JP4658028B2 - Manufacturing method of wheel bearing device - Google Patents

Manufacturing method of wheel bearing device Download PDF

Info

Publication number
JP4658028B2
JP4658028B2 JP2006340054A JP2006340054A JP4658028B2 JP 4658028 B2 JP4658028 B2 JP 4658028B2 JP 2006340054 A JP2006340054 A JP 2006340054A JP 2006340054 A JP2006340054 A JP 2006340054A JP 4658028 B2 JP4658028 B2 JP 4658028B2
Authority
JP
Japan
Prior art keywords
inner ring
press
axial movement
outer member
inner member
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
JP2006340054A
Other languages
Japanese (ja)
Other versions
JP2007085553A (en
Inventor
基晴 仁木
英児 田島
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
NTN Corp
Original Assignee
NTN Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by NTN Corp filed Critical NTN Corp
Priority to JP2006340054A priority Critical patent/JP4658028B2/en
Publication of JP2007085553A publication Critical patent/JP2007085553A/en
Application granted granted Critical
Publication of JP4658028B2 publication Critical patent/JP4658028B2/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C43/00—Assembling bearings
    • F16C43/04—Assembling rolling-contact bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/063—Fixing them on the shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
    • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
    • F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
    • F16C19/184—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement
    • F16C19/185—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement with two raceways provided integrally on a part other than a race ring, e.g. a shaft or housing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—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
    • F16C2229/00—Setting preload
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2326/00—Articles relating to transporting
    • F16C2326/01—Parts of vehicles in general
    • F16C2326/02—Wheel hubs or castors

Landscapes

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

Description

本発明は車輪軸受装置の製造方法に関し、詳しくは、自動車に用いられ、軸受剛性の向上を図り得る車輪軸受装置の製造方法に関する。 The present invention relates to a method of manufacturing a wheel bearing device, particularly, used in an automobile, a method of manufacturing a wheel bearing device for obtaining aims to improve the bearing rigidity.

図４は自動車に用いられる車輪軸受装置の一例で、従動輪用として用いた場合の構造を示す。この軸受装置は、ハブ輪１を車軸軸受２によって回転自在に支持した構造を有し、そのハブ輪１に車輪ホイールが固定され、車軸軸受２をナックル３を介して車体の懸架装置によって支持する（例えば、特許文献１参照）。   FIG. 4 shows an example of a wheel bearing device used in an automobile, and shows a structure when used for a driven wheel. This bearing device has a structure in which a hub wheel 1 is rotatably supported by an axle bearing 2, a wheel wheel is fixed to the hub wheel 1, and the axle bearing 2 is supported by a vehicle body suspension device via a knuckle 3. (For example, refer to Patent Document 1).

車軸軸受２は、複列転がり軸受であって、内径面に複列の軌道面４，５が形成された外輪６と、外径面に軌道面７，８が形成された内輪９，１０と、外輪６と内輪９，１０との間に介在させた複列の転動体１１と、各列の転動体１１を円周方向等間隔に支持する保持器１２とで構成される。   The axle bearing 2 is a double-row rolling bearing, and includes an outer ring 6 in which double-row raceway surfaces 4 and 5 are formed on the inner diameter surface, and inner rings 9 and 10 in which raceway surfaces 7 and 8 are formed on the outer diameter surface. The double-row rolling elements 11 interposed between the outer ring 6 and the inner rings 9 and 10 and the cage 12 that supports the rolling elements 11 in each row at equal intervals in the circumferential direction.

外輪６はナックル３に圧入されて止め輪１３で固定されている。車軸軸受２に対して外部からの異物の侵入や内部に充填したグリースの漏出を防止するため、シール１４，１５が設けられている。図示の例では、車軸軸受２として複列アンギュラ玉軸受が使用されている。   The outer ring 6 is press-fitted into the knuckle 3 and fixed with a retaining ring 13. Seals 14 and 15 are provided to prevent intrusion of foreign matter from the outside and leakage of grease filled inside the axle bearing 2. In the illustrated example, a double-row angular ball bearing is used as the axle bearing 2.

ハブ輪１はフランジ１６を備え、このフランジ１６の円周方向等間隔位置に車輪ホイールを固定するためのハブボルト１７が取り付けられている。また、ハブ輪１のフランジ１６には、ブレーキロータ１８がハブボルト１７により固定されている。このハブ輪１の端部外径に前記車軸軸受２の内輪９，１０を圧入し、そのハブ輪１の突出する端部をナット１９で固定することにより組み付けられている。
特開平７−２７１３５号公報（図１、図４） The hub wheel 1 includes a flange 16, and hub bolts 17 for fixing the wheel wheels are attached to the flange 16 at equal circumferential positions. A brake rotor 18 is fixed to the flange 16 of the hub wheel 1 by a hub bolt 17. The hub ring 1 is assembled by press-fitting the inner rings 9 and 10 of the axle bearing 2 into the outer diameter of the end of the hub wheel 1 and fixing the protruding end of the hub wheel 1 with a nut 19.
JP-A-7-27135 (FIGS. 1 and 4)

ところで、前述した従来の車輪軸受装置では、車軸軸受２の外輪６を、外径が異形のナックル３に強タイトで圧入するため、外輪６の軌道面４，５が変形してしまうことがある。このような変形により、軸受のアキシャル振れ等が悪化し、ナックル３への圧入後、ハブ輪１のフランジ１６に取り付けられたブレーキロータ１８に軸方向振れ（又は面振れ）が生じて、自動車の高速走行からのブレーキ時の振動の原因となったり、ブレーキの偏摩耗の原因になったりする。   By the way, in the above-described conventional wheel bearing device, the outer ring 6 of the axle bearing 2 is pressed tightly into the knuckle 3 having a different outer diameter, so that the raceway surfaces 4 and 5 of the outer ring 6 may be deformed. . Such deformation deteriorates axial runout of the bearing, and after press-fitting into the knuckle 3, axial runout (or runout) occurs in the brake rotor 18 attached to the flange 16 of the hub wheel 1. This may cause vibration during braking from high speed running or cause uneven wear of the brake.

また、高い予圧を付与して軸受剛性を高めることも考えられるが、ハブ輪１と一対の内輪９，１０間、外輪６とナックル３間といった嵌め合い部分があるため、嵌め合い公差の集積上、予圧のためのすきま減少量のばらつき範囲が大きくならざるを得ず、必ずしも十分な予圧を付与し得る構造ではなかった。   It is also conceivable to increase the bearing rigidity by applying a high preload. However, since there are fitting parts such as between the hub wheel 1 and the pair of inner rings 9 and 10 and between the outer ring 6 and the knuckle 3, the fitting tolerances are accumulated. However, the variation range of the clearance reduction amount for the preload has to be large, and the structure is not necessarily capable of providing a sufficient preload.

そこで、本発明は前述の問題点に鑑みて提案されたもので、その目的とするところは、軸受剛性を向上させることにより、ブレーキロータの軸方向振れを抑制し得る車輪軸受装置を提供することにある。   Therefore, the present invention has been proposed in view of the above-described problems, and an object of the present invention is to provide a wheel bearing device that can suppress axial deflection of the brake rotor by improving bearing rigidity. It is in.

前述の目的を達成するための技術的手段として、本発明に係る車輪軸受装置の製造方法は、内周に複列の軌道面を一体に設けた外方部材と、一端に車輪取付け用フランジ、他端に円筒状小径段部を設け、その小径段部に内輪を圧入して外方部材の軌道面に対向する複列の軌道面を形成した内方部材と、外方部材と内方部材の両軌道面間に介在する複列の転動体とを備え、内方部材の小径段部の端部を径方向外方に加締めることにより圧入した内輪を内方部材に固定した車輪軸受装置の製造方法において、内輪を内方部材に圧入するに際して、軸受すきまが正の状態で内輪の圧入を一旦止め、この状態での外方部材の軸方向移動量を測定し、その後、圧入を一旦止めた状態から内輪を内方部材の肩部あるいは内輪の小径端面に当接するまで圧入して内方部材の小径段部の端部を加締めた状態に至るまでの内輪の軸方向移動量を測定し、外方部材の軸方向移動量の測定値と内輪の軸方向移動量の測定値との差を負の軸受すきまとすることを特徴とする。 As a technical means for achieving the above-mentioned object, a manufacturing method of a wheel bearing device according to the present invention includes an outer member integrally provided with a double row raceway surface on an inner periphery, a wheel mounting flange at one end, An inner member in which a cylindrical small-diameter step is provided at the other end, and an inner ring is press-fitted into the small-diameter step to form a double-row raceway surface facing the raceway surface of the outer member, and the outer member and the inner member And a double row rolling element interposed between the two raceway surfaces, and a wheel bearing device in which an inner ring press-fitted by crimping an end portion of a small diameter step portion of the inner member radially outward is fixed to the inner member In this manufacturing method, when the inner ring is press-fitted into the inner member, the inner ring is temporarily stopped when the bearing clearance is positive, the axial movement of the outer member in this state is measured, and then the press-fitting is temporarily performed. Press-fit until the inner ring comes into contact with the shoulder of the inner member or the small-diameter end surface of the inner ring. Measure the amount of axial movement of the inner ring until the end of the small diameter step of the inner member is crimped, and measure the amount of axial movement of the outer member and the amount of axial movement of the inner ring The difference between the values is the negative bearing clearance.

本発明では、軸受すきまが正の状態で内輪の圧入を一旦止めた状態での外方部材の軸方向移動量の測定値と、圧入を一旦止めた状態から内輪を内方部材の肩部に当接するまで圧入して内方部材の小径段部の端部を加締めた状態に至るまでの内輪の軸方向移動量の測定値との差を負の軸受すきまとした点、あるいは、内輪を内方部材に圧入するに際して、軸受すきまが正の状態で内輪の圧入を一旦止め、この状態での外方部材の軸方向移動量を測定し、その後、圧入を一旦止めた状態から内輪を内方部材の肩部あるいは内輪の小径端面に当接するまで圧入して内方部材の小径段部の端部を加締めた状態に至るまでの内輪の軸方向移動量を測定し、外方部材の軸方向移動量の測定値と内輪の軸方向移動量の測定値との差を負の軸受すきまとする点で、軸受剛性を向上させることができ、その結果、ブレーキロータの軸方向振れを抑制することが容易となる。 In the present invention, the measured value of the amount of axial movement of the outer member when the inner ring is once stopped when the bearing clearance is positive, and the inner ring is moved to the shoulder of the inner member from the state where the press-fitting is temporarily stopped. The difference between the axial movement amount of the inner ring and the inner ring until the end of the small diameter step of the inner member is crimped until it comes into contact is the negative bearing clearance, or the inner ring When press-fitting into the inner member, the inner ring is temporarily stopped when the bearing clearance is positive, and the axial movement of the outer member in this state is measured. The amount of axial movement of the inner ring until the end of the small diameter step of the inner member is crimped by pressing until it contacts the shoulder of the outer member or the small diameter end surface of the inner ring is measured . point of the difference between the measured value of the axial movement of the measured values and the inner ring of the axial movement amount and negative bearing clearance , It is possible to improve the bearing rigidity. As a result, it becomes easy to suppress the runout axial brake rotor.

本発明によれば、軸受すきまが正の状態で内輪の圧入を一旦止めた状態での外方部材の軸方向移動量の測定値と、圧入を一旦止めた状態から内輪を内方部材の肩部に当接するまで圧入して内方部材の小径段部の端部を加締めた状態に至るまでの内輪の軸方向移動量の測定値との差を負の軸受すきまとした点、あるいは、内輪を内方部材に圧入するに際して、軸受すきまが正の状態で内輪の圧入を一旦止め、この状態での外方部材の軸方向移動量を測定し、その後、圧入を一旦止めた状態から内輪を内方部材の肩部あるいは内輪の小径端面に当接するまで圧入して内方部材の小径段部の端部を加締めた状態に至るまでの内輪の軸方向移動量を測定し、外方部材の軸方向移動量の測定値と内輪の軸方向移動量の測定値との差を負の軸受すきまとする点から、軸受剛性の向上が容易に図れ、内方部材の車輪取付け用フランジにブレーキロータを装着した場合、そのブレーキロータの軸方向振れを抑制することができる。その結果、車輪軸受装置全体の剛性を向上させることができる。 According to the present invention, the measured value of the axial movement amount of the outer member when the inner ring is temporarily stopped when the bearing clearance is positive, and the inner ring is moved to the shoulder of the inner member from the state where the press-fitting is temporarily stopped. The difference between the measured value of the axial movement of the inner ring until the end of the small diameter step of the inner member is crimped until it comes into contact with the inner part is the negative bearing clearance, or When the inner ring is press-fitted into the inner member, the inner ring is temporarily stopped when the bearing clearance is positive, and the amount of axial movement of the outer member in this state is measured. the measured axial movement of the inner ring up to the state caulked end of the cylindrical portion of the press-fit to the inner member until it abuts against the shoulder or the smaller-diameter end face of the inner ring of the inner member, the outer to the difference between the measured value of the measurement values of the axial movement and the inner ring of the axial movement amount of the member and the negative bearing clearance From the point, improved bearing stiffness is easily Hakare, when fitted with a brake rotor to the wheel mounting flange of the inner member, it is possible to suppress the axial runout direction of the brake rotor. As a result, the rigidity of the entire wheel bearing device can be improved.

本発明に係る車輪軸受装置の実施形態を以下に詳述する。   An embodiment of a wheel bearing device according to the present invention will be described in detail below.

図１に示す実施形態の車輪軸受装置は、内周に複列の軌道面２１，２２を一体に設け、外周に車体取付け用フランジ２３を一体に有する外方部材２４と、一端に車輪取付け用フランジ２５、他端に円筒状小径段部２６を設け、その小径段部２６の外径に内輪２７，２８を圧入して前記外方部材２４の軌道面２１，２２に対向する複列の軌道面２９，３０を形成した内方部材３１と、前記外方部材２４と内方部材３１のそれぞれの軌道面間に介在する複列の転動体３２と、内方部材３１と外方部材２４との間に介在し、複列の転動体３２を各列ごとに円周方向等間隔に支持する保持器３３とを具備する。   The wheel bearing device of the embodiment shown in FIG. 1 has an outer member 24 integrally provided with double-row raceway surfaces 21 and 22 on the inner periphery and a body mounting flange 23 on the outer periphery, and a wheel attachment on one end. A cylindrical small diameter step portion 26 is provided at the flange 25 and the other end, and inner rings 27 and 28 are press-fitted into the outer diameter of the small diameter step portion 26 so as to face the raceway surfaces 21 and 22 of the outer member 24. An inner member 31 having surfaces 29 and 30; a double row rolling element 32 interposed between the raceway surfaces of the outer member 24 and the inner member 31; the inner member 31 and the outer member 24; And a retainer 33 that supports the double-row rolling elements 32 at equal intervals in the circumferential direction.

内輪２７，２８と外方部材２４の両端には、外部からの異物の侵入や内部に充填したグリースの漏出を防止するためにシール３４を装着している。内方部材３１の車輪取付け用フランジ２５の円周方向等間隔位置に車輪ホイールを固定するためのハブボルト３５が取り付けられている。また、内方部材３１のフランジ２５には、ブレーキロータ３６がハブボルト３５により固定されている。さらに、外方部材２４の車体取付け用フランジ２３には、ナックル（図示せず）を介して車体の懸架装置が取り付けられている。   Seals 34 are attached to both ends of the inner rings 27, 28 and the outer member 24 in order to prevent entry of foreign matter from the outside and leakage of grease filled in the inside. Hub bolts 35 for fixing the wheel wheels are attached to the circumferentially equidistant positions in the circumferential direction of the wheel mounting flange 25 of the inner member 31. A brake rotor 36 is fixed to the flange 25 of the inner member 31 with a hub bolt 35. Furthermore, a vehicle body suspension device is attached to the vehicle body attachment flange 23 of the outer member 24 via a knuckle (not shown).

本発明は、前記実施形態以外にも、図２に示すような構造を有する実施形態も可能である。この実施形態の車輪軸受装置は、前記内方部材３１の軌道面２９，３０のうち、車輪取付け用フランジ側（アウトボード側）の軌道面２９を内方部材３１の外径に直接形成した構造を有する。その他の構造については、図１の実施形態と同様であるため、同一部分には同一参照符号を付して重複説明は省略する。   In addition to the above-described embodiment, the present invention may have an embodiment having a structure as shown in FIG. The wheel bearing device according to this embodiment has a structure in which, of the raceway surfaces 29 and 30 of the inner member 31, the raceway surface 29 on the wheel mounting flange side (outboard side) is directly formed on the outer diameter of the inner member 31. Have Since the other structure is the same as that of the embodiment of FIG. 1, the same reference numerals are given to the same parts, and the duplicate description is omitted.

これらの実施形態では、軸受構造が、外方部材２４の軌道面２１，２２及び内方部材３１の軌道面２９，３０と転動体３２とが接触角を有する複列アンギュラ玉軸受構造であるために軸受負荷容量が大きい。他の軸受構造として、転動体に円すいころを使用した複列円すいころ軸受構造を採用することも可能である。   In these embodiments, the bearing structure is a double-row angular contact ball bearing structure in which the raceway surfaces 21 and 22 of the outer member 24 and the raceway surfaces 29 and 30 of the inner member 31 and the rolling elements 32 have contact angles. The bearing load capacity is large. As another bearing structure, it is also possible to adopt a double row tapered roller bearing structure in which tapered rollers are used as rolling elements.

前記内方部材３１の小径段部２６の端部を径方向外方に加締めることにより、その小径段部２６の外径に圧入された内輪２７，２８を内方部材３１に固定する。この内方部材３１の一端を加締めることにより、内輪２７，２８が内方部材３１の肩部３７との間に挟持されて軸方向で位置決めされ、軸受すきまが負に設定されて転動体３２に定められた予圧が付与された状態で内方部材３１に固定される。なお、内方部材３１の小径段部２６の端部を径方向外方に加締めることにより圧入した内輪２７，２８を内方部材３１に固定したことにより、装置全体の軽量、コンパクト化を実現することが容易になる。   The inner rings 27 and 28 press-fitted into the outer diameter of the small-diameter step portion 26 are fixed to the inner member 31 by caulking the end portion of the small-diameter step portion 26 of the inner member 31 radially outward. By crimping one end of the inner member 31, the inner rings 27, 28 are sandwiched between the inner member 31 and the shoulder portion 37 and positioned in the axial direction, and the bearing clearance is set to a negative value, so that the rolling element 32. It is fixed to the inner member 31 in a state where the preload determined in (1) is applied. In addition, the inner ring 27, 28 that has been press-fitted by crimping the end of the small-diameter step portion 26 of the inner member 31 radially outward is fixed to the inner member 31, thereby realizing a lighter and more compact device as a whole. Easy to do.

この加締めは、内輪２７，２８の内径に内方部材３１の小径段部２６を挿入し、インナー側に突出した内方部材３１の小径段部２６の端部外径を円筒状のポンチ等で加圧し、径方向外側に塑性変形させることにより行われる。この塑性変形によって形成された加締め部分３８は、図３に示すように内輪２８の内周面よりも外径側に突出し、かつ、円周方向の一部領域で連続した複数、例えば四つの第一領域３９と、隣接する第一領域３９間に形成され、第一領域３９よりも外径側に突出してその肉厚が第一領域３９よりも薄い第二領域４０とで構成される。   This caulking is performed by inserting the small-diameter step portion 26 of the inner member 31 into the inner diameter of the inner rings 27 and 28, and setting the outer diameter of the end portion of the small-diameter step portion 26 of the inner member 31 protruding to the inner side to a cylindrical punch or the like. By applying pressure and plastically deforming radially outward. As shown in FIG. 3, the caulking portion 38 formed by this plastic deformation protrudes to the outer diameter side from the inner peripheral surface of the inner ring 28 and is continuous in a partial region in the circumferential direction, for example, four A first region 39 and a second region 40 that is formed between adjacent first regions 39, protrudes to the outer diameter side from the first region 39, and is thinner than the first region 39.

この第一領域３９及び第二領域４０は、加圧面の四箇所に半径方向の突出部を設けた押し型を用いることによって一工程で同時成形することができる。この場合、突出部で第二領域４０が、突出部間の平面部分で第一領域３９がそれぞれ成形される。両領域３９，４０を同時に成形する他、両領域３９，４０を別工程で、例えば第一領域３９の成形後に第二領域４０を成形するようにしてもよい。   The first region 39 and the second region 40 can be simultaneously molded in one step by using a pressing die provided with radial protrusions at four locations on the pressing surface. In this case, the 2nd area | region 40 is shape | molded by the protrusion part, and the 1st area | region 39 is shape | molded by the plane part between protrusion parts, respectively. In addition to forming both regions 39 and 40 simultaneously, both regions 39 and 40 may be formed in separate steps, for example, after forming the first region 39, the second region 40 may be formed.

前記加締め部分３８のうち、主に第一領域３９は、内輪２８との間の隙間を充足して内輪２８のがたつきを防止し、第二領域４０は第一領域３９よりも大きな拘束力で内輪２８の抜けを防止する機能を発揮する。この場合、第一領域３９の変形量は第二領域４０に比べて小さく、その一方で第二領域４０によって内輪２８に対する拘束力が十分に確保されているため、加締め部分３８全体で見れば、少ない変形量でもって十分な拘束力を得られ、加締め時の予肉量の不足が発生することなく、加締め部分３８での耐久性の向上を図ることが可能である。加締めはこれ以外にも、内方部材３１の端部に凹みを形成し、直径方向外方に広げる通常の加締めでもよい。   Of the caulking portion 38, the first area 39 mainly satisfies the gap between the inner ring 28 and prevents the inner ring 28 from rattling, and the second area 40 is more restrained than the first area 39. The function of preventing the inner ring 28 from coming off with force is exhibited. In this case, the deformation amount of the first region 39 is smaller than that of the second region 40. On the other hand, the second region 40 sufficiently secures the restraining force against the inner ring 28. It is possible to obtain a sufficient restraining force with a small amount of deformation, and to improve the durability at the caulking portion 38 without causing a shortage of the pre-mesh amount at the time of caulking. In addition to this, the normal caulking may be performed by forming a dent at the end of the inner member 31 and spreading it outward in the diameter direction.

この実施形態では、前記加締めにより軸受すきまが負に設定されて予圧が付与された構造を具備している。軸受すきまは、軸受加工工程において、外方部材２４の複列の軌道面２１，２２のピッチＰ０と溝径、内輪２７の軌道面２９の小径端面（又は内方部材３１の軌道面２９の肩部３７）からの軸方向寸法Ｐ１と溝径、内輪２８の軌道面３０の小径端面からの軸方向寸法Ｐ２と溝径、及びボール径をそれぞれ管理して選択組み合わせすることにより所望の負の軸受すきまに設定することができる。 In this embodiment, the bearing clearance is set to be negative by the caulking, and a preload is applied. In the bearing machining process, the bearing clearance includes the pitch P 0 and the groove diameter of the double-row raceway surfaces 21 and 22 of the outer member 24, the small-diameter end face of the raceway surface 29 of the inner ring 27 (or the raceway surface 29 of the inner member 31). the axial dimension P 1 and the groove diameter of the shoulder portion 37) of the raceway surface 30 of the inner ring 28 axial dimension P 2 and the groove diameter from the small-diameter end face, and desired by selecting combinations manage respectively a ball diameter Negative bearing clearance can be set.

負の軸受すきまは、以下の要領で測定することができる。例えば、図２に示す実施形態の場合、内輪２８を内方部材３１に圧入するに際して、軸受すきまが正の状態で内輪２８の圧入を一旦止め、この状態での外方部材２４の軸方向移動量を測定し、その後、内輪２８を内方部材３１の肩部３７に当接するまで圧入してその圧入を完了し、圧入を一旦止めた状態から圧入を完了した状態に至るまでの内輪２８の軸方向移動量を測定し、外方部材２４の軸方向移動量の測定値と内輪２８の軸方向移動量の測定値との差を組み立て完了後の負の軸受すきまとして求めればよい。 Negative bearing clearance can be measured as follows. For example, in the embodiment shown in FIG. 2, when the inner ring 28 is press-fitted into the inner member 31, the press-fitting of the inner ring 28 is temporarily stopped when the bearing clearance is positive, and the outer member 24 is moved in the axial direction in this state. the amount was measured, then, completes its pressed into pressed until it abuts the inner ring 28 on the shoulder portion 37 of the inner member 31, the inner ring 28 press-fitted from the stopped once the state up to the state completing the press fit The axial movement amount is measured, and the difference between the measured value of the axial movement amount of the outer member 24 and the measured value of the axial movement amount of the inner ring 28 may be obtained as a negative bearing clearance after assembly is completed.

本発明の実施形態では、負の軸受すきまで予圧を付与したことにより、同一スパンでも、軸受剛性を大きく向上させることが可能となる。また、同一空間内で内部諸元を変更し、転動体個数を増加させて軸受剛性を向上させたり、外方部材２４の肉厚やフランジ２３の肉厚を最適化して外方部材２４の変形を抑え、軸受剛性を向上させることが可能となる。さらに、組み込み後の予圧量のばらつき範囲を狭く抑えて高い予圧を維持させることができる。すなわち、図４の従来例に比べて図１の実施形態、さらには図２の実施形態の方が嵌め合いが少なくなるので、嵌め合い公差によるすきま減少量のばらつき成分がゼロになり、従って、公差集積上発生していた低予圧領域がなくなり、軸受剛性も高まる。   In the embodiment of the present invention, the bearing rigidity can be greatly improved even in the same span by applying the preload up to the negative bearing clearance. Further, by changing the internal specifications in the same space and increasing the number of rolling elements to improve the bearing rigidity, the thickness of the outer member 24 and the thickness of the flange 23 are optimized, and the outer member 24 is deformed. As a result, the bearing rigidity can be improved. Furthermore, a high preload can be maintained by narrowing the variation range of the preload amount after incorporation. That is, since the fitting of the embodiment of FIG. 1 and the embodiment of FIG. 2 is less than the conventional example of FIG. 4, the variation component of the clearance reduction amount due to the fitting tolerance becomes zero. The low preload region that occurs due to tolerance accumulation is eliminated, and the bearing rigidity is increased.

図１及び図２に示す実施形態は、自動車の従動輪用としての構造例であるが、本発明はこれに限定されることなく、自動車の駆動輪用としても適用可能である。その場合、内方部材は、その中心部に軸方向に貫通孔が形成された中空形状をなし、その貫通孔の内径面にスプライン又はセレーション等が形成される。その内方部材の貫通孔に等速自在継手の軸部を挿通し、その軸部の外径面に形成されたスプライン又はセレーション等との結合により両者間でトルク伝達が可能となる。駆動輪側において、等速自在継手の組立時に、ナットの締付けトルクの管理による軸受すきまの調整が不要となる。また、従動輪用においても、内方部材を中空構造とし、放熱効果を向上して、軸受の昇温の抑制や軽量化を図ることもできる。   The embodiment shown in FIGS. 1 and 2 is an example of a structure for a driven wheel of an automobile, but the present invention is not limited to this and can also be applied to a driving wheel of an automobile. In this case, the inner member has a hollow shape in which a through hole is formed in the central portion in the axial direction, and a spline or a serration is formed on the inner diameter surface of the through hole. The shaft portion of the constant velocity universal joint is inserted into the through-hole of the inner member, and torque can be transmitted between the two by coupling with a spline or serration formed on the outer diameter surface of the shaft portion. On the drive wheel side, adjustment of the bearing clearance by managing the tightening torque of the nut becomes unnecessary when assembling the constant velocity universal joint. Also for the driven wheel, the inner member can have a hollow structure to improve the heat dissipation effect, thereby suppressing the temperature rise of the bearing and reducing the weight.

本発明に係る車輪軸受装置の実施形態を示す断面図である。It is sectional drawing which shows embodiment of the wheel bearing apparatus which concerns on this invention. 本発明の他の実施形態を示す断面図である。It is sectional drawing which shows other embodiment of this invention. 図１又は図２の内方部材の加締め部分を示す側面図である。It is a side view which shows the crimping part of the inward member of FIG. 1 or FIG. 車輪軸受装置の従来例を示す断面図である。It is sectional drawing which shows the prior art example of a wheel bearing apparatus.

符号の説明Explanation of symbols

２１，２２ 軌道面
２４ 外方部材
２５ 車輪取付け用フランジ
２６ 小径段部
２７，２８ 内輪
２９，３０ 軌道面
３１ 内方部材
３２ 転動体
３８ 加締め部分 21, 22 Raceway surface 24 Outer member 25 Wheel mounting flange 26 Small diameter step portion 27, 28 Inner ring 29, 30 Raceway surface 31 Inner member 32 Rolling element 38 Clamping portion

Claims (2)

内周に複列の軌道面２１，２２を一体に設けた外方部材２４と、一端に車輪取付け用フランジ２５、他端に円筒状小径段部２６を設け、その小径段部２６に内輪２８を圧入して前記外方部材２４の軌道面２１，２２に対向する複列の軌道面２９，３０を形成した内方部材３１と、前記外方部材２４と内方部材３１の両軌道面間に介在する複列の転動体３２とを備え、車輪取付け用フランジ側の軌道面２９を前記内方部材３１の外周に直接形成し、前記内方部材３１の小径段部２６の端部を径方向外方に加締めることにより圧入した内輪２８を内方部材３１に固定した車輪軸受装置の製造方法において、前記外方部材２４、内方部材３１、内輪２８及び転動体３２を選択組み合わせし、前記内輪２８を内方部材に圧入するに際して、軸受すきまが正の状態で内輪２８の圧入を一旦止め、この状態での外方部材２４の軸方向移動量を測定し、その後、圧入を一旦止めた状態から内輪２８を内方部材３１の肩部３７に当接するまで圧入して内方部材３１の小径段部２６の端部を加締めた状態に至るまでの内輪２８の軸方向移動量を測定し、前記外方部材２４の軸方向移動量の測定値と前記内輪２８の軸方向移動量の測定値との差を負の軸受すきまとすることを特徴とする車輪軸受装置の製造方法。   An outer member 24 integrally provided with double-row raceway surfaces 21 and 22 on the inner periphery, a wheel mounting flange 25 at one end, and a cylindrical small diameter step portion 26 at the other end, an inner ring 28 at the small diameter step portion 26. The inner member 31 formed with double rows of raceway surfaces 29 and 30 facing the raceway surfaces 21 and 22 of the outer member 24, and between the raceway surfaces of the outer member 24 and the inner member 31. And a double-row rolling element 32 interposed therebetween, and a raceway surface 29 on the wheel mounting flange side is formed directly on the outer periphery of the inner member 31, and the end of the small-diameter step portion 26 of the inner member 31 has a diameter. In the manufacturing method of the wheel bearing device in which the inner ring 28 press-fitted by caulking outward in the direction is fixed to the inner member 31, the outer member 24, the inner member 31, the inner ring 28 and the rolling element 32 are selectively combined, When press-fitting the inner ring 28 into the inner member, the bearing clearance In the positive state, the press-fitting of the inner ring 28 is temporarily stopped, the axial movement amount of the outer member 24 in this state is measured, and then the inner ring 28 is moved to the shoulder 37 of the inner member 31 from the state where the press-fitting is temporarily stopped. The amount of axial movement of the inner ring 28 until the end of the small-diameter step portion 26 of the inner member 31 is crimped until it comes into contact is measured, and the amount of axial movement of the outer member 24 is measured. The difference between the measured value and the measured value of the amount of axial movement of the inner ring 28 is defined as a negative bearing clearance. 内周に複列の軌道面２１，２２を一体に設けた外方部材２４と、一端に車輪取付け用フランジ２５、他端に円筒状小径段部２６を設け、その小径段部２６に内輪２７，２８を圧入して前記外方部材２４の軌道面２１，２２に対向する複列の軌道面２９，３０を形成した内方部材３１と、前記外方部材２４と内方部材３１の両軌道面間に介在する複列の転動体３２とを備え、前記内方部材３１の小径段部２６の端部を径方向外方に加締めることにより圧入した内輪２７，２８を内方部材３１に固定した車輪軸受装置の製造方法において、前記外方部材２４、内方部材３１、内輪２７，２８及び転動体３２を選択組み合わせし、前記内輪２８を内方部材３１に圧入するに際して、軸受すきまが正の状態で内輪２８の圧入を一旦止め、この状態での外方部材２４の軸方向移動量を測定し、その後、圧入を一旦止めた状態から内輪２８を内輪２７の小径端面に当接するまで圧入して内方部材３１の小径段部２６の端部を加締めた状態に至るまでの内輪２８の軸方向移動量を測定し、前記外方部材２４の軸方向移動量の測定値と前記内輪２８の軸方向移動量の測定値との差を負の軸受すきまとすることを特徴とする車輪軸受装置の製造方法。   An outer member 24 integrally provided with double-row raceway surfaces 21 and 22 on the inner periphery, a wheel mounting flange 25 at one end, and a cylindrical small diameter step portion 26 at the other end, and an inner ring 27 at the small diameter step portion 26. , 28 are press-fitted to form an inner member 31 having double rows of raceway surfaces 29, 30 facing the raceway surfaces 21, 22 of the outer member 24, and both raceways of the outer member 24 and the inner member 31. A plurality of rolling elements 32 interposed between the surfaces, and inner rings 27 and 28 that are press-fitted by caulking the end of the small-diameter step portion 26 of the inner member 31 radially outward. In the manufacturing method of the fixed wheel bearing device, when the outer member 24, the inner member 31, the inner rings 27, 28 and the rolling elements 32 are selectively combined and the inner ring 28 is press-fitted into the inner member 31, a bearing clearance is generated. In the positive state, the press-fitting of the inner ring 28 is temporarily stopped. The axial movement of the side member 24 is measured, and then the inner ring 28 is press-fitted until the inner ring 28 comes into contact with the small-diameter end surface of the inner ring 27 from the state where the press-fitting is temporarily stopped. The axial movement amount of the inner ring 28 until the tightened state is measured, and the difference between the measured value of the axial movement amount of the outer member 24 and the measured value of the axial movement amount of the inner ring 28 is a negative bearing. A method for manufacturing a wheel bearing device, characterized by a clearance.
JP2006340054A 2006-12-18 2006-12-18 Manufacturing method of wheel bearing device Expired - Lifetime JP4658028B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2006340054A JP4658028B2 (en) 2006-12-18 2006-12-18 Manufacturing method of wheel bearing device

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2006340054A JP4658028B2 (en) 2006-12-18 2006-12-18 Manufacturing method of wheel bearing device

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
JP26903799A Division JP3962187B2 (en) 1999-09-22 1999-09-22 Wheel bearing device

Publications (2)

Publication Number Publication Date
JP2007085553A JP2007085553A (en) 2007-04-05
JP4658028B2 true JP4658028B2 (en) 2011-03-23

Family

ID=37972703

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2006340054A Expired - Lifetime JP4658028B2 (en) 2006-12-18 2006-12-18 Manufacturing method of wheel bearing device

Country Status (1)

Country Link
JP (1) JP4658028B2 (en)

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5868518A (en) * 1981-10-16 1983-04-23 Nippon Seiko Kk Assembling method for double row ball bearing
JPS58121322A (en) * 1982-01-14 1983-07-19 Nippon Seiko Kk Assembling method for race separation type double row angular ball bearing
JPS5983832A (en) * 1982-11-02 1984-05-15 Tokyo Seimitsu Co Ltd Combining method and device of ball bearing
JPH07217649A (en) * 1994-02-04 1995-08-15 Nippon Seiko Kk Method of measuring pre-load clearance of double row rolling bearing and device therefor
JPH10185717A (en) * 1996-11-05 1998-07-14 Koyo Seiko Co Ltd Method for measuring pre-load of a plurality of rows of rolling bearings
JPH11129703A (en) * 1997-08-28 1999-05-18 Nippon Seiko Kk Rolling bearing unit for wheel supporting

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5868518A (en) * 1981-10-16 1983-04-23 Nippon Seiko Kk Assembling method for double row ball bearing
JPS58121322A (en) * 1982-01-14 1983-07-19 Nippon Seiko Kk Assembling method for race separation type double row angular ball bearing
JPS5983832A (en) * 1982-11-02 1984-05-15 Tokyo Seimitsu Co Ltd Combining method and device of ball bearing
JPH07217649A (en) * 1994-02-04 1995-08-15 Nippon Seiko Kk Method of measuring pre-load clearance of double row rolling bearing and device therefor
JPH10185717A (en) * 1996-11-05 1998-07-14 Koyo Seiko Co Ltd Method for measuring pre-load of a plurality of rows of rolling bearings
JPH11129703A (en) * 1997-08-28 1999-05-18 Nippon Seiko Kk Rolling bearing unit for wheel supporting

Also Published As

Publication number Publication date
JP2007085553A (en) 2007-04-05

Similar Documents

Publication Publication Date Title
US8449197B2 (en) Bearing apparatus for a wheel of vehicle
JP5134340B2 (en) Wheel bearing device
JP5366665B2 (en) Wheel bearing device
JP5134356B2 (en) Wheel bearing device
JP2004340311A (en) Bearing unit for wheel
US7665900B2 (en) Vehicle wheel bearing apparatus
JP2001180210A (en) Wheel bearing device
JP2010047059A (en) Wheel bearing device and axle module
JP3962187B2 (en) Wheel bearing device
US20080273824A1 (en) Bearing device for axle and fixing structure using the same
JP2010042785A (en) Bearing device for wheel
JP4658028B2 (en) Manufacturing method of wheel bearing device
JP2009058077A (en) Wheel bearing unit
JP4772637B2 (en) Wheel bearing device
JP2012035798A (en) Method for manufacturing bearing device for wheel
JP2007162828A (en) Wheel bearing device and axle module equipped therewith
JP2017047716A (en) Bearing device for wheel
JP2006312459A5 (en)
JP2008168797A (en) Bearing device for driving wheel
JP5150990B2 (en) Manufacturing method of axle bearing device
JP5143442B2 (en) Drive wheel bearing device
CN103348149A (en) Bearing device for hub shaft for wheel
WO2010021225A1 (en) Bearing device for wheel, and axle module
JP4120178B2 (en) Manufacturing method of rolling bearing unit for driving wheel and driving unit for wheel
JP4826779B2 (en) Rolling bearing device for wheels

Legal Events

Date Code Title Description
RD04 Notification of resignation of power of attorney

Free format text: JAPANESE INTERMEDIATE CODE: A7424

Effective date: 20091105

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20100115

A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20100311

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20100512

A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20100709

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20101006

A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20101027

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

Free format text: JAPANESE INTERMEDIATE CODE: A01

Effective date: 20101210

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

Free format text: JAPANESE INTERMEDIATE CODE: A01

A61 First payment of annual fees (during grant procedure)

Free format text: JAPANESE INTERMEDIATE CODE: A61

Effective date: 20101222

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

Free format text: PAYMENT UNTIL: 20140107

Year of fee payment: 3

R150 Certificate of patent or registration of utility model

Ref document number: 4658028

Country of ref document: JP

Free format text: JAPANESE INTERMEDIATE CODE: R150

Free format text: JAPANESE INTERMEDIATE CODE: R150

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

EXPY Cancellation because of completion of term