａ、９ｂの弾性変形に基づいて、これら外輪４ａの中心とハブ１ａの中心とのずれが大きくなる。そして、この外輪４ａの上端部に設けた、上記変位センサ１６の検出面と上記センサリング１７の外周面との距離は、上記重量が嵩む程短くなる。そこで、上記変位センサ１６の検出信号を制御器に送れば、予め実験等により求めた関係式或はマップ等から、当該変位センサ１６を組み込んだ転がり軸受ユニットに加わる荷重を求める事ができる。この様にして求めた、各転がり軸受ユニットに加わる荷重に基づいて、ＡＢＳを適正に制御する他、積載状態の不良を運転者に知らせる。   In the case of the second example of the conventionally known rolling bearing unit load measuring device configured as described above, the load applied to the rolling bearing unit can be obtained based on the detection signal of the displacement sensor 16. That is, the outer ring 4a supported by the vehicle suspension device is pushed downward by the weight of the vehicle, whereas the hub 1a supporting and fixing the wheel tends to stop at the same position. For this reason, the larger the weight, the greater the deviation between the center of the outer ring 4a and the center of the hub 1a based on the elastic deformation of the outer ring 4a, the hub 1a, and the rolling elements 9a, 9b. The distance between the detection surface of the displacement sensor 16 and the outer peripheral surface of the sensor ring 17 provided at the upper end of the outer ring 4a becomes shorter as the weight increases. Therefore, if the detection signal of the displacement sensor 16 is sent to the controller, the load applied to the rolling bearing unit in which the displacement sensor 16 is incorporated can be obtained from a relational expression or a map obtained beforehand through experiments or the like. Based on the load applied to each rolling bearing unit thus obtained, the ABS is appropriately controlled and the driver is informed of the poor loading state.

尚、図７に示した従来構造の第２例は、上記転がり軸受ユニットに加わる荷重に加えて、上記ハブ１ａの回転速度も検出自在としている。この為に、前記内輪１４の内端部にセンサロータ１８を外嵌固定すると共に、上記外輪４ａの内端開口部に被着したカバー１９に回転速度検出センサ２０を支持している。そして、この回転速度検出センサ２０の検知部を、上記センサロータ１８の被検出部に、検出隙間を介して対向させている。   In the second example of the conventional structure shown in FIG. 7, in addition to the load applied to the rolling bearing unit, the rotational speed of the hub 1a can also be detected. For this purpose, the sensor rotor 18 is fitted and fixed to the inner end portion of the inner ring 14, and the rotational speed detection sensor 20 is supported by a cover 19 attached to the inner end opening of the outer ring 4 a. And the detection part of this rotational speed detection sensor 20 is made to oppose the to-be-detected part of the said sensor rotor 18 through a detection gap.

上述の様な回転速度検出装置を組み込んだ転がり軸受ユニットの使用時、車輪を固定したハブ１ａと共に上記センサロータ１８が回転し、このセンサロータ１８の被検知部が上記回転速度検出センサ２０の検知部の近傍を走行すると、この回転速度検出センサ２０の出力が変化する。この様にして回転速度検出センサ２０の出力が変化する周波数は、上記車輪の回転数に比例する。従って、この回転速度検出センサ２０の出力信号を図示しない制御器に送れば、ＡＢＳやＴＣＳを適切に制御できる。   When the rolling bearing unit incorporating the rotational speed detection device as described above is used, the sensor rotor 18 rotates together with the hub 1a to which the wheel is fixed, and the detected portion of the sensor rotor 18 is detected by the rotational speed detection sensor 20. When traveling in the vicinity of the section, the output of the rotational speed detection sensor 20 changes. The frequency at which the output of the rotational speed detection sensor 20 changes in this way is proportional to the rotational speed of the wheel. Therefore, if the output signal of the rotational speed detection sensor 20 is sent to a controller (not shown), ABS and TCS can be controlled appropriately.

図６に示した従来構造の第１例の場合、ナックル５に対し外輪４を支持固定する為のボルト９と同数だけ、荷重センサ１１を設ける必要がある。この為、荷重センサ１１自体が高価である事と相まって、転がり軸受ユニットの荷重測定装置全体としてのコストが相当に嵩む事が避けられない。又、特許文献２に記載された方法は、外輪相当部材の一部の剛性を低くする必要があり、この外輪相当部材の耐久性確保が難しくなる可能性がある。   In the case of the first example of the conventional structure shown in FIG. 6, it is necessary to provide as many load sensors 11 as bolts 9 for supporting and fixing the outer ring 4 to the knuckle 5. For this reason, coupled with the fact that the load sensor 11 itself is expensive, it is inevitable that the cost of the entire load measuring device of the rolling bearing unit is considerably increased. Further, the method described in Patent Document 2 requires that the rigidity of a part of the outer ring equivalent member be lowered, and it may be difficult to ensure the durability of the outer ring equivalent member.

又、図７に示した従来構造の第２例の場合、変位センサ１６により、外輪４ａとハブ１ａとの径方向に関する変位を測定する事で、転がり軸受ユニットに加わる荷重を測定するが、この径方向に関する変位量は僅かである為、この荷重を精度良く求める為には、上記変位センサ１６として、高精度のものを使用する必要がある。高精度の非接触式センサは高価である為、やはり荷重測定装置付転がり軸受ユニット全体としてコストが嵩む事が避けられない。   In the case of the second example of the conventional structure shown in FIG. 7, the load applied to the rolling bearing unit is measured by measuring the displacement in the radial direction between the outer ring 4a and the hub 1a by the displacement sensor 16. Since the displacement amount in the radial direction is small, it is necessary to use a highly accurate displacement sensor 16 in order to obtain this load with high accuracy. Since high-precision non-contact sensors are expensive, it is inevitable that the cost of the entire rolling bearing unit with a load measuring device is increased.

この様な事情に鑑み、低コストで構成できて、耐久性に問題を生じる事がなく、各車輪に加わるアキシアル荷重を、制御の為に必要とされる精度を確保しつつ測定できる荷重測定用転がり軸受ユニットに関する発明として、特願２００３−１２００７２号、同２００３−１３３９３４号に開示されたものがある。この先発明の場合には、公転速度検出センサにより、転がり軸受ユニットに複列に配置した玉のうちの片側の列を構成する玉の公転速度を検出し、回転速度検出センサにより、ハブの回転速度を検出する。そして、これら両センサの検出信号に基づき、公転速度と回転速度との比である速度比を求める。アキシアル荷重が変化し、上記各玉の接触角が変化すると、これら各玉の公転速度、延ては上記速度比が変化するので、この速度比の変化に基づいて、上記アキシアル荷重を算出する。   In view of such circumstances, it can be configured at low cost, does not cause problems in durability, and can measure the axial load applied to each wheel while ensuring the accuracy required for control As inventions related to rolling bearing units, there are those disclosed in Japanese Patent Application Nos. 2003-120072 and 2003-133934. In the case of this prior invention, the revolution speed detection sensor detects the revolution speed of the balls constituting one side of the balls arranged in a double row on the rolling bearing unit, and the rotation speed detection sensor detects the rotation speed of the hub. Is detected. And based on the detection signal of both these sensors, the speed ratio which is a ratio of revolution speed and rotation speed is calculated | required. When the axial load changes and the contact angle of each ball changes, the revolution speed of each ball, and thus the speed ratio, changes. Therefore, the axial load is calculated based on the change in the speed ratio.

ところで、玉等の転動体の公転速度は、アキシアル荷重の大きさにより変化するだけでなく、予圧の大きさやラジアル荷重の大きさによっても変化する。言い換えれば、予圧又はラジアル荷重が、上記アキシアル荷重を求める事に対する、一種の漏話（クロストーク）成分として入り込む。従って、或る特定の（単列の）玉の公転速度だけを検出しても、転がり軸受ユニットに加わるアキシアル荷重を正確に求める事は難しい。上記先発明に係る転がり軸受ユニットの荷重測定装置の場合には、初期設定により予圧の影響を排除する事に加え、加速度、ヨーレート、舵角、操舵力のうちから選択される何れかの値から上記転がり軸受ユニットにアキシアル荷重が加わる状況か否かを判定して、このアキシアル荷重を正確に測定できる様にしている。従って、このアキシアル荷重を算出する為の演算器には、転がり軸受ユニット部分に設けたセンサの出力信号以外の信号も入力する。   By the way, the revolution speed of rolling elements such as balls changes not only according to the magnitude of the axial load, but also changes depending on the magnitude of the preload and the magnitude of the radial load. In other words, the preload or radial load enters as a kind of crosstalk component with respect to the determination of the axial load. Therefore, even if only the revolution speed of a specific (single row) ball is detected, it is difficult to accurately determine the axial load applied to the rolling bearing unit. In the case of the load measuring device for a rolling bearing unit according to the above invention, in addition to eliminating the influence of the preload by the initial setting, from any value selected from acceleration, yaw rate, steering angle, and steering force It is determined whether or not the axial load is applied to the rolling bearing unit so that the axial load can be accurately measured. Therefore, a signal other than the output signal of the sensor provided in the rolling bearing unit portion is also input to the arithmetic unit for calculating the axial load.

これに対して特願２００３−１７２４８３号には複列に配置された転動体の公転速度に基づいて転がり軸受ユニットに加わるアキシアル荷重を測定する構造が、同２００３−１７１７１５号には同じくラジアル荷重を測定する構造が、それぞれ記載されている。この様な第二の先発明の構造によれば、転がり軸受ユニット部分に設けたセンサの出力信号のみで、この転がり軸受ユニットに加わるアキシアル荷重又はラジアル荷重を正確に求められる構造を、低コストで実現できる。   On the other hand, Japanese Patent Application No. 2003-17283 has a structure for measuring the axial load applied to the rolling bearing unit based on the revolution speed of the rolling elements arranged in a double row, and No. 2003-171715 also has a radial load. Each structure to be measured is described. According to such a structure of the second prior invention, a structure in which an axial load or a radial load applied to the rolling bearing unit can be accurately obtained only by an output signal of a sensor provided in the rolling bearing unit portion can be obtained at low cost. realizable.

但し、上記第二の先発明の構造では、複列に配置された転動体同士の間に１対の公転速度検出センサを配置する必要がある。又、転がり軸受ユニットの円周方向に関する、これら両公転速度検出センサの設置位置（回転方向の位相）は、設置作業及び信号取り出し用ハーネスの取り回し容易化の面から一致させる必要がある。従って、上記両公転速度検出センサは、上記転がり軸受ユニットの軸方向に隣接した状態で配置される。又、これら両公転速度検出センサとして、磁気検知式のものを使用する事が、各転動体を設置した部分に封入したグリース等に妨げられる事なく、正確な公転速度検出を行なう面からは好ましい。   However, in the structure of the second prior invention, it is necessary to arrange a pair of revolution speed detection sensors between the rolling elements arranged in a double row. Further, the installation positions (phases in the rotational direction) of these revolution speed detection sensors with respect to the circumferential direction of the rolling bearing unit must be matched in terms of installation work and easy handling of the signal extraction harness. Therefore, the two revolution speed detection sensors are arranged in a state adjacent to the rolling bearing unit in the axial direction. In addition, it is preferable to use a magnetic detection type sensor as both of these revolution speed detection sensors in terms of accurate revolution speed detection without being obstructed by grease or the like enclosed in the portion where each rolling element is installed. .

ところが、それぞれが磁気検知式である１対の公転速度検出センサを近接配置した場合、何らの対策も施さないと、これら両公転速度検出センサ同士の間で磁束が干渉し、正確な公転速度検出が難しくなる可能性がある。特に、公転速度検出の信頼性を向上させるべく、上記両公転速度検出センサに内蔵した永久磁石、或はエンコーダとして保持器に支持した永久磁石の磁束密度を高くすると、却って、上記干渉に基づく公転速度検出の信頼性低下を来す可能性が高くなる。   However, when a pair of revolution speed detection sensors, each of which is magnetic detection type, are arranged close to each other, if no measures are taken, magnetic flux interferes between these two revolution speed detection sensors, and accurate revolution speed detection is performed. Can be difficult. In particular, in order to improve the reliability of the revolution speed detection, if the magnetic flux density of the permanent magnet built in the two revolution speed detection sensors or the permanent magnet supported by the cage as an encoder is increased, the revolution based on the interference is instead. There is a high possibility that the reliability of speed detection will be reduced.

特開平３−２０９０１６号公報Japanese Patent Laid-Open No. 3-209016 特開２００１−２１５７７号公報JP 2001-21577 A 特公昭６２−３３６５号公報Japanese Patent Publication No.62-3365

本発明は、１対の公転速度検出センサを近接配置した場合でも、これら両公転速度検出センサ同士の間で磁束の干渉を生じにくくする事により、公転速度検出の信頼性を向上させて、転がり軸受ユニットに加わる荷重を正確に検出できる構造を実現すべく発明したものである。   Even when a pair of revolution speed detection sensors are arranged close to each other, the present invention improves the reliability of revolution speed detection by making it difficult for magnetic flux interference to occur between the two revolution speed detection sensors. The invention was invented to realize a structure capable of accurately detecting the load applied to the bearing unit.

本発明の荷重測定用転がり軸受ユニットは、静止輪と、回転輪と、複数個の転動体と、１対の公転速度検出センサと、磁性体とを備える。
このうちの静止輪は、使用時にも回転しない。
又、上記回転輪は、この静止輪と同心に配置されて使用時に回転する。
又、上記各転動体は、これら静止輪と回転輪との互いに対向する部分にそれぞれ２列ずつ形成された静止側軌道と回転側軌道との間にそれぞれ複数個ずつ、接触角の方向を互いに逆にして転動自在に設けられている。
又、上記両公転速度検出センサは、両列の転動体同士の間に設けられて、これら両列の転動体の公転速度をそれぞれ円周方向に関する磁気特性の変化に基づいて検出する。
又、上記磁性体は、上記静止輪の軸方向に関して、上記両公転速度検出センサ同士の間に配置されている。 The load measuring rolling bearing unit of the present invention includes a stationary wheel, a rotating wheel, a plurality of rolling elements, a pair of revolution speed detection sensors, and a magnetic body.
Of these, the stationary wheels do not rotate during use.
The rotating wheel is arranged concentrically with the stationary wheel and rotates during use.
In addition, each of the rolling elements has a plurality of contact angle directions between the stationary-side track and the rotating-side track formed in two rows in the opposite portions of the stationary wheel and the rotating wheel, respectively. On the contrary, it is provided so that it can roll freely.
The both revolution speed detection sensors are provided between the rolling elements in both rows, and detect the revolution speeds of the rolling elements in both rows based on changes in the magnetic characteristics in the circumferential direction.
The magnetic body is disposed between the two revolution speed detection sensors with respect to the axial direction of the stationary wheel.

上述の様に構成する本発明の転がり軸受ユニットの荷重測定装置は、接触角の方向が互いに異なる１対の列の転動体の公転速度をそれぞれ検出する事により、上記転がり軸受ユニットに負荷されるアキシアル荷重又はラジアル荷重を測定できる。即ち、複列アンギュラ型の玉軸受の如き転がり軸受ユニットがアキシアル荷重又はラジアル荷重を負荷すると、転動体（玉）の接触角が変化する。転がり軸受の技術分野で周知の様に、転動体の公転速度は接触角が変化すると変化する。   The rolling bearing unit load measuring device of the present invention configured as described above is loaded on the rolling bearing unit by detecting the revolution speeds of a pair of rolling elements with different contact angle directions. Axial load or radial load can be measured. That is, when a rolling bearing unit such as a double row angular type ball bearing applies an axial load or a radial load, the contact angle of the rolling elements (balls) changes. As is well known in the technical field of rolling bearings, the revolution speed of the rolling elements changes as the contact angle changes.

具体的には、上記アキシアル荷重を支承する側の列に関しては、このアキシアル荷重が大きくなる程接触角が大きくなり、反対側の列に関してはこのアキシアル荷重が大きくなる程接触角が小さくなる。そして、外輪相当部材が回転輪の場合には上記アキシアル荷重を支承する側の列で転動体の公転速度が遅くなり、反対側の列で転動体の公転速度が速くなる。逆に、内輪相当部材が回転輪の場合には上記アキシアル荷重を支承する側の列で公転速度が速くなり、反対側の列で転動体の公転速度が遅くなる。従って、上記両列の転動体の公転速度の変化を測定する事で、上記転がり軸受ユニットに加わるアキシアル荷重を求める事ができる。同時に、上記両列の公転速度は、上記ラジアル荷重に応じても変化する。従って、これら両列の転動体の公転速度の変化を測定する事で、上記転がり軸受ユニットに加わるラジアル荷重を求める事もできる。   Specifically, for the row on which the axial load is supported, the contact angle increases as the axial load increases, and for the row on the opposite side, the contact angle decreases as the axial load increases. When the outer ring equivalent member is a rotating wheel, the revolution speed of the rolling elements is reduced in the row on which the axial load is supported, and the revolution speed of the rolling elements is increased in the opposite row. On the contrary, when the inner ring equivalent member is a rotating wheel, the revolution speed is increased in the row on which the axial load is supported, and the revolution speed of the rolling element is decreased in the opposite row. Therefore, the axial load applied to the rolling bearing unit can be obtained by measuring the change in the revolution speed of the rolling elements in both rows. At the same time, the revolution speed of the two rows also changes depending on the radial load. Therefore, the radial load applied to the rolling bearing unit can be obtained by measuring the change in the revolution speed of the rolling elements in both rows.

又、本発明の場合には、前述した第二の先発明の場合と同様に、接触角の方向が互いに異なる１対の列の転動体の公転速度を検出する為、予圧やラジアル荷重の影響を排除して、上記アキシアル荷重の測定精度を向上させる事ができる。即ち、上記予圧は各列の転動体に均等に加わるし、上記ラジアル荷重に関してもほぼ均等に加わる。従って、これら予圧及びラジアル荷重が上記各列の転動体の公転速度に及ぼす影響はほぼ同じになる。そこで、これら各列の転動体の公転速度の比、或は差に基づいて上記アキシアル荷重を求めれば、上記予圧やラジアル荷重がこのアキシアル荷重の測定値に及ぼす影響を低く抑えられる。
又、上記公転速度を測定する為の公転速度検出センサは、従来からＡＢＳやＴＣＳの制御用信号を得る為に広く使用されている、安価な速度センサを使用できる。この為、転がり軸受ユニットの荷重測定装置全体を安価に構成できる。 Further, in the case of the present invention, as in the case of the second prior invention described above, since the revolution speed of a pair of rolling elements with different contact angle directions is detected, the influence of preload and radial load is detected. The accuracy of measuring the axial load can be improved. In other words, the preload is equally applied to the rolling elements in each row, and the radial load is also applied substantially evenly. Therefore, the effects of the preload and the radial load on the revolution speed of the rolling elements in each row are almost the same. Therefore, if the axial load is obtained based on the ratio or difference between the revolution speeds of the rolling elements in each row, the influence of the preload and the radial load on the measured value of the axial load can be kept low.
Further, as the revolution speed detection sensor for measuring the revolution speed, an inexpensive speed sensor that has been widely used for obtaining control signals for ABS and TCS can be used. For this reason, the whole load measuring device of a rolling bearing unit can be constituted at low cost.

特に、本発明の場合には、近接配置された１対の公転速度検出センサ同士の間に磁性材を配置しているので、これら両公転速度検出センサ同士の間で磁束の干渉を生じにくくして、公転速度検出の信頼性を向上させる事ができる。
従って、比較的低コストで構成できるにも拘らず、各車輪等の回転部材に加わるアキシアル荷重を、制御の為に必要とされる精度を確保しつつ測定できる。この為、例えば、各種車両用走行安定装置の高性能化に寄与できる。 In particular, in the case of the present invention, a magnetic material is disposed between a pair of revolution speed detection sensors arranged in close proximity, so that magnetic flux interference is less likely to occur between these two revolution speed detection sensors. Thus, the reliability of revolution speed detection can be improved.
Therefore, although it can be configured at a relatively low cost, the axial load applied to the rotating member such as each wheel can be measured while ensuring the accuracy required for control. For this reason, for example, it can contribute to the performance enhancement of various vehicle travel stabilizers.

本発明を実施する場合に好ましくは、静止輪と回転輪とのうちの一方の軌道輪を外輪相当部材とし、他方の軌道輪を内輪相当部材とすると共に、各転動体を玉とする。そして、この内輪相当部材の外周面に形成された複列アンギュラ型の内輪軌道と上記外輪相当部材の内周面に形成された複列アンギュラ型の外輪軌道との間にそれぞれ複数個ずつ設けられた玉に、背面組み合わせ型の接触角を付与する。   Preferably, when carrying out the present invention, one of the stationary ring and the rotating ring is an outer ring equivalent member, the other race ring is an inner ring equivalent member, and each rolling element is a ball. A plurality of angular contact type inner ring raceways formed on the outer peripheral surface of the inner ring equivalent member and a plurality of double row angular outer ring raceways formed on the inner peripheral surface of the outer ring equivalent member are provided. A contact angle of the back combination type is given to the ball.

又、好ましくは、上記回転輪の回転速度を検出する為の回転速度検出センサを備え、両公転速度検出センサから送り込まれる検出信号と、この回転速度検出センサから送り込まれる検出信号とに基づいて、静止輪と回転輪との間に加わるアキシアル荷重とラジアル荷重とのうちの少なくとも一方の荷重を算出する。
この様に回転速度検出センサを設ければ、上記回転輪の回転速度が変化する状況でも、転がり軸受ユニットに加わる荷重を正確に測定できる。即ち、この転がり軸受ユニットが、回転輪の回転速度が常に一定の状態で使用されるものであれば、荷重算出の為の回転検出センサは、上記両公転速度検出センサのみで足りる。これに対して、使用時に上記回転輪の回転速度が変化する様な場合には、回転速度検出センサが検出するこの回転輪の回転速度と上記公転速度とにより、上記アキシアル荷重又はラジアル荷重を求める事ができる。 Preferably, a rotation speed detection sensor for detecting the rotation speed of the rotating wheel is provided, and based on a detection signal sent from both revolution speed detection sensors and a detection signal sent from the rotation speed detection sensor, At least one of an axial load and a radial load applied between the stationary wheel and the rotating wheel is calculated.
If the rotational speed detection sensor is provided in this manner, the load applied to the rolling bearing unit can be accurately measured even in a situation where the rotational speed of the rotating wheel changes. That is, if this rolling bearing unit is used in a state where the rotational speed of the rotating wheel is always constant, the rotation detection sensor for calculating the load need only be the both revolution speed detection sensors. On the other hand, when the rotational speed of the rotating wheel changes during use, the axial load or radial load is obtained from the rotational speed of the rotating wheel detected by the rotational speed detection sensor and the revolution speed. I can do things.

この場合に、上記両列の転動体の公転速度の差と回転速度との比である速度比を算出し、この速度比から上記アキシアル荷重を求めれば、上記回転輪の回転速度が変化しても、このアキシアル荷重を正確に求める事ができる。
又、ラジアル荷重に関しては、上記両列の転動体の公転速度の和と回転速度との比である速度比を算出し、この速度比から上記ラジアル荷重を求めれば、上記回転輪の回転速度が変化しても、このラジアル荷重を正確に求める事ができる。 In this case, if the speed ratio, which is the ratio between the revolution speed difference of the rolling elements in both rows and the rotational speed, is calculated, and the axial load is obtained from this speed ratio, the rotational speed of the rotating wheel changes. This axial load can be obtained accurately.
Regarding the radial load, the speed ratio, which is the ratio of the sum of the revolution speeds of the rolling elements in both rows and the rotational speed, is calculated, and if the radial load is obtained from this speed ratio, the rotational speed of the rotating wheel is calculated. Even if it changes, this radial load can be calculated accurately.

図１〜２は、本発明の実施例１を示している。本実施例は、自動車の従動輪（ＦＲ車、ＲＲ車、ＭＤ車の前輪、ＦＦ車の後輪）を支持する為の転がり軸受ユニットに本発明を適用した場合に就いて示している。この転がり軸受ユニットの構造に関しては、前述の図７に示した従来構造の第２例と同様であるから、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、本発明の特徴部分を中心に説明する。静止輪であり外輪相当部材である外輪４ａの内周面には、それぞれが静止側軌道である、複列アンギュラ型の外輪軌道７、７を形成している。そして、これら各外輪軌道７、７と、ハブ１ｂの外周面に設けた、それぞれが回転側軌道である、複列アンギュラ型の内輪軌道３、３との間に、それぞれが転動体である複数の玉８ａ、８ｂを複列（２列）に分けて、各列毎にそれぞれ複数個ずつ、保持器２１ａ、２１ｂにより保持した状態で転動自在に設ける事により、上記外輪４ａの内径側に上記ハブ１ｂを、回転自在に支持している。この状態で上記両列の玉８ａ、８ｂには、互いに逆方向で、且つ、同じ大きさの接触角αa 、αb （図２）が付与されて、背面組み合わせ型の、複列アンギュラ型玉軸受を構成する。上記各列の玉８ａ、８ｂには、使用時に加わるアキシアル荷重によって回転精度が劣化する事がない程度に、十分な予圧を付与している。 1 and 2 show Embodiment 1 of the present invention. The present embodiment shows a case where the present invention is applied to a rolling bearing unit for supporting a driven wheel of an automobile (FR wheel, RR vehicle, front wheel of MD vehicle, rear wheel of FF vehicle). Since the structure of this rolling bearing unit is the same as that of the second example of the conventional structure shown in FIG. 7 described above, the same reference numerals are given to the equivalent parts, and the overlapping description is omitted or simplified. The description will focus on the features of the present invention. Double row angular outer ring raceways 7 and 7, each of which is a stationary side raceway, are formed on the inner peripheral surface of the outer race 4 a that is a stationary wheel and an outer ring equivalent member. A plurality of rolling elements are provided between the outer ring raceways 7 and 7 and the double-row angular inner ring raceways 3 and 3, which are provided on the outer peripheral surface of the hub 1 b. The balls 8a and 8b are divided into double rows (two rows), and a plurality of balls 8a and 8b are provided for each row so that they can roll while being held by the cages 21a and 21b. The hub 1b is rotatably supported. In this state, the balls 8a and 8b in both rows are provided with contact angles α a and α b (FIG. 2) in opposite directions and the same magnitude, and are a double row angular type with a rear combination type. Configure ball bearings. Sufficient preload is applied to the balls 8a and 8b in each row so that the rotational accuracy does not deteriorate due to the axial load applied during use.

上述の様な転がり軸受ユニットを構成する上記外輪４ａの軸方向中間部で上記複列の外輪軌道７、７の間部分に取付孔１５ａを、この外輪４ａを径方向に貫通する状態で形成している。そして、この取付孔１５ａにセンサユニット２２を、上記外輪４ａの径方向外方から内方に挿通し、このセンサユニット２２の先端部に設けた検出部２３を、上記外輪４ａの内周面から突出させている。この検出部２３には、１対の公転速度検出センサ２４ａ、２４ｂを設けている。   A mounting hole 15a is formed in the intermediate portion of the outer ring 4a constituting the rolling bearing unit as described above between the double row outer ring raceways 7 and 7 so as to penetrate the outer ring 4a in the radial direction. ing. The sensor unit 22 is inserted into the mounting hole 15a from the radially outer side of the outer ring 4a to the inner side, and the detection unit 23 provided at the tip of the sensor unit 22 is inserted from the inner peripheral surface of the outer ring 4a. It is protruding. The detection unit 23 is provided with a pair of revolution speed detection sensors 24a and 24b.

これら両公転速度検出センサ２４ａ、２４ｂは、上記複列に配置された玉８ａ、８ｂの公転速度を測定する為のもので、上記検出部２３のうち、上記ハブ１ｂの軸方向（図１〜２の左右方向）に関する両側面に、それぞれの検出面を配置している。本例の場合、上記両公転速度検出センサ２４ａ、２４ｂは、上記複列に配置された各玉８ａ、８ｂの公転速度を、前記各保持器２１ａ、２１ｂの回転速度として検出する。この為に本例の場合には、これら各保持器２１ａ、２１ｂを構成するリム部２５、２５を、互いに対向する側に配置している。そして、これら各リム部２５、２５の互いに対向する面に、それぞれが円輪状である公転速度検出用エンコーダ２６ａ、２６ｂを、全周に亙り添着支持している。   These revolution speed detection sensors 24a and 24b are for measuring the revolution speed of the balls 8a and 8b arranged in the double row, and the axial direction of the hub 1b (see FIGS. 2 in the left and right directions), the respective detection surfaces are arranged. In the case of this example, the both revolution speed detection sensors 24a and 24b detect the revolution speeds of the balls 8a and 8b arranged in the double row as the rotation speeds of the cages 21a and 21b. For this reason, in the case of this example, the rim portions 25 and 25 constituting the retainers 21a and 21b are arranged on the sides facing each other. Then, revolving speed detection encoders 26a and 26b each having a ring shape are attached and supported on the surfaces of the rim portions 25 and 25 facing each other over the entire circumference.

これら両エンコーダ２６ａ、２６ｂの被検出面の磁気特性は、円周方向に関して交互に且つ等間隔で変化させて、上記各保持器２１ａ、２１ｂの回転速度を上記両公転速度検出センサ２４ａ、２４ｂにより検出自在としている。この為に本例の場合には、上記両エンコーダ２６ａ、２６ｂを、円輪状の永久磁石製としている。この様な永久磁石としては、フェライト磁石、ネオジウム鉄ボロン磁石、サマリウムコバルト磁石等の燒結磁石、アルミマンガン磁石、アルニコ等の金属磁石、磁性粉を合成樹脂或はゴム中に混入したプラスチック磁石或はゴム磁石を使用できる。このうちの燒結磁石及び金属磁石は、強い磁力を得られる反面、欠けや割れ等の損傷を生じ易い為、プラスチック磁石或はゴム磁石を使用する事が好ましい。この様な両公転速度検出用エンコーダ２６ａ、２６ｂは、別途造られた上記各保持器２１ａ、２１ｂのリム部２５、２５の側面に接着により結合固定したり、或はこれら各保持器２１ａ、２１ｂを射出時にキャビティ内に上記両公転速度検出用エンコーダ２６ａ、２６ｂをセットしておく事で、インサート成形する。何れの方法を採用するかは、コスト及び要求される結合強度等に応じて選択する。尚、図示は省略するが、製造個数がより多くなる様な場合には、保持器自体にエンコーダとしての機能を持たせる事も、コスト低減と信頼性向上との面から有効である。   The magnetic characteristics of the detected surfaces of both the encoders 26a and 26b are changed alternately and at equal intervals in the circumferential direction, and the rotational speeds of the cages 21a and 21b are changed by the revolution speed detection sensors 24a and 24b. Detectable. Therefore, in the case of this example, both the encoders 26a and 26b are made of an annular permanent magnet. Such permanent magnets include ferrite magnets, neodymium iron boron magnets, sintered magnets such as samarium cobalt magnets, metal magnets such as aluminum manganese magnets and alnico, plastic magnets in which magnetic powder is mixed in synthetic resin or rubber, or Rubber magnets can be used. Among these, the sintered magnet and the metal magnet can obtain a strong magnetic force, but are liable to cause damage such as chipping and cracking. Therefore, it is preferable to use a plastic magnet or a rubber magnet. Such revolving speed detection encoders 26a and 26b are bonded and fixed to the side surfaces of the rim portions 25 and 25 of the respective holders 21a and 21b separately manufactured, or these holders 21a and 21b. At the time of injection, insert molding is performed by setting the above-mentioned revolving speed detecting encoders 26a and 26b in the cavity. Which method is adopted is selected according to the cost, the required bond strength, and the like. Although illustration is omitted, it is also effective from the viewpoint of cost reduction and reliability improvement that the cage itself has a function as an encoder when the number of manufactured products is increased.

上述の様な両エンコーダ２６ａ、２６ｂ或はエンコーダとして機能する保持器を介して前記各列の玉８ａ、８ｂの公転速度を検出する為に、上記両公転速度検出センサ２４ａ、２４ｂの検出面を、上記両公転速度検出用エンコーダ２６ａ、２６ｂの被検出面である、互いに対向する面に近接対向させている。尚、これら両公転速度検出用エンコーダ２６ａ、２６ｂの被検出面と上記両公転速度検出センサ２４ａ、２４ｂの検出面との距離（検出隙間）は、上記各保持器２１ａ、２１ｂのポケットの内面と上記各玉８ａ、８ｂの転動面との間の隙間であるポケット隙間よりも大きく、２mm以下とする事が好ましい。上記検出隙間がポケット隙間以下になると、上記各保持器２１ａ、２１ｂがこのポケット隙間分変位した場合に、上記被検出面と上記検出面とが擦れ合う可能性を生じる為、好ましくない。反対に、上記検出隙間が２mmを越えると、上記両公転速度検出センサ２４ａ、２４ｂにより上記両公転速度検出用エンコーダ２６ａ、２６ｂの回転を正確に測定する事が難しくなる。   In order to detect the revolution speeds of the balls 8a and 8b in each row through both the encoders 26a and 26b or the cage functioning as an encoder as described above, the detection surfaces of the both revolution speed detection sensors 24a and 24b are used. The two revolution speed detection encoders 26a and 26b are close to each other and are opposed to each other, which are the detection surfaces. The distance (detection gap) between the detected surfaces of the two revolution speed detection encoders 26a and 26b and the detection surfaces of the two revolution speed detection sensors 24a and 24b is the distance between the inner surfaces of the pockets of the cages 21a and 21b. It is preferably larger than the pocket gap which is a gap between the balls 8a and 8b and 2 mm or less. If the detection gap is equal to or less than the pocket gap, it is not preferable because the detected surface and the detection surface may rub against each other when the cages 21a and 21b are displaced by the pocket gap. On the contrary, if the detection gap exceeds 2 mm, it becomes difficult to accurately measure the rotations of the revolution speed detection encoders 26a and 26b by the revolution speed detection sensors 24a and 24b.

又、上記両公転速度検出センサ２４ａ、２４ｂは、磁気式の回転検出センサで、ホール素子、ホールＩＣ、磁気抵抗素子（ＭＲ素子）、ＧＭＲ素子、ＭＩ素子等の磁気検出素子を組み込んだアクティブ型のものが、好ましく使用できる。この様な磁気検出素子を組み込んだアクティブ型の回転検出センサを構成するには、例えば、この磁気検出素子の一側面を、直接又は磁性材製のステータを介して永久磁石の着磁方向一端面に突き当て（磁性材製のエンコーダを使用する場合）、上記磁気検出素子の他側面を、直接又は磁性材製のステータを介して、上記両エンコーダ２６ａ、２６ｂの被検出面に対向させる。尚、本例の場合、永久磁石製のエンコーダを使用するので、センサ側の永久磁石は不要である。   The revolving speed detection sensors 24a and 24b are magnetic rotation detection sensors, and are active types incorporating magnetic detection elements such as Hall elements, Hall ICs, magnetoresistive elements (MR elements), GMR elements, and MI elements. Can be preferably used. In order to configure an active type rotation detection sensor incorporating such a magnetic detection element, for example, one side surface of this magnetic detection element is directly or via one end surface in the magnetization direction of a permanent magnet through a stator made of a magnetic material. (When an encoder made of a magnetic material is used), the other side of the magnetic detection element is made to face the detected surfaces of the encoders 26a and 26b directly or via a stator made of a magnetic material. In this example, since a permanent magnet encoder is used, a permanent magnet on the sensor side is unnecessary.

更に、前記センサユニット２２の先端部（図１〜２の下端部）で、上記両公転速度検出センサ２４ａ、２４ｂ同士の間部分に、磁性材２７を設置している。言い換えれば、これら両公転速度検出センサ２４ａ、２４ｂは、この磁性材２７をサンドイッチ状に挟んだ状態で配置されている。この磁性材２７としては、ＳＳ材、ＳＰＣＣ材、マルテンサイト系ステンレス材、フェライト系ステンレス材等の鉄系金属材料の他、合成樹脂、ゴム、塗料、接着剤等の非磁性材料、弾性材料に磁性粉を混入して磁性を持たせたもの等、各種材料が利用可能である。この様な磁性材２７は、上記両公転速度検出センサ２４ａ、２４ｂを支持する為の構造用部材として上記センサユニット２２に組み込む事もできるし、これら両公転速度検出センサ２４ａ、２４ｂの背面（上記両エンコーダ２６ａ、２６ｂと反対側の面）に塗布、貼着、添着して設置する事もできる。   Furthermore, the magnetic material 27 is installed in the front-end | tip part (lower end part of FIGS. 1-2) of the said sensor unit 22 in the part between both said revolution speed detection sensors 24a and 24b. In other words, the two revolution speed detection sensors 24a and 24b are arranged in a state where the magnetic material 27 is sandwiched. As the magnetic material 27, in addition to ferrous metal materials such as SS material, SPCC material, martensitic stainless material, and ferritic stainless material, nonmagnetic materials such as synthetic resin, rubber, paint, and adhesive, and elastic materials can be used. Various materials can be used, such as those made magnetic by mixing magnetic powder. Such a magnetic material 27 can be incorporated into the sensor unit 22 as a structural member for supporting the two revolution speed detection sensors 24a and 24b, and the back surfaces of the two revolution speed detection sensors 24a and 24b (see above). It can also be installed by applying, sticking, or attaching to the surface opposite to both the encoders 26a, 26b.

本例の転がり軸受ユニットの荷重測定装置の場合、上記両公転速度検出センサ２４ａ、２４ｂの検出信号は、図示しない演算器に入力する。そして、この演算器が、これら両公転速度検出センサ２４ａ、２４ｂから送り込まれる検出信号に基づいて、前記外輪４ａと前記ハブ１ｂとの間に加わるアキシアル荷重又はラジアルを算出する。このうちのアキシアル荷重を求める場合に上記演算器は、上記両公転速度検出センサ２４ａ、２４ｂの検出信号から求められる、前記両列の玉８ａ、８ｂの公転速度の差から上記アキシアル荷重を求める。又、ラジアル荷重に関しては、上記両列の玉８ａ、８ｂの公転速度の和に基づいて算出する。尚、上記公転速度の差と上記アキシアル荷重との関係、或はこの公転速度の和と上記ラジアル荷重との関係は、予め実験及び計算により求めて、上記演算器のメモリに記憶させておく。何れにしても、上記両列の玉８ａ、８ｂの公転速度に基づいて、上記アキシアル荷重或はラジアル荷重を求める事により、これら両列の玉８ａ、８ｂに付与されている予圧の影響を少なく抑えて、上記アキシアル荷重或はラジアル荷重を精度良く求められる。   In the case of the load measuring device of the rolling bearing unit of this example, the detection signals of the two revolution speed detection sensors 24a and 24b are input to a calculator (not shown). And this calculator calculates the axial load or radial applied between the said outer ring | wheel 4a and the said hub 1b based on the detection signal sent from both these revolution speed detection sensors 24a and 24b. When the axial load is obtained, the computing unit obtains the axial load from the difference between the revolution speeds of the balls 8a and 8b in the two rows obtained from the detection signals of the revolution speed detection sensors 24a and 24b. The radial load is calculated based on the sum of the revolution speeds of the balls 8a and 8b in both rows. The relationship between the difference in revolution speed and the axial load, or the relation between the sum of revolution speeds and the radial load is obtained in advance by experiments and calculations and stored in the memory of the arithmetic unit. In any case, by determining the axial load or radial load based on the revolution speed of the balls 8a and 8b in both rows, the influence of the preload applied to the balls 8a and 8b in both rows is reduced. Therefore, the axial load or radial load can be obtained with high accuracy.

特に、本実施例の場合には、近接配置された上記両公転速度検出センサ２４ａ、２４ｂ同士の間に前記磁性材２７を配置しているので、これら両公転速度検出センサ２４ａ、２４ｂ同士の間で磁束の干渉を生じにくくして、公転速度検出の信頼性を向上させる事ができる。この点に就いて、図３を参照しつつ説明する。
互いの被検出面を対向させて配置された前記１対のエンコーダ２６ａ、２６ｂの被検出面から出る磁束は、上記磁性材２７が存在する場合には、この磁性材２７により遮られて、図３（Ａ）に示す様に、それ以上遠くにまで達する事はない。従って、上記両エンコーダ２６ａ、２６ｂのうちの一方のエンコーダ２６ａの被検出面から出た磁束は、上記両公転速度検出センサ２４ａ、２４ｂのうちの一方の回転検出センサ２４ａの検出部のみ通過する。又、他方のエンコーダ２６ｂの被検出面から出た磁束は、他方の回転検出センサ２４ｂの検出部のみ通過する。従って、これら両公転速度検出センサ２４ａ、２４ｂは、それぞれの検出部が対向したエンコーダ２６ａ、２６ｂを介して、上記両列の玉８ａ、８ｂの公転速度を正確に表す信号を出力する。 In particular, in the case of the present embodiment, the magnetic material 27 is disposed between the two revolution speed detection sensors 24a and 24b that are disposed in proximity to each other, and therefore, between the two revolution speed detection sensors 24a and 24b. Therefore, it is possible to improve the reliability of revolution speed detection by making it difficult for magnetic flux interference to occur. This point will be described with reference to FIG.
When the magnetic material 27 is present, the magnetic flux emitted from the detected surfaces of the pair of encoders 26a and 26b arranged with the detected surfaces facing each other is blocked by the magnetic material 27. As shown in 3 (A), it does not reach further. Accordingly, the magnetic flux emitted from the detected surface of one of the encoders 26a and 26b passes only the detection part of one of the rotation speed detection sensors 24a and 24b. Further, the magnetic flux emitted from the detected surface of the other encoder 26b passes only through the detection portion of the other rotation detection sensor 24b. Therefore, both the revolution speed detection sensors 24a and 24b output signals that accurately represent the revolution speeds of the balls 8a and 8b in both rows through the encoders 26a and 26b opposed to the respective detection units.

これに対して、上記両公転速度検出センサ２４ａ、２４ｂ同士の間に磁性材が存在しないと、図３（Ｂ）に示す様に、１対のエンコーダ２６ａ、２６ｂの被検出面から出る磁束が、それぞれに対向した公転速度検出センサ２４ａ、２４ｂの検出部だけでなく、他の公転速度検出センサ２４ａ、２４ｂの検出部にまで達する可能性を生じる。この様に、これら公転速度検出センサ２４ａ、２４ｂの検出部に、上記両エンコーダ２６ａ、２６ｂの被検出面から出る磁束が達すると、これら公転速度検出センサ２４ａ、２４ｂから出る信号が、上記両列の玉８ａ、８ｂの公転速度を正確に表さなくなる。本実施例の場合、この様な問題をなくして、上記両列の玉８ａ、８ｂの公転速度を正確に求められる。   On the other hand, if there is no magnetic material between the two revolution speed detection sensors 24a and 24b, as shown in FIG. 3B, the magnetic flux emitted from the detected surfaces of the pair of encoders 26a and 26b. There is a possibility that not only the detection units of the revolution speed detection sensors 24a and 24b facing each other but also the detection units of the other revolution speed detection sensors 24a and 24b may be reached. In this way, when the magnetic flux from the detection surfaces of the encoders 26a and 26b reaches the detection portions of the revolution speed detection sensors 24a and 24b, the signals output from the revolution speed detection sensors 24a and 24b The revolution speed of the balls 8a and 8b is not accurately represented. In the case of the present embodiment, such a problem is eliminated and the revolution speeds of the balls 8a and 8b in both rows can be accurately obtained.

図４は、本発明の実施例２を示している。本実施例の場合、センサユニット２２ａのホルダ２８の先端面（図４の下端面）に基板２９を固定し、更にこの基板２９に１対の公転速度検出センサ２４ａ、２４ｂを支持して、リード型のセンサユニット２２ａを構成している。又、これら両公転速度検出センサ２４ａ、２４ｂ同士の間に、磁性材２７ａを設けている。上記基板２９は、これら両公転速度検出センサ２４ａ、２４ｂ毎に独立させる他、共通の一体型として良い。その他の構成及び作用は、上述した実施例１と同様である為、重複する説明は省略する。   FIG. 4 shows a second embodiment of the present invention. In the case of this embodiment, a substrate 29 is fixed to the tip surface (lower end surface in FIG. 4) of the holder 28 of the sensor unit 22a, and a pair of revolution speed detection sensors 24a and 24b are supported on the substrate 29 to A mold type sensor unit 22a is configured. A magnetic material 27a is provided between the two revolution speed detection sensors 24a and 24b. The substrate 29 may be independent of each of the revolution speed detection sensors 24a and 24b, or may be a common integrated type. Other configurations and operations are the same as those of the first embodiment described above, and thus redundant description is omitted.

図５は、本発明の実施例３を示している。本実施例の場合には、センサユニット２２ｂの先端面に回転速度検出センサ２０ａを設けると共に、ハブ１ｂの中間部で１対の内輪軌道３、３の間部分に、回転速度検出用のセンサロータ１８ａを外嵌固定している。このセンサロータ１８ａの外周面の磁気特性は、円周方向に関して交互に且つ等間隔で変化している。上記回転速度検出センサ２０ａは上記ハブ１ｂの回転速度を測定する為のもので、その検出面は、上記センサロータ１８ａの外周面に対向している。このセンサロータ１８ａの外周面と上記回転速度検出センサ２０ａの検出面との間の測定隙間は２mm以下に抑えている。   FIG. 5 shows a third embodiment of the present invention. In the case of the present embodiment, a rotational speed detection sensor 20a is provided on the tip surface of the sensor unit 22b, and a rotational speed detection sensor rotor is provided between the pair of inner ring raceways 3 and 3 in the middle of the hub 1b. The outer fitting 18a is fixed. The magnetic characteristics of the outer peripheral surface of the sensor rotor 18a change alternately and at equal intervals in the circumferential direction. The rotational speed detection sensor 20a is for measuring the rotational speed of the hub 1b, and its detection surface faces the outer peripheral surface of the sensor rotor 18a. The measurement gap between the outer peripheral surface of the sensor rotor 18a and the detection surface of the rotational speed detection sensor 20a is suppressed to 2 mm or less.

本例の場合、上記センサユニット２２ｂに、１対の公転速度検出センサ２４ａ、２４ｂに加えて上記回転速度検出センサ２０ａを設ける事により、上記ハブ１ｂの回転速度の変動に拘らず、転がり軸受ユニットに加わるアキシアル荷重或はラジアル荷重を精度良く求められる。即ち、前述した通り、このアキシアル荷重は両列の玉８ａ、８ｂの公転速度の差に基づいて、ラジアル荷重はこれら両列の玉８ａ、８ｂの公転速度の和に基づいて、それぞれ算出するが、各荷重が同じであっても、上記差或は和は、上記ハブ１ｂの回転速度に応じて変化する。従って、工作機械や産業機械の回転支持部に設置する転がり軸受ユニットの様に、使用時の回転速度が一定であれば、１対の公転速度検出センサ２４ａ、２４ｂのみでも、上記アキシアル荷重或はラジアル荷重を必要とする精度を確保しつつ求める事は可能である。これに対して、自動車或は鉄道車両の車輪を支持する為の転がり軸受ユニットの様に、使用時の回転速度が常に変化する場合には、本実施例の様に、上記両列の玉８ａ、８ｂの公転速度に加えて、上記ハブ１ｂの回転速度を求める必要がある。   In the case of this example, by providing the sensor unit 22b with the rotational speed detection sensor 20a in addition to a pair of revolution speed detection sensors 24a and 24b, a rolling bearing unit regardless of fluctuations in the rotational speed of the hub 1b. The axial load or the radial load applied to the can be obtained with high accuracy. That is, as described above, the axial load is calculated based on the difference between the revolution speeds of the balls 8a and 8b in both rows, and the radial load is calculated based on the sum of the revolution speeds of the balls 8a and 8b in both rows. Even if the loads are the same, the difference or sum changes according to the rotational speed of the hub 1b. Accordingly, if the rotational speed at the time of use is constant, such as a rolling bearing unit installed on a rotation support part of a machine tool or industrial machine, the axial load or the above-described axial load or only by a pair of revolution speed detection sensors 24a and 24b. It is possible to obtain it while ensuring the accuracy that requires a radial load. On the other hand, when the rotational speed at the time of use always changes like a rolling bearing unit for supporting the wheel of an automobile or a railway vehicle, the balls 8a in both rows as in the present embodiment. In addition to the revolution speed of 8b, it is necessary to determine the rotational speed of the hub 1b.

具体的には、本例の場合に演算器は、アキシアル荷重を求める場合には、上記各センサ２４ａ、２４ｂ、２０ａの検出信号に基づいて、上記両列の玉８ａ、８ｂの公転速度の差と上記ハブ１ｂの回転速度との比である速度比を算出する。そして、この速度比から、上記アキシアル荷重を求める。
又、ラジアル荷重を求める場合には、上記両列の玉８ａ、８ｂの公転速度の和と上記ハブ１ｂの回転速度との比である速度比を算出する。そして、この速度比から上記ラジアル荷重を求める。
この様にすれば、上記ハブ１ｂの回転速度が変化しても、上記アキシアル荷重或は上記ラジアル荷重を正確に求める事ができる。 Specifically, in the case of this example, when the arithmetic unit obtains the axial load, based on the detection signals of the sensors 24a, 24b, and 20a, the difference between the revolution speeds of the balls 8a and 8b in both rows is calculated. And a speed ratio which is a ratio of the rotational speed of the hub 1b. And the said axial load is calculated | required from this speed ratio.
Further, when the radial load is obtained, a speed ratio that is a ratio between the sum of the revolution speeds of the balls 8a and 8b in both rows and the rotational speed of the hub 1b is calculated. And the said radial load is calculated | required from this speed ratio.
In this way, even if the rotational speed of the hub 1b changes, the axial load or the radial load can be obtained accurately.

本発明は、図示の実施例に示す様な、複列アンギュラ型の転がり軸受ユニットに限らず、一般的な複列若しくは多列の玉軸受や円すいころ軸受に適用する事もできる。又、自動車の車輪を支持する為の複列アンギュラ型の転がり軸受ユニットに適用する場合にしても、図示の様な、外側の内輪軌道をハブ本体の中間部外周面に形成した、所謂第三世代のハブユニットに限らずに実施できる。即ち、ハブ本体の中間部乃至内端部に１対の内輪を外嵌固定した、所謂第二世代のハブユニットや、ハブ本体の中間部乃至内端部に１対の内輪を外嵌固定すると共に、外周面を単なる円筒状とした外輪をナックルの支持孔に内嵌支持する、所謂第一世代のハブユニットにも適用できる。或は、ハブ本体の中間部乃至内端部の外周面とナックルの支持孔の内周面との間に、それぞれが単列型である転がり軸受を１対設けて複列転がり軸受ユニットとする構造にも、本発明を適用する事ができる。勿論、駆動輪用のハブユニットに本発明を適用する事もできる。更には、各種工作機械、産業機械等の回転軸を支持する為の複列転がり軸受ユニットで本発明を実施する事もできる。   The present invention is not limited to a double-row angular type rolling bearing unit as shown in the illustrated embodiment, and can be applied to a general double-row or multi-row ball bearing or tapered roller bearing. Further, even when applied to a double-row angular type rolling bearing unit for supporting the wheels of an automobile, a so-called third type in which an outer inner ring raceway is formed on the outer peripheral surface of the intermediate part of the hub body as shown in the figure. This is not limited to the generation hub unit. That is, a so-called second-generation hub unit in which a pair of inner rings are fitted and fixed to an intermediate portion or an inner end portion of the hub body, or a pair of inner rings is fitted and fixed to an intermediate portion or an inner end portion of the hub body. In addition, the present invention can also be applied to a so-called first-generation hub unit in which an outer ring whose outer peripheral surface is simply cylindrical is fitted and supported in a knuckle support hole. Alternatively, a pair of single-row rolling bearings are provided between the outer peripheral surface of the intermediate portion or inner end portion of the hub body and the inner peripheral surface of the support hole of the knuckle to form a double-row rolling bearing unit. The present invention can also be applied to the structure. Of course, the present invention can also be applied to a hub unit for driving wheels. Furthermore, the present invention can be implemented with a double-row rolling bearing unit for supporting a rotating shaft of various machine tools, industrial machines, and the like.

本発明の実施例１を示す断面図。Sectional drawing which shows Example 1 of this invention. 図１のＡ部拡大図。The A section enlarged view of FIG. １対の公転速度検出センサ同士の間に磁性材を設ける場合と設けない場合とで磁束の流れに違いが生じる状態を説明する為の、図２と同様の図。The same figure as FIG. 2 for demonstrating the state in which a difference arises in the flow of magnetic flux between the case where a magnetic material is provided between a pair of revolution speed detection sensors, and the case where it does not provide. 本発明の実施例２を示す、図２と同様の図。The figure similar to FIG. 2 which shows Example 2 of this invention. 本発明の実施例３を示す断面図。Sectional drawing which shows Example 3 of this invention. 従来構造の第１例を示す断面図。Sectional drawing which shows the 1st example of a conventional structure. 同第２例を示す断面図。Sectional drawing which shows the 2nd example.

符号の説明Explanation of symbols

１、１ａ、１ｂ ハブ
２、２ａ 回転側フランジ
３ 内輪軌道
４、４ａ 外輪
５ ナックル
６ 固定側フランジ
７ 外輪軌道
８、８ａ、８ｂ 玉
９ ボルト
１０ ねじ孔
１１ 荷重センサ
１２ ハブ本体
１３ ナット
１４ 内輪
１５、１５ａ 取付孔
１６ 変位センサ
１７ センサリング
１８、１８ａ センサロータ
１９ カバー
２０、２０ａ 回転速度検出センサ
２１ａ、２１ｂ 保持器
２２、２２ａ、２２ｂ センサニット
２３ 検出部
２４ａ、２４ｂ 公転速度検出センサ
２５ リム部
２６ａ、２６ｂ 公転速度検出用エンコーダ
２７、２７ａ 磁性材
２８ ホルダ
２９ 基板
1, 1a, 1b Hub 2, 2a Rotation side flange 3 Inner ring raceway 4, 4a Outer ring 5 Knuckle 6 Fixed side flange 7 Outer ring raceway 8, 8a, 8b Ball 9 Bolt 10 Screw hole 11 Load sensor 12 Hub body 13 Nut 14 Inner ring 15 , 15a Mounting hole 16 Displacement sensor 17 Sensor ring 18, 18a Sensor rotor 19 Cover 20, 20a Rotational speed detection sensor 21a, 21b Cage 22, 22a, 22b Sensor knit 23 Detection part 24a, 24b Revolution speed detection sensor 25 Rim part 26a , 26b Revolution speed detection encoder 27, 27a Magnetic material 28 Holder 29 Substrate

Claims (8)

使用時にも回転しない静止輪と、この静止輪と同心に配置されて使用時に回転する回転輪と、これら静止輪と回転輪との互いに対向する部分にそれぞれ２列ずつ形成された静止側軌道と回転側軌道との間にそれぞれ複数個ずつ、接触角の方向を互いに逆にして転動自在に設けられた転動体と、両列の転動体同士の間に設けられて、これら両列の転動体の公転速度をそれぞれ円周方向に関する磁気特性の変化に基づいて検出する為の１対の公転速度検出センサと、上記静止輪の軸方向に関して、これら両公転速度検出センサ同士の間に配置された磁性体とを備えた、荷重測定用転がり軸受ユニット。   A stationary wheel that does not rotate even when in use, a rotating wheel that is arranged concentrically with the stationary wheel and that rotates when in use, and a stationary side track that is formed in two rows on opposite portions of the stationary wheel and the rotating wheel. A plurality of rolling elements provided between the rotating side raceways and the rolling elements provided so as to be able to roll with the contact angle directions being opposite to each other and between the rolling elements of both rows are provided. A pair of revolution speed detection sensors for detecting the revolution speed of the moving body based on the change in magnetic characteristics in the circumferential direction, and the revolution speed detection sensors arranged between the two revolution speed detection sensors in the axial direction of the stationary wheel. A rolling bearing unit for load measurement, comprising a magnetic material. 静止輪と回転輪とのうちの一方の軌道輪が外輪相当部材であり、他方の軌道輪が内輪相当部材であり、各転動体が玉であり、この内輪相当部材の外周面に形成された複列アンギュラ型の内輪軌道と上記外輪相当部材の内周面に形成された複列アンギュラ型の外輪軌道との間にそれぞれ複数個ずつ設けられた玉に、背面組み合わせ型の接触角が付与されている、請求項１に記載した荷重測定用転がり軸受ユニット。   One of the stationary ring and the rotating ring is an outer ring equivalent member, the other race ring is an inner ring equivalent member, each rolling element is a ball, and is formed on the outer peripheral surface of the inner ring equivalent member. A contact angle of the back combination type is given to a plurality of balls provided between the double row angular type inner ring raceway and the double row angular type outer ring raceway formed on the inner peripheral surface of the outer ring equivalent member. The load-measuring rolling bearing unit according to claim 1. 各列の転動体が磁性材製で、これら各転動体が、１対の保持器に円周方向に関して等間隔に設けられたポケット内に保持されており、両公転速度検出センサの検出部が上記各転動体に対向している、請求項１〜２の何れかに記載した荷重測定用転がり軸受ユニット。   The rolling elements in each row are made of a magnetic material, and each of these rolling elements is held in a pair of cages that are provided at equal intervals in the circumferential direction. The rolling bearing unit for load measurement according to claim 1, which faces each of the rolling elements. 各列の転動体を保持した１対の保持器の互いに対向する側面に、互いに対向する側面の磁気特性を円周方向に関して等間隔に変化させたエンコーダが、上記両保持器と同心に支持されており、両公転速度検出センサの検出部がこれら両エンコーダの互いに対向する側面に対向している、請求項１〜２の何れかに記載した荷重測定用転がり軸受ユニット。   Encoders that change the magnetic properties of the opposing side surfaces at equal intervals in the circumferential direction are supported concentrically with the side surfaces of the pair of cages holding the rolling elements of each row. The load measuring rolling bearing unit according to claim 1, wherein the detection portions of the two revolution speed detection sensors are opposed to the mutually opposing side surfaces of the two encoders. 各列の転動体を保持した１対の保持器が、合成樹脂中に磁性粉末を混入して軸方向に着磁されたプラスチック磁石製で、着磁方向が円周方向に関して交互に且つ等間隔で変化しており、両公転速度検出センサの検出部が上記両保持器の互いに対向する側面に対向している、請求項１〜２の何れかに記載した荷重測定用転がり軸受ユニット。   A pair of cages holding rolling elements in each row is made of a plastic magnet mixed with magnetic powder in a synthetic resin and magnetized in the axial direction, and the magnetization directions are alternately and equally spaced in the circumferential direction. The rolling bearing unit for load measurement according to any one of claims 1 to 2, wherein the detection portions of both revolution speed detection sensors face opposite side surfaces of the two cages. 両公転速度検出センサから送り込まれる検出信号に基づいて、静止輪と回転輪との間に加わるアキシアル荷重とラジアル荷重とのうちの少なくとも一方の荷重を算出する演算器を備えた、請求項１〜５の何れかに記載した荷重測定用転がり軸受ユニット。   An arithmetic unit for calculating at least one of an axial load and a radial load applied between the stationary wheel and the rotating wheel based on a detection signal sent from both revolution speed detection sensors. The rolling bearing unit for load measurement described in any one of 5. 回転輪の回転速度を検出する為の回転速度検出センサを備えた、請求項１〜６の何れかに記載した荷重測定用転がり軸受ユニット。   The rolling bearing unit for load measurement according to any one of claims 1 to 6, comprising a rotation speed detection sensor for detecting the rotation speed of the rotating wheel. 両公転速度検出センサから送り込まれる検出信号と、回転速度検出センサから送り込まれる検出信号とに基づいて、静止輪と回転輪との間に加わるアキシアル荷重とラジアル荷重とのうちの少なくとも一方の荷重を算出する演算器を備えた、請求項７に記載した荷重測定用転がり軸受ユニット。
Based on a detection signal sent from both revolution speed detection sensors and a detection signal sent from the rotation speed detection sensor, at least one of an axial load and a radial load applied between the stationary wheel and the rotation wheel is determined. The rolling bearing unit for load measurement according to claim 7, comprising a calculator for calculating.
JP2003288475A 2003-08-07 2003-08-07 Ball bearing unit for load measurement Pending JP2005055379A (en)

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPWO2007058351A1 (en) * 2005-11-18 2009-05-07 日本精工株式会社 Resin cage and rolling bearing
JP2010518339A (en) * 2007-02-14 2010-05-27 シャエフラー カーゲー Rolling bearing device with integrated sensor system
CN114776715A (en) * 2022-04-21 2022-07-22 洛阳轴承研究所有限公司 Spacer assembly and bearing assembly

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPWO2007058351A1 (en) * 2005-11-18 2009-05-07 日本精工株式会社 Resin cage and rolling bearing
JP4766051B2 (en) * 2005-11-18 2011-09-07 日本精工株式会社 Resin cage and rolling bearing
US8303192B2 (en) 2005-11-18 2012-11-06 Nsk Ltd. Resin cage and rolling bearing
JP2010518339A (en) * 2007-02-14 2010-05-27 シャエフラー カーゲー Rolling bearing device with integrated sensor system
CN114776715A (en) * 2022-04-21 2022-07-22 洛阳轴承研究所有限公司 Spacer assembly and bearing assembly

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