JP2006312459A5 - - Google Patents
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- JP2006312459A5 JP2006312459A5 JP2006219424A JP2006219424A JP2006312459A5 JP 2006312459 A5 JP2006312459 A5 JP 2006312459A5 JP 2006219424 A JP2006219424 A JP 2006219424A JP 2006219424 A JP2006219424 A JP 2006219424A JP 2006312459 A5 JP2006312459 A5 JP 2006312459A5
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- 238000005096 rolling process Methods 0.000 claims description 13
- 238000004519 manufacturing process Methods 0.000 claims description 6
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- 230000001939 inductive effect Effects 0.000 description 2
- 239000011248 coating agent Substances 0.000 description 1
- 238000000576 coating method Methods 0.000 description 1
- 230000023298 conjugation with cellular fusion Effects 0.000 description 1
- 230000001808 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
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Description
本発明は自動車の駆動車輪用の軸受ユニットに関するもので、より詳しくは、ハブ輪と等速自在継手の外方継手部材と車軸軸受とをユニット化した駆動車輪用軸受ユニットの製造方法に関するものである。 The present invention relates to a bearing unit for a drive wheel of an automobile, and more particularly to a method for manufacturing a drive wheel bearing unit in which a hub wheel, an outer joint member of a constant velocity universal joint, and an axle bearing are unitized. is there.
自動車のエンジンから駆動車輪に動力を伝達する動力伝達系は、エンジンと車輪との相対的位置関係の変化による角度変位と軸方向変位に対応する必要があるため、たとえば図４に示すように、エンジン側と駆動車輪側との間にドライブシャフト（１）を介装し、ドライブシャフト（１）の一端を摺動型等速自在継手（Ｊ1）を介してディファレンシャルに連結し、他端を固定型等速自在継手（Ｊ2）を介して駆動車輪（２）に連結している。摺動型等速自在継手（Ｊ1）のいわゆるプランジングによって軸方向の変位が吸収される。これに対して固定型等速自在継手（Ｊ2）は角度変位のみが可能である。 Since the power transmission system that transmits power from the engine of the automobile to the driving wheel needs to cope with angular displacement and axial displacement due to a change in the relative positional relationship between the engine and the wheel, for example, as shown in FIG. A drive shaft (1) is interposed between the engine side and the drive wheel side, one end of the drive shaft (1) is connected to the differential via a sliding type constant velocity universal joint (J1), and the other end is fixed. It is connected to the drive wheel (2) via a mold constant velocity universal joint (J2). The axial displacement is absorbed by so-called plunging of the sliding type constant velocity universal joint (J1). In contrast, the fixed type constant velocity universal joint (J2) can only be angularly displaced.
固定型等速自在継手（Ｊ2）は、ドライブシャフト（１）の前記他端に取り付けられた内方継手部材（４）と、ハブ輪（７）に結合された外方継手部材（３）と、内方継手部材（４）および外方継手部材（３）のボール溝間に組み込まれた複数のトルク伝達ボール（５）と、内方継手部材（４）の外球面と外方継手部材（３）の内球面との間に介在してトルク伝達ボールを保持する保持器（６）を主要な構成要素としている。ハブ輪（７）は車軸軸受（８）によって回転自在に支持され、このハブ輪（７）に駆動車輪（２）のホイールが固定される。 The fixed type constant velocity universal joint (J2) includes an inner joint member (4) attached to the other end of the drive shaft (1), and an outer joint member (3) coupled to the hub wheel (7). , A plurality of torque transmitting balls (5) incorporated between the ball grooves of the inner joint member (4) and the outer joint member (3), the outer spherical surface of the inner joint member (4) and the outer joint member ( A cage (6) that holds the torque transmitting ball interposed between the inner spherical surface of 3) is a main component. The hub wheel (7) is rotatably supported by an axle bearing (8), and the wheel of the drive wheel (2) is fixed to the hub wheel (7).
ハブ輪（７）と等速自在継手（Ｊ2 ）の外方継手部材（３）と車軸軸受（８）がユニット化されて駆動車輪用軸受ユニット（Ｈ）を構成している。 The hub wheel (7), the outer joint member (3) of the constant velocity universal joint (J2) and the axle bearing (8) are unitized to form a drive wheel bearing unit (H).
車軸軸受（８）は複列転がり軸受であって、ナックル（９）を介して車体の懸架装置によって支持され、複列のボール（8a，8b）のうちの一方（8a）が車両のアウトボード側に位置し他方（8b）が車両のインボード側に位置する。インボード側のボール列は、ドライブシャフト（１）からトルクを受ける等速自在継手（Ｊ2）の外方継手部材（３）からの熱による影響があり、しかもインボード側故に良好な放熱状態が得にくいことから、非常に厳しい荷重条件が要求されている。 The axle bearing (8) is a double-row rolling bearing and is supported by the vehicle suspension via the knuckle (9), and one of the double-row balls (8a, 8b) (8a) is outboard of the vehicle. The other side (8b) is located on the inboard side of the vehicle. The ball row on the inboard side is affected by heat from the outer joint member (3) of the constant velocity universal joint (J2) that receives torque from the drive shaft (1), and also has a good heat dissipation state due to the inboard side. Since it is difficult to obtain, very severe load conditions are required.
本発明の目的は、駆動車輪用軸受ユニットの剛性を高めて耐久性を向上させるとともに小型化、コンパクト化を図ることにある。 An object of the present invention is to increase the rigidity of a bearing unit for a drive wheel to improve durability and to reduce the size and size.
本発明は、ハブ輪と等速自在継手の外方継手部材と車軸軸受とをユニット化し、車軸軸受の複列のインナレースのうちの少なくとも一方を外方継手部材に形成し、外方継手部材がマウス部と軸部を有し、マウス部の軸部側端面をハブ輪との突合せ面とし、軸部とハブ輪をはめあい部とセレーションとにより結合し、はめあい部を複列の転動体間に配置し、セレーション部は、噛み合い歯間に締めしろを設け、円周方向ガタをなくし、また、その長さをはめあい部の長さよりも長くした駆動車輪用軸受ユニットを製造する方法であって、次の工程からなる。
ハブ輪と車軸軸受を組み付け、
ハブ輪に外方継手部材を組み付け、
ハブ輪の通し孔に外方継手部材の軸部を挿入し、
セレーションが噛み合うように周方向の位相を合わせてさらに軸方向に押してはめあい部の圧入を開始し、
ハブ輪の環状凸縁に外方継手部材の突合せ部が当たった時点で圧入を終了する。
はめあい部は、その締め代量によって、ハブ輪外径が、比例膨張するため、はめあい部上に転動体（レース面）がある場合、軸受すきま管理が繁雑となり、また、転動体とはめあい部の軸方向位置によっては、レース形状が変形し耐久性の悪化を招く。そのため、はめあい部は、転動体を避けた位置に設けるのが望ましいのである。そして、はめあい部の長さ、セレーション部の長さ、はめあい部の締め代を適切な範囲に設定することによって、車輪用軸受ユニットとして必要な剛性と現実的な方法、圧入力での組立て、すなわち車輪用軸受ユニットの製造が可能になる。
This onset Ming, the outer joint member and the axle bearing of the wheel hub and the constant velocity universal joint unitized to form at least one of the inner race of the double row of the axle bearing outer joint member, the outer joint The member has a mouth part and a shaft part, the shaft part side end surface of the mouse part is a butting surface with the hub wheel, the shaft part and the hub wheel are joined by a fitting part and serrations, and the fitting part is a double row rolling element The serration part is a method of manufacturing a drive wheel bearing unit in which a margin is provided between the meshing teeth, the circumferential play is eliminated, and the length thereof is longer than the length of the fitting part. It consists of the following steps.
Assemble the hub wheel and axle bearing,
Assemble the outer joint member to the hub wheel,
Insert the shaft part of the outer joint member into the through hole of the hub wheel,
Match the circumferential phase so that the serrations engage, and push it further in the axial direction to start press fitting.
The press-fitting is completed when the butted portion of the outer joint member hits the annular convex edge of the hub wheel.
Is Meai part, by the interference amount, since the hub wheel outer diameter is proportional expansion, when there is a rolling element on the mating part (raceways), bearing clearance management becomes complicated, also fit a rolling element Depending on the position of the portion in the axial direction, the race shape may be deformed, resulting in deterioration of durability. Therefore, it is desirable that the fitting portion is provided at a position avoiding the rolling elements. And by setting the length of the fitting part, the length of the serration part, and the tightening allowance of the fitting part to an appropriate range, the rigidity and practical method required for the wheel bearing unit, assembly by pressure input , that is, The wheel bearing unit can be manufactured .
そこで、本発明は、セレーション部の噛み合い歯間に締め代を設け、そして、長さ（Ｓ）をはめあい部の長さ（Ｌ）よりも長く（Ｓ＞Ｌ）したことを特徴とする。セレーション部に、円周方向ガタがあると、突合わせ部においてガタ分だけ擦れるため、摩耗、フレッティングが生じ、軸受すきまに影響し、軸受剛性が低下するなど不都合が生じる。そのため、セレーション部のガタをなくすことは、軸受性能維持にとって重要である。一方、セレーション部長さを前述の構成とすることで、ハブ輪に外方継手部材を組み付ける際に、まずセレーション部が噛み合い始め、周方向の位相が合った後、圧入が始まるため、圧入操作が容易となる。つまり、一旦圧入が始まった後では相対回転は難しく、セレーションの周方向位相合わせを行うことは困難である。 Accordingly, the present invention is the interference is provided between the meshing teeth of the serration portion, and is characterized in that the long (S> L) than the length length of portion fitting the (S) (L). The serration portion, if there is circumferential backlash, since rubbing by backlash in the abutting portion, wear, cause deflection Tsu coating affects the bearing gap, the inconveniences such as the bearing rigidity is lowered. Therefore, it is important for eliminating bearing backlash to maintain the bearing performance. On the other hand, by setting the serration portion length as described above, when the outer joint member is assembled to the hub wheel, the serration portion first starts to mesh, and after the circumferential phase is matched, press-fitting starts. It becomes easy. That is, once the press-fitting has started, relative rotation is difficult, and it is difficult to perform circumferential phase alignment of serrations.
より具体的な例を挙げるならば、はめあい部の長さを、はめあい部軸径の１／５以上とし、そして、はめあい部締め代（Ａ）を０≦Ａ≦６０μｍとする。はめあい部には、軸受のラジアル荷重が負荷されるので、前述の長さ設定より短い場合、面圧が高くなり、問題となる。したがって、はめあい部は、請求項１の転動体間における前述の長さ設定値が望ましい位置および長さとなる。また、はめあい部の締め代の下限については、軸受支持剛性の面から０μｍ≦Ａとし、上限については、セレーション部とはめあい部を合わせた圧入力がナットの軸力以下となるようＡ≦６０μｍとしたものである。 If a more specific example, the length of the fitting portion, and 1/5 or more fitting portions axis diameter, and, you fitting portion interference with (A) and 0 ≦ A ≦ 60μm. Since the radial load of the bearing is applied to the fitting portion, when the length is shorter than the above-described length setting, the surface pressure becomes high, which causes a problem. Accordingly, the fitting portion has a position and a length in which the above-described length setting value between the rolling elements of claim 1 is desirable. Further, the lower limit of the interference of the fitting portion is set to 0 μm ≦ A from the viewpoint of bearing support rigidity, and the upper limit is set to A ≦ 60 μm so that the pressure input including the serration portion and the fitting portion is less than the axial force of the nut. It is a thing.
請求項２の発明は、外方継手部材のマウス底に圧入治具を当てるための平坦部を設けたことを特徴とする。これにより、ハブ輪に外方継手部材の軸部を圧入して組み付ける際に、外方継手部材を押圧する圧入治具がマウス底の平坦部に当接して、押圧力が正しく軸方向に作用するため、圧入作業が容易となる。 The invention of claim 2 is characterized in that a flat portion for applying a press-fitting jig to the mouth bottom of the outer joint member is provided. As a result, when the shaft portion of the outer joint member is press-fitted and assembled to the hub wheel, the press-fitting jig that presses the outer joint member contacts the flat portion of the bottom of the mouse, and the pressing force acts correctly in the axial direction. Therefore, the press-fitting operation becomes easy.
以上説明したように、本発明は、ハブ輪と等速自在継手の外方継手部材と車軸軸受とをユニット化し、車軸軸受の複列のインナレースのうちの少なくとも一方を外方継手部材に形成し、外方継手部材がマウス部と軸部を有し、マウス部の軸部側端面をハブ輪との突合せ面とし、軸部とハブ輪をはめあいとセレーションとにより結合し、はめあい部を複列の転動体間に配置し、セレーション部は、噛み合い歯間に締めしろを設け、円周方向ガタをなくし、また、その長さをはめあい部の長さよりも長くした駆動車輪用軸受ユニットを製造する方法であって、ハブ輪と車軸軸受を組み付け、ハブ輪に外方継手部材を組み付け、ハブ輪の通し孔に外方継手部材の軸部を挿入し、セレーションが噛み合うように周方向の位相を合わせてさらに軸方向に押してはめあい部の圧入を開始し、ハブ輪の環状凸縁に外方継手部材の突合せ部が当たった時点で圧入を終了するようにしたものであるから、セレーション部とはめあい部の各々の長さ及び締め代を適切な範囲に設定することによって、車輪用軸受ユニットとして必要な剛性と現実的な方法、圧入力での組立てが可能になる。 As described above, the onset Ming, the outer joint member and the axle bearing of the wheel hub and the constant velocity universal joint unitized, the outer joint member at least one of the inner race of the double row axle bearing formed, the outer joint member has a mouth portion and a shaft portion, the shaft portion side end face of the mouth portion and abutting surfaces of the hub wheel, when fitting the shaft portion and the hub wheel connected by a serration, the fitting portion The drive wheel bearing unit is arranged between the double row rolling elements , the serration part is provided with a margin between the meshing teeth, the circumferential play is eliminated, and the length is longer than the length of the fitting part. A method of manufacturing, in which a hub wheel and an axle bearing are assembled, an outer joint member is assembled to the hub wheel, a shaft portion of the outer joint member is inserted into the through hole of the hub wheel, and the circumferential direction is set so that the serration meshes. Match the phase further in the axial direction And starts press-fitting portion fitting in, since it is that so as to end the press-fitting when the butted portion of the outer joint member strikes the annular convex rim of the wheel hub, each of the serrated portion and Fitting unit length By setting the length and the tightening allowance within appropriate ranges, the rigidity required for the wheel bearing unit, assembling with a realistic method and pressure input can be performed.
具体的には、セレーション部の長さ（Ｓ）とはめあい部の長さ（Ｌ）との関係をＳ＞Ｌとすることにより、ハブ輪に外方継手部材を組み付ける際に、まずセレーション部が噛み合い始め、周方向の位相が合った後、はめあい部に入るため、圧入操作が容易となる。 Specifically, when the relationship between the length of the serration portion (S) and the length of the fitting portion (L) is S> L, when the outer joint member is assembled to the hub wheel, the serration portion first After the meshing is started and the phases in the circumferential direction are matched, since the fitting portion is entered, the press-fitting operation becomes easy.
請求項２の発明のように、外方継手部材のマウス底に圧入治具を当てるための平坦部を設けることにより、ハブ輪に外方継手部材の軸部を圧入して組み付ける際に、外方継手部材を押圧する圧入治具がマウス底の平坦部に当接して、押圧力が正しく軸方向に作用するため、圧入作業が容易となる。 As in the invention of claim 2 , by providing a flat portion for applying a press-fitting jig to the mouth bottom of the outer joint member, when the shaft portion of the outer joint member is press-fitted to the hub wheel and assembled, Since the press-fitting jig that presses the joint member comes into contact with the flat part of the bottom of the mouse, and the pressing force acts correctly in the axial direction, the press-fitting operation becomes easy.
図１に示すように、ハブ輪（10）と、等速自在継手の外方継手部材（20）と、車軸軸受（30）とをユニット化して駆動車輪用軸受ユニットが構成されている。 As shown in FIG. 1, a hub unit (10), an outer joint member (20) of a constant velocity universal joint, and an axle bearing (30) are unitized to form a drive wheel bearing unit.
車軸軸受（30）は複列のアウタレース（32ａ，32ｂ）を備えた軸受外輪（31）と、複列のインナレース（33ａ，33ｂ）と、複列の転動体（34ａ，34ｂ）とで構成される。ここでは複列のインナレース（33ａ，33ｂ）のうちの一方（33ａ）をハブ輪（10）の外周面に直接形成し、他方（33ｂ）を外方継手部材（20）の外周面に直接形成した場合を例示してあるが、レース面を備えた別体のリング（内側軌道輪）をハブ輪（10）および／または外方継手部材（20）に嵌合させるようにしてもよい。軸受外輪（31）はフランジ（35）にてナックルに固定される。図示した実施の形態は複列アンギュラ玉軸受構造であるため軸受負荷容量が大きい。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。車軸軸受（30）の両端開口部には、外部からの異物の浸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（36）を装着してある。 The axle bearing (30) includes a bearing outer ring (31) having a double row outer race (32a, 32b), a double row inner race (33a, 33b), and a double row rolling element (34a, 34b). Is done. Here, one (33a) of the double row inner races (33a, 33b) is formed directly on the outer peripheral surface of the hub wheel (10), and the other (33b) is directly connected to the outer peripheral surface of the outer joint member (20). Although the case where it forms is illustrated, a separate ring (inner race) having a race surface may be fitted to the hub ring (10) and / or the outer joint member (20). The bearing outer ring (31) is fixed to the knuckle by the flange (35). Since the illustrated embodiment has a double-row angular contact ball bearing structure, the bearing load capacity is large. It is also possible to adopt a double-row tapered roller bearing structure in which tapered rollers are used for the rolling elements. Seals (36) are attached to the opening portions at both ends of the axle bearing (30) in order to prevent entry of foreign matter from the outside and leakage of grease filled inside.
ハブ輪（10）はフランジ（11）を備え、このフランジ（11）の円周方向等間隔位置にホイールベースを固定するためのハブボルト（12）を取り付けてある。ハブ輪（10）の外周面には複列のインナレースのうちの一方（33ａ）が形成されている。このインナレース部には高周波焼入れ等によって硬化層を形成させてある。ハブ輪（10）の外方継手部材側の端部には、外周部分に環状凸縁（13）を形成してある。ハブ輪（10）は反外方継手部材側の端面に開口する空洞部（16）を有し、ハブ輪（10）の中心部には軸方向に貫通した通し孔を設けてある。 The hub wheel (10) includes a flange (11), and a hub bolt (12) for fixing the wheel base is attached to the flange (11) at equal circumferential positions. One (33a) of the double row inner races is formed on the outer peripheral surface of the hub wheel (10). A hardened layer is formed on the inner race portion by induction hardening or the like. At the end of the hub wheel (10) on the outer joint member side, an annular convex edge (13) is formed on the outer peripheral portion. The hub wheel (10) has a hollow portion (16) opened at the end face on the side opposite to the outer joint member, and a through hole penetrating in the axial direction is provided at the center of the hub wheel (10).
外方継手部材（20）は、概ね椀状のマウス部（28）と、マウス部（28）と一体的に形成された軸部（29）とを有する。マウス部（28）は、内球面（21）の円周方向等間隔位置に軸方向に延びるボール溝（22）を備えている。このボール溝（22）はトルク伝達ボール（43）が転動するためのもので、高周波焼入れ等により硬化層（23）を形成させてある。外方継手部材（20）の外周面には車軸軸受（30）の複列のインナレースのうちの一方（33ｂ）が形成されている。 The outer joint member (20) has a generally bowl-shaped mouse part (28) and a shaft part (29) formed integrally with the mouse part (28). The mouse portion (28) includes ball grooves (22) extending in the axial direction at equal circumferential positions on the inner spherical surface (21). The ball groove (22) is used for rolling the torque transmitting ball (43), and a hardened layer (23) is formed by induction hardening or the like. One (33b) of the double row inner races of the axle bearing (30) is formed on the outer peripheral surface of the outer joint member (20).
外方継手部材（20）のマウス部（28）内に、内方継手部材（40）、トルク伝達ボール（43）、保持器（44）が組み込まれる。内方継手部材（40）はエンジンからの動力を伝達するドライブシャフト（図示省略）とセレーションまたはスプライン結合するようになっており、外球面（41）の円周方向等分位置に外方継手部材（20）のボール溝（22）と対応するボール溝（42）を備えている。外方継手部材（20）のボール溝（22）と内方継手部材（40）のボール溝（42）との間にトルク伝達ボール（43）が介在して両者間でトルクを伝達する。各トルク伝達ボール（43）は保持器（44）のポケット（45）内に組み込んである。保持器（44）は外方継手部材（20）の内球面（21）と内方継手部材（40）の外球面（41）との間に介在し、トルク伝達ボール（43）を継手二等分面上に配向せしめることによって継手の等速性を担保する役割を果たす。 The inner joint member (40), the torque transmission ball (43), and the cage (44) are incorporated into the mouth portion (28) of the outer joint member (20). The inner joint member (40) is serrated or spline-coupled to a drive shaft (not shown) that transmits power from the engine, and is located at the circumferentially equal position of the outer spherical surface (41). A ball groove (42) corresponding to the ball groove (22) of (20) is provided. A torque transmitting ball (43) is interposed between the ball groove (22) of the outer joint member (20) and the ball groove (42) of the inner joint member (40) to transmit torque therebetween. Each torque transmitting ball (43) is incorporated in a pocket (45) of the cage (44). The cage (44) is interposed between the inner spherical surface (21) of the outer joint member (20) and the outer spherical surface (41) of the inner joint member (40), and the torque transmission ball (43) It plays a role of ensuring the constant velocity of the joint by orienting on the dividing plane.
外方継手部材（20）の軸部（29）は、先端部に雄ねじを切ってあり、さらに、セレーション部（29ａ）とはめあい部（29ｂ）を備えている。マウス部（28）の軸部側端面、言い換えると、はめあい部（29ｂ）のマウス部側端部から半径方向に立ち上がった部分をハブ輪（10）の環状凸縁（13）に対する突合せ部（26）としている。環状凸縁（13）および突合せ部（26）の軸方向位置は複列のインナレース（33ａ，33ｂ）間の距離を左右する。したがって、環状凸縁（13）および突合せ部（26）のいずれか一方または両方の加工量を加減することによって軸受すきま（または予圧）の調整をすることができる。 The shaft portion (29) of the outer joint member (20) has a male screw cut at the tip portion, and further includes a serration portion (29a) and a fitting portion (29b). The shaft part side end face of the mouse part (28), in other words, the part of the fitting part (29b) rising in the radial direction from the mouse part side end part is the butting part (26 to the annular convex edge (13) of the hub wheel (10). ). The axial positions of the annular convex edge (13) and the butting portion (26) influence the distance between the double rows of inner races (33a, 33b). Therefore, the bearing clearance (or preload) can be adjusted by adjusting the amount of processing of either or both of the annular convex edge (13) and the butting portion (26).
図１は、理解を容易にする目的で、中心線を境にして上半分に通常の断面を示し、下半分ではクロスハッチングにより硬化層（熱処理範囲）および熱影響層を表したものである。なお、硬化層を目の詰まったクロスハッチングで表し、熱影響層を目の粗いクロスハッチングで表してある。図示のとおり、インナレース（33ｂ）部分から突合せ部（26）およびシール（36）の摺接部にかけて、外方継手部材（20）の表面に硬化層（25）が形成され、かつ、その熱影響層がボール溝（22）の硬化層（23）の熱影響層と連続している。 For the purpose of facilitating understanding, FIG. 1 shows a normal cross-section in the upper half with the center line as a boundary, and the lower half shows a hardened layer (heat treatment range) and a heat-affected layer by cross-hatching. The hardened layer is represented by clogged cross hatching, and the heat-affected layer is represented by coarse cross hatching. As shown in the figure, a hardened layer (25) is formed on the surface of the outer joint member (20) from the inner race (33b) portion to the sliding contact portion of the butting portion (26) and the seal (36), and the heat The influence layer is continuous with the heat influence layer of the hardened layer (23) of the ball groove (22).
ハブ輪（10）の通し孔には、外方継手部材（20）のセレーション部（29ａ）及びはめあい部（29ｂ）とそれぞれ対応する軸方向位置に、セレーション部（17ａ）及びはめあい部（17ｂ）が形成されている。そして、ハブ輪（10）の通し孔から突出した軸部（29）の雄ねじにナット（29ｃ）を締め付けることによって、ハブ輪（10）と外方継手部材（20）が分離可能に締結される。セレーション部は、ねじれ角がつけてあり、噛み合い歯間を締め代にして、円周方向ガタをなくしている。この場合、セレーション部（17ａ，29ａ）によりトルクの伝達が行なわれる。また、はめあい部（17ｂ，29ｂ）によって、複列のインナレース（33ａ，33ｂ）の心出しがなされる。この心出しは、複列のインナレース（33ａ，33ｂ）が別々の部材すなわちハブ輪（10）と外方継手部材（20）とに配分的に形成されていることから、車軸軸受（30）の良好な軸受性能を発揮させる上で重要な意義を有する。 In the through hole of the hub wheel (10), the serration portion (17a) and the fitting portion (17b) are located at axial positions corresponding to the serration portion (29a) and the fitting portion (29b) of the outer joint member (20), respectively. Is formed. The hub wheel (10) and the outer joint member (20) are detachably fastened by tightening the nut (29c) to the male screw of the shaft portion (29) protruding from the through hole of the hub wheel (10). . The serration portion has a torsion angle, and eliminates the backlash in the circumferential direction by using a clearance between the meshing teeth. In this case, torque is transmitted by the serration units (17a, 29a). Further, centering of the double row inner races (33a, 33b) is performed by the fitting portions (17b, 29b). This centering is formed by distributing the double-row inner races (33a, 33b) to separate members, that is, the hub wheel (10) and the outer joint member (20). It has an important significance in exerting good bearing performance.
図１の駆動車輪用軸受ユニットを組み立てる際には、図２に示すように、先にハブ輪（10）と車軸軸受（30）を組み付けておき、次に、ハブ輪（10）に外方継手部材（20）を組み付ける。なお、外方継手部材（20）の組付けを終えるまでは、インナレース（33ａ，33ｂ）の一方（33ｂ）がないため、片方の転動体列は保持器（37）によって保持される。ハブ輪（10）の通し孔に外方継手部材（20）の軸部（29）を挿入すると、まずセレーション部（17ａ，29ａ）が当たるので、セレーションが噛み合うように周方向の位相を合わせてさらに軸方向に押す。続いて、はめあい部（17ｂ）への挿入が始まる。ハブ輪（10）の環状凸縁（13）に外方継手部材（20）の突合せ部（26）が当たった時点で圧入を終了する。 When assembling the drive wheel bearing unit of FIG. 1, as shown in FIG. 2, the hub wheel (10) and the axle bearing (30) are assembled first, and then the hub wheel (10) is moved outward. Assemble the joint member (20). Until the assembly of the outer joint member (20) is completed, one of the inner races (33a, 33b) (33b) does not exist, so that one of the rolling element rows is held by the cage (37). When the shaft part (29) of the outer joint member (20) is inserted into the through hole of the hub wheel (10), the serration part (17a, 29a) first hits, so the circumferential phase is adjusted so that the serrations mesh. Push further in the axial direction. Subsequently, the insertion into the fitting portion (17b) starts. The press fitting is finished when the butted portion (26) of the outer joint member (20) hits the annular convex edge (13) of the hub wheel (10).
セレーション部（17ａ，29ａ）の長さ（Ｓ）とはめあい部（17ｂ，29ｂ）の長さ（Ｌ）との関係をＳ＞Ｌとする（図１）。これにより、セレーション部（17ａ，29ａ）の噛み合い始めがはめあい部よりも先行することとなるので、セレーション部（17ａ，29ａ）の周方向位相合わせが容易となる。 The relationship between the length (S) of the serration part (17a, 29a) and the length (L) of the fitting part (17b, 29b) is S> L (FIG. 1). Thereby, since the meshing start of the serration portions (17a, 29a) precedes the fitting portion, the circumferential phase alignment of the serration portions (17a, 29a) becomes easy.
図示するように、はめあい部（17ｂ，29ｂ）を複列の転動体（34ａ，34ｂ）間に配置することで、はめあい部の締め代によりハブ輪（10）の外径に変化が生じてもインナレース（33ａ）に影響を与える心配がなくなる。はめあい部（17ｂ，29ｂ）の長さ（Ｌ）は軸径（Ｄ）の１／５以上とする。はめあい部（17ａ，29ａ）の締め代（Ａ）は０μｍ≦Ａ≦６０μｍの範囲に設定する。下限を０μｍ以上とするのは軸受の剛性を確保するためである。上限を６０μｍ以下とするのは、セレーション部（17ａ，29ａ）とはめあい部（17ｂ，29ｂ）を合わせた圧入力がナット（29ｃ）締付けによる軸力以下となるようにしてナット（29ｃ）による締結を有効にするためである。 As shown in the figure, by disposing the fitting portions (17b, 29b) between the double row rolling elements (34a, 34b), even if the outer diameter of the hub wheel (10) changes due to the interference of the fitting portions. No worries affecting inner race (33a). The length (L) of the fitting portion (17b, 29b) is set to 1/5 or more of the shaft diameter (D). The interference (A) of the fitting portions (17a, 29a) is set in a range of 0 μm ≦ A ≦ 60 μm. The lower limit is set to 0 μm or more in order to ensure the rigidity of the bearing. The upper limit is set to 60 μm or less by fastening with the nut (29c) so that the pressure input including the serration parts (17a, 29a) and the fitting parts (17b, 29b) is less than the axial force by tightening the nut (29c). This is to make it effective.
図２に示す外方継手部材（20）はマウス部（28）の底に平坦部（27）を設けてある。この平坦部（27）に圧入治具（50）の先端を当てて力を加えることにより、加えた力がすべて正しく軸方向に作用するため、圧入操作が容易となり、しかも、こじったり、部品を傷めたりする心配がない。 The outer joint member (20) shown in FIG. 2 has a flat portion (27) on the bottom of the mouth portion (28). By applying the force by applying the tip of the press-fitting jig (50) to this flat part (27), all the applied force acts correctly in the axial direction, so the press-fitting operation is easy, and the There is no worry about hurting.
図３に示す実施の形態は、外方継手部材（20）の軸部（29）を中空円筒形とし、符号29ｄで示すように軸端部をかしめることによってハブ輪（10）との結合を行っている。ハブ輪（10）の通し穴の端部に環状段部を形成してスペーサリング（18）を収容させ、このスペーサリング（18）を挟み込むようにしてかしめる。このスペーサリング（18）を省略してハブ輪（10）の通し穴の端部に軸部（29）の軸端部を直接かしめてもよい。軸部（29）を中空としたことによって軽量化、放熱条件の緩和といった利点が得られる。はめあい部（29ｂ）の所期の締め代を保持するため、強度上、軸部（29）の中空部（24）の孔径ｄをはめあい部（29ｂ）の軸径Ｄの９０％以下に設定するのが好ましい。 In the embodiment shown in FIG. 3, the shaft portion (29) of the outer joint member (20) is formed into a hollow cylindrical shape, and the shaft end portion is caulked as indicated by reference numeral 29d, thereby coupling to the hub wheel (10). It is carried out. An annular step is formed at the end of the through hole of the hub wheel (10) to accommodate the spacer ring (18), and the spacer ring (18) is clamped so as to be sandwiched. The spacer ring (18) may be omitted, and the shaft end portion of the shaft portion (29) may be directly caulked to the end portion of the through hole of the hub wheel (10). By making the shaft portion (29) hollow, advantages such as weight reduction and relaxation of heat dissipation conditions can be obtained. In order to maintain the desired tightening allowance of the fitting portion (29b), the hole diameter d of the hollow portion (24) of the shaft portion (29) is set to 90% or less of the shaft diameter D of the fitting portion (29b) in terms of strength. Is preferred.
マウス部（28）の底に形成された平坦部（27）にエンドプレート（48）を装着して、マウス部（28）に充填したグリースの漏出を防ぐようにしている。マウス部底に平坦部（27）を設けない場合などには中空部（24）にエンドプレート（48）を装着するようにしてもよい。エンドプレート（48）には貫通小孔（49）を設けてあるため、中空部（24）による放熱作用が損なわれることはない。つまり、この貫通小孔（49）を通じてマウス部（28）内と外気とが連通しているため、マウス部内や外側継手部材の内表面の熱を貫通小孔（49）および中空部（24）を通じて外部に放散させることができる。 An end plate (48) is attached to a flat part (27) formed at the bottom of the mouse part (28) so as to prevent leakage of grease filled in the mouse part (28). When the flat part (27) is not provided on the bottom of the mouse part, the end plate (48) may be attached to the hollow part (24). Since the end plate (48) is provided with the small through hole (49), the heat radiation action by the hollow portion (24) is not impaired. That is, since the inside of the mouse part (28) communicates with the outside air through the through hole (49), the heat of the inside of the mouse part and the outer surface of the outer joint member is transferred to the through hole (49) and the hollow part (24). Can be dissipated to the outside.
以下、実施例の効果に言及する。外方継手部材の軸端部を加締めることによって外方継手部材とハブ輪とを結合することができる。これにより、ハブ輪から突出した外方継手部材の軸部にハブナットを締め付けることによってハブ輪と外方継手部材を締結するのに比べて、ハブナットを廃止できるため軽量化とコストダウンが図れる。この場合、外方継手部材の軸部の少なくとも端部を中空円筒状にしておくのが好ましい。また、ハブ輪の内径にスペーサリングを嵌入し、このスペーサリングから加締めるようにしてもよい。 Hereinafter, effects of the embodiment will be described. The outer joint member and the hub wheel can be coupled by caulking the shaft end portion of the outer joint member . As a result, the hub nut can be abolished as compared with the case where the hub wheel and the outer joint member are fastened by tightening the hub nut to the shaft portion of the outer joint member protruding from the hub wheel, so that weight reduction and cost reduction can be achieved. In this case, it is preferable that at least an end portion of the shaft portion of the outer joint member is formed in a hollow cylindrical shape. Alternatively, a spacer ring may be fitted into the inner diameter of the hub wheel and crimped from the spacer ring.
外方継手部材の軸部を中空にしてマウス部内と外気を連通させた場合、放熱効果が得られるため、軸受の昇温による寿命低下を抑えることができる。具体的には、中実のものに比べて軸受の温度上昇が約１０℃低下することが確認されている。この場合、強度上、軸部の孔径をはめあい部径の９０％以下とするのが望ましい。また、マウス部底に貫通小孔を有するエンドプレートを装着することにより、外側継手部材のマウス部内に充填したグリースの漏洩を防止しつつ、マウス部内を外気に連通させて通気を促すとともに、継手内部の内圧増大を防止し、放熱効果を維持することができる。 When the shaft portion of the outer joint member is hollow and the inside of the mouth portion communicates with the outside air , a heat dissipation effect can be obtained, so that a reduction in the life due to the temperature rise of the bearing can be suppressed. Specifically, it has been confirmed that the temperature rise of the bearing is reduced by about 10 ° C. compared to the solid one. In this case, the intensity over, not to want to 90% or less of each other portion diameter fitting the pore diameter of the shaft portion. Further, the Rukoto to attach the end plate having a through small holes in the mouse section bottom, while preventing the grease filled in the mouth portion of the outer joint member leaks, encourages the venting communicated mice portion to the outside air The internal pressure increase inside the joint can be prevented, and the heat dissipation effect can be maintained.
10 ハブ輪
17ａ セレーション部
17ｂ はめあい部
20 外方継手部材
26 突合せ部
27 平坦部
28 マウス部
29 軸部
29ａ セレーション部
29ｂ はめあい部
29ｃ ハブナット
30 車軸軸受
33ａ インナレース（アウトボード側）
33ｂ インナレース（インボード側）
48 エンドプレート
49 貫通小孔
50 圧入治具
10 Hub wheel
17a Serration part
17b Fit section
20 Outer joint member
26 Butting part
27 Flat part
28 Mouse part
29 Shaft
29a Serration part
29b Fit part
29c Hub nut
30 Axle bearing
33a Inner race (outboard side)
33b Inner race (inboard side)
48 End plate
49 Through hole
50 Press-fitting jig
Claims (2)
ハブ輪と車軸軸受を組み付け、
ハブ輪に外方継手部材を組み付け、
ハブ輪の通し孔に外方継手部材の軸部を挿入し、
セレーションが噛み合うように周方向の位相を合わせてさらに軸方向に押してはめあい部の圧入を開始し、
ハブ輪の環状凸縁に外方継手部材の突合せ部が当たった時点で圧入を終了する、
車輪用軸受ユニットの製造方法。 The hub wheel and the outer joint member of the constant velocity universal joint and the axle bearing are unitized, and at least one of the double row inner races of the axle bearing is formed in the outer joint member , and the outer joint member is connected to the mouth portion. It has a shaft part, the shaft part side end face of the mouse part is a butting surface with the hub wheel, the shaft part and the hub wheel are joined by fitting and serration, the fitting part is arranged between the double row rolling elements , and serration The part is a method for producing a bearing unit for a drive wheel in which a margin is provided between the meshing teeth, the backlash in the circumferential direction is eliminated, and the length thereof is longer than the length of the fitting part,
Assemble the hub wheel and axle bearing,
Assemble the outer joint member to the hub wheel,
Insert the shaft part of the outer joint member into the through hole of the hub wheel,
Match the circumferential phase so that the serrations mesh with each other, and push it further in the axial direction to start press fitting.
The press-fitting is finished when the butted portion of the outer joint member hits the annular convex edge of the hub wheel.
Manufacturing method of wheel bearing unit.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2006219424A JP4319208B2 (en) | 1998-08-26 | 2006-08-11 | Method for manufacturing drive wheel bearing unit |
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP24058398 | 1998-08-26 | ||
| JP2006219424A JP4319208B2 (en) | 1998-08-26 | 2006-08-11 | Method for manufacturing drive wheel bearing unit |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP11232985A Division JP2000135903A (en) | 1998-08-26 | 1999-08-19 | Bearing unit for driving wheel |
Related Child Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2006292840A Division JP4397921B2 (en) | 1998-08-26 | 2006-10-27 | Drive wheel bearing unit |
Publications (3)
| Publication Number | Publication Date |
|---|---|
| JP2006312459A JP2006312459A (en) | 2006-11-16 |
| JP2006312459A5 true JP2006312459A5 (en) | 2006-12-28 |
| JP4319208B2 JP4319208B2 (en) | 2009-08-26 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2006219424A Expired - Fee Related JP4319208B2 (en) | 1998-08-26 | 2006-08-11 | Method for manufacturing drive wheel bearing unit |
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| JP (1) | JP4319208B2 (en) |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| JP5098748B2 (en) * | 2008-03-28 | 2012-12-12 | 株式会社ジェイテクト | Wheel bearing device |
| JP2009248788A (en) * | 2008-04-08 | 2009-10-29 | Jtekt Corp | Bearing device for wheel |
| JP5623243B2 (en) * | 2010-11-05 | 2014-11-12 | Ntn株式会社 | Constant velocity universal joint |
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