JP4530291B2 - Method for manufacturing drive wheel bearing device - Google Patents

Method for manufacturing drive wheel bearing device Download PDF

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JP4530291B2
JP4530291B2 JP2007122508A JP2007122508A JP4530291B2 JP 4530291 B2 JP4530291 B2 JP 4530291B2 JP 2007122508 A JP2007122508 A JP 2007122508A JP 2007122508 A JP2007122508 A JP 2007122508A JP 4530291 B2 JP4530291 B2 JP 4530291B2
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joint member
wheel
outer joint
hub wheel
bearing
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JP2007261577A5 (en
JP2007261577A (en
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仁博 小澤
英児 田島
光 梅木田
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NTN Corp
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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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/64—Special methods of manufacture
    • 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
    • F16C19/187—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 all four raceways integrated on parts other than race rings, e.g. fourth 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
    • 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
    • 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
    • F16C19/527—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions related to vibration and noise
    • 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)
  • Manufacturing & Machinery (AREA)
  • Mounting Of Bearings Or Others (AREA)
  • Rolling Contact Bearings (AREA)

Description

本発明は、自動車等の駆動車輪を支持する駆動車輪用軸受装置の製造方法に関するもので、特に、ハブ輪と等速自在継手と複列の転がり軸受とをユニット化した駆動車輪用軸受装置の製造方法に関する。
The present invention relates to a process for the preparation of the driving wheel bearing equipment for supporting the drive wheels of an automobile or the like, in particular, the hub wheel and the constant velocity universal joint and a rolling bearing and a unitized drive wheel bearing instrumentation double row The present invention relates to a manufacturing method of a device.

ＦＲ車の後輪、ＦＦ車の前輪、あるいは４ＷＤ車の全輪といった自動車の駆動輪は、駆動車輪用軸受装置により懸架装置に支持する。近年、駆動車輪用軸受装置は軽量・コンパクト化を狙って、ハブ輪と等速自在継手と軸受部とをユニット化する傾向にある。  Driving wheels of automobiles such as rear wheels of FR vehicles, front wheels of FF vehicles, or all wheels of 4WD vehicles are supported on a suspension device by a bearing device for driving wheels. In recent years, bearing devices for drive wheels have a tendency to unitize a hub wheel, a constant velocity universal joint, and a bearing portion in order to reduce weight and size.

図６は従来の駆動車輪用軸受装置を示す縦断面図で、ハブ輪５０と、軸受部６０と、等速自在継手７０とをユニット化して構成している。ハブ輪５０は車輪（図示せず）を取り付けるための車輪取付フランジ５１を一体に有し、この車輪取付フランジ５１の円周等配位置には車輪を固定するためのハブボルト５２を植設している。  FIG. 6 is a longitudinal sectional view showing a conventional drive wheel bearing device, in which a hub wheel 50, a bearing portion 60, and a constant velocity universal joint 70 are formed as a unit. The hub wheel 50 integrally has a wheel mounting flange 51 for mounting a wheel (not shown), and a hub bolt 52 for fixing the wheel is implanted at a circumferentially equidistant position of the wheel mounting flange 51. Yes.

軸受部６０は外方部材６１と内方部材６２と複列の転動体６３、６３とからなり、外方部材６１は外周に車体（図示せず）に取り付けるための車体取付フランジ６４を一体に有し、内周には複列の転走面６１ａ、６１ａを形成している。一方、内方部材６２は、前記した外方部材６１の転走面６１ａ、６１ａに対向する複列の転走面５０ａ、７１ａを形成している。この一方の転走面５０ａはハブ輪５０の外周に一体形成し、他方の転走面７１ａは等速自在継手７０の外側継手部材７１の外周に一体形成している。複列の転動体６３、６３をこれら転走面６１ａ、５０ａと６１ａ、７１ａ間にそれぞれ収容し、保持器６５、６５で転動自在に保持している。この場合、内方部材６２はハブ輪５０と外側継手部材７１を指す。軸受部６０の端部にはシール６６、６７を装着し、軸受内部に封入した潤滑グリースの漏洩と、外部からの雨水やダスト等の侵入を防止している。  The bearing portion 60 includes an outer member 61, an inner member 62, and double-row rolling elements 63, 63. The outer member 61 is integrally provided with a vehicle body mounting flange 64 for mounting to a vehicle body (not shown) on the outer periphery. And the double-row rolling surfaces 61a and 61a are formed on the inner periphery. On the other hand, the inner member 62 forms double-row rolling surfaces 50a and 71a facing the rolling surfaces 61a and 61a of the outer member 61 described above. One rolling surface 50 a is integrally formed on the outer periphery of the hub wheel 50, and the other rolling surface 71 a is integrally formed on the outer periphery of the outer joint member 71 of the constant velocity universal joint 70. Double-row rolling elements 63 and 63 are accommodated between the rolling surfaces 61a and 50a and 61a and 71a, respectively, and are held by rollers 65 and 65 so as to be freely rollable. In this case, the inner member 62 refers to the hub wheel 50 and the outer joint member 71. Seals 66 and 67 are attached to the end portion of the bearing portion 60 to prevent leakage of lubricating grease sealed inside the bearing and intrusion of rainwater and dust from the outside.

等速自在継手７０は外側継手部材７１と図示しない継手内輪、ケージ、およびトルク伝達ボールとからなる。外側継手部材７１はカップ状のマウス部７２と、このマウス部７２から軸方向に延びる軸部７３を有し、マウス部７２の内周には軸方向に延びる曲線状のトラック溝７２ａを形成している。  The constant velocity universal joint 70 includes an outer joint member 71, a joint inner ring (not shown), a cage, and a torque transmission ball. The outer joint member 71 has a cup-shaped mouth portion 72 and a shaft portion 73 extending in the axial direction from the mouth portion 72, and a curved track groove 72 a extending in the axial direction is formed on the inner periphery of the mouth portion 72. ing.

中空に形成した外側継手部材７１の軸部７３をハブ輪５０に内嵌すると共に、ハブ輪５０の内周面に凹凸部５３を形成し、軸部７３を拡径してこの凹凸部５３に食い込ませ、その嵌合部を加締めてハブ輪５０と外側継手部材７１とを塑性結合させている。  The shaft portion 73 of the outer joint member 71 formed in a hollow shape is fitted into the hub wheel 50, the uneven portion 53 is formed on the inner peripheral surface of the hub wheel 50, the diameter of the shaft portion 73 is expanded, and the uneven portion 53 is formed. The hub wheel 50 and the outer joint member 71 are plastically coupled by biting and crimping the fitting portion.

前述の従来の駆動車輪用軸受装置では、セレーション等のトルク伝達手段に比べ嵌合部の緩みを防止でき、かつ嵌合部の摩耗を抑制することができるため、装置の耐久性と操縦安定性を向上させることができる。また、この結合部はトルク伝達手段と、ハブ輪と外側継手部材の結合手段とを併せ持つため、締結ナット等の固定手段が不要となり装置の一層の軽量・コンパクト化が達成できる。
特開２００１−１８６０５号公報 In the conventional drive wheel bearing device described above, the looseness of the fitting portion can be prevented and the wear of the fitting portion can be suppressed compared to torque transmission means such as serrations, so that the durability and handling stability of the device can be reduced. Can be improved. In addition, since this coupling portion has both the torque transmission means and the coupling means for the hub wheel and the outer joint member, a fixing means such as a fastening nut is not required, and the apparatus can be further reduced in weight and size.
Japanese Patent Laid-Open No. 2001-18605

しかしながら、こうした駆動車輪用軸受装置において、車両旋回時に過大な曲げモーメント荷重が生じた時、ハブ輪と外側継手部材との突き合せ部が節となって繰り返し曲げ荷重を受けることになる。この時、ハブ輪のインロウ部と外側継手部材の軸部、特に軸部の隅部に過大な応力が発生し、耐久性が低下する恐れがあった。また、繰り返し曲げ荷重によって、インロウ部や軸部が変形し、突合せ部に異常摩耗が発生する恐れがある。この摩耗によって摩耗粉が軸受内部に混入して寿命低下を招来する恐れもあった。  However, in such a drive wheel bearing device, when an excessive bending moment load is generated during turning of the vehicle, the butt portion between the hub wheel and the outer joint member becomes a node and receives a repeated bending load. At this time, excessive stress is generated in the in-row portion of the hub wheel and the shaft portion of the outer joint member, particularly in the corner portion of the shaft portion, and there is a fear that durability is lowered. Further, the in-brow part and the shaft part may be deformed by repeated bending loads, and abnormal wear may occur in the butt part. This wear may cause wear powder to enter the bearing and cause a reduction in service life.

本発明は、このような事情に鑑みてなされたもので、塑性結合により、装置の軽量・コンパクト化を図ると共に、こうした過大応力や摩耗の発生を抑制し、耐久性を向上させた駆動車輪用軸受装置の製造方法を提供することを目的としている。
The present invention has been made in view of such circumstances, and for a drive wheel that has improved durability by suppressing the occurrence of such excessive stress and wear while reducing the weight and size of the device by plastic bonding. and its object is to provide a method of manufacturing a bearing equipment.

係る目的を達成すべく、本発明は、車輪取付フランジを一端に有するハブ輪と、カップ状のマウス部、このマウス部の底部をなす肩部、この肩部から軸方向に延びる軸部をそれぞれ一体に有する中空状の外側継手部材を備える等速自在継手と、車体に対して車輪を回転自在に支承する複列の転がり軸受とをユニット化し、この複列の転がり軸受における内側転走面のうち一方を前記ハブ輪の外周面に、他方を前記外側継手部材の外周面にそれぞれ形成し、前記ハブ輪の端面を前記外側継手部材の肩部に衝合させて両部材を嵌合し、この嵌合部で、前記ハブ輪の内周面に硬化させた凹凸部を形成し、この凹凸部に前記外側継手部材の嵌合部を拡径させて食い込ませることにより、前記ハブ輪と前記外側継手部材とを一体に塑性結合した駆動車輪用軸受装置の製造方法において、前記ハブ輪を受け台に載置する工程と、マンドレルを前記外側継手部材のインボード側からアウトボード側方向に挿入して前記ハブ輪との嵌合部を拡径させる工程を備えた構成を採用した。In order to achieve such an object, the present invention includes a hub wheel having a wheel mounting flange at one end, a cup-shaped mouth portion, a shoulder portion forming the bottom portion of the mouth portion, and a shaft portion extending in the axial direction from the shoulder portion. A constant velocity universal joint having a hollow outer joint member integrally formed and a double row rolling bearing that rotatably supports the wheel with respect to the vehicle body are unitized, and the inner rolling surface of the double row rolling bearing is One of them is formed on the outer peripheral surface of the hub wheel, and the other is formed on the outer peripheral surface of the outer joint member, and the end surface of the hub wheel is abutted against the shoulder of the outer joint member to fit both members, By forming a hardened concave and convex portion on the inner peripheral surface of the hub wheel at the fitting portion, and expanding the biting portion of the outer joint member into the concave and convex portion, the hub wheel and the hub Drive wheel with plastic joint integrally with outer joint member Enlarged in the manufacturing method of the bearing device, a step of placing the cradle the wheel hub, the fitting portion between the hub wheel by inserting the mandrel from the inboard side of the outer joint member on the outboard side direction The structure provided with the process to make was adopted.

本発明の駆動車輪用軸受装置の製造方法は、受け台にハブ輪を載置し、マンドレルを外 側継手部材のインボード側からアウトボード側方向に挿入することによって、その押込力でハブ輪のインロウ部が、外側継手部材の肩部と受け台とで軸方向に圧縮され、この状態で嵌合部を拡径させるため、塑性結合後も圧縮応力が残留することになる。したがって、こうした塑性結合の際に、インロウ部と肩部との突き合せ部に軸方向のすきまは発生せず、複列の転がり軸受の内部すきまは当初設定した負すきまを維持することができる。Method for producing a driving wheel bearing apparatus of the present invention, by placing the wheel hub, inserting the mandrel from the inboard side of the outer-side joint member to the outboard side direction in the cradle, the hub wheel in the pushing force The in-row portion is compressed in the axial direction by the shoulder portion and the cradle of the outer joint member, and the fitting portion is expanded in this state, so that compressive stress remains even after plastic bonding. Therefore, during such plastic coupling, no axial clearance is generated at the butted portion of the inrow portion and the shoulder portion, and the internal clearance of the double row rolling bearing can maintain the initially set negative clearance.

以下、本発明の実施の形態を図面に基づいて詳細に説明する。図１は、本発明に係る駆動車輪用軸受装置の実施形態を示す縦断面図である。  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. FIG. 1 is a longitudinal sectional view showing an embodiment of a drive wheel bearing device according to the present invention.

この駆動車輪用軸受装置は、ハブ輪１と、複列の転がり軸受２と、等速自在継手３とをユニット化して構成している。なお、以下の説明では、車両に組み付けた状態で、車両の外側寄りとなる側をアウトボード側（図面左側）、中央寄り側をインボード側（図面右側）という。  This drive wheel bearing device comprises a hub wheel 1, a double row rolling bearing 2 and a constant velocity universal joint 3 as a unit. In the following description, the side closer to the outside of the vehicle in the state assembled to the vehicle is referred to as the outboard side (left side in the drawing), and the side closer to the center is referred to as the inboard side (right side in the drawing).

ハブ輪１は、アウトボード側の端部に車輪（図示せず）を取り付けるための車輪取付フランジ４を一体に有している。ハブ輪１の内周面には凹凸部５を形成し、熱処理によって表面硬さを５４〜６４ＨＲＣの範囲に硬化層１０を形成する（図中クロスハッチングにて示す）。熱処理としては、局部加熱ができ、硬化層深さの設定が比較的容易にできる高周波誘導加熱による焼入れが好適である。   The hub wheel 1 integrally has a wheel mounting flange 4 for mounting a wheel (not shown) at an end portion on the outboard side. Concave and convex portions 5 are formed on the inner peripheral surface of the hub wheel 1, and a hardened layer 10 is formed with a surface hardness in the range of 54 to 64 HRC by heat treatment (indicated by cross-hatching in the figure). As the heat treatment, local heating is preferable, and quenching by high-frequency induction heating that can set the hardened layer depth relatively easily is preferable.

なお、凹凸部５は、図２に示すような複数列の溝を直交させた形状を例示することができる。（ａ）は互いに傾斜した螺旋溝６で、（ｂ）は軸方向溝と独立した環状溝との交叉溝６’でアヤメローレット状を形成することができる。また、凹凸部５の凸部は良好な食い込み性を確保するために、三角形状等の尖塔形状に形成する。  In addition, the uneven | corrugated | grooved part 5 can illustrate the shape which orthogonally crossed the groove | channel of several rows as shown in FIG. (A) is a spiral groove 6 inclined with respect to each other, and (b) is a crossed groove 6 ′ of an annular groove independent of an axial groove, and an iris knurl can be formed. Moreover, the convex part of the uneven part 5 is formed in a spire shape such as a triangular shape in order to ensure good bite.

複列の転がり軸受２は、外方部材７と内方部材８と複列の転動体９、９とからなり、外方部材７は外周に車体（図示せず）に取り付けるための車体取付フランジ７ａを一体に有し、内周には複列の外側転走面７ｂ、７ｂを形成している。一方、内方部材８は、ハブ輪１と後述する外側継手部材１４を指し、外方部材７の外側転走面７ｂ、７ｂに対向するアウトボード側の内側転走面１ａをハブ輪１の外周に、またインボード側の内側転走面１４ａを外側継手部材１４の外周にそれぞれ形成している。複列の転動体９、９をこれら転走面７ｂ、１ａと７ｂ、１４ａ間にそれぞれ収容し、保持器１１、１１で転動自在に保持している。複列の転がり軸受２の端部にはシール１２、１３を装着し、軸受内部に封入した潤滑グリースの漏洩と、外部からの雨水やダスト等の侵入を防止している。  The double-row rolling bearing 2 includes an outer member 7, an inner member 8, and double-row rolling elements 9, 9. The outer member 7 is a vehicle body mounting flange for mounting to the vehicle body (not shown) on the outer periphery. 7a is integrally formed, and double row outer rolling surfaces 7b and 7b are formed on the inner periphery. On the other hand, the inner member 8 refers to the hub wheel 1 and an outer joint member 14 to be described later. The inner rolling surface 1a on the outboard side facing the outer rolling surfaces 7b and 7b of the outer member 7 is connected to the hub wheel 1. An inner rolling surface 14a on the inboard side is formed on the outer periphery and on the outer periphery of the outer joint member 14, respectively. Double row rolling elements 9, 9 are accommodated between the rolling surfaces 7b, 1a and 7b, 14a, respectively, and are held by the retainers 11, 11 so as to be freely rollable. Seals 12 and 13 are attached to the ends of the double-row rolling bearing 2 to prevent leakage of lubricating grease sealed inside the bearing and intrusion of rainwater and dust from the outside.

ハブ輪１において、図３（ａ）に示すように、シール１２のシールリップが摺接するシールランド部１８、内側転走面１ａ、および外側継手部材１４の肩部１６と当接するインロウ部１ｂの表面、さらにはこのインロウ部１ｂの端面１９に高周波焼入れによって硬化層１０’を形成している（図中クロスハッチングにて示す）。  In the hub wheel 1, as shown in FIG. 3A, the seal land portion 18 in which the seal lip of the seal 12 is in sliding contact, the inner rolling surface 1 a, and the inrow portion 1 b in contact with the shoulder portion 16 of the outer joint member 14. A hardened layer 10 ′ is formed on the surface and further on the end face 19 of the in-row part 1 b by induction hardening (indicated by cross-hatching in the figure).

図３（ｂ）にインロウ部１ｂの端部を拡大して示しているが、硬化層１０’は端面１９およびインロウ部１ｂの端部内径にまで一部達するように設定している。これによって、円筒面で嵌合するインロウ部１ｂと後述する外側継手部材１４の小径段部１７ａとの摩耗を抑制することができる。さらに、インロウ部１ｂの端面１９には、内径側にグリース溜まり部２０を形成している。ここでは端面１９に凹部を形成した形状を例示しているが、これに限らず、例えば内径側に大きな面取りを形成してグリース溜まり部としても良い。ここで複列の転がり軸受２は転動体９、９をボールとした複列アンギュラ玉軸受を例示したが、これに限らず転動体に円すいころを使用した複列円すいころ軸受であっても良い。  FIG. 3B shows an enlarged end portion of the in-row portion 1b. The hardened layer 10 'is set so as to partially reach the end surface 19 and the inner end portion of the in-row portion 1b. As a result, it is possible to suppress wear between the in-row portion 1b fitted on the cylindrical surface and the small-diameter step portion 17a of the outer joint member 14 described later. Further, a grease reservoir portion 20 is formed on the inner diameter side of the end surface 19 of the in-row portion 1b. Here, the shape in which the concave portion is formed on the end surface 19 is illustrated, but the shape is not limited to this, and for example, a large chamfer may be formed on the inner diameter side to form the grease reservoir portion. Here, the double-row rolling bearing 2 is exemplified as a double-row angular ball bearing in which the rolling elements 9 and 9 are balls. However, the double-row rolling bearing 2 is not limited thereto, and may be a double-row tapered roller bearing using a tapered roller as the rolling element. .

ハブ輪１の端面１９と外側継手部材１４の肩部１６との衝合面にグリースを介在させたので、突き合せ部の摩耗を抑制すると共に、外側継手部材１４を介してトルクを伝達する際、外側継手部材１４の軸部１７が捩じれ、ハブ輪１の端面１９との間で相対滑り音、所謂スティックスリップ音が発生するのを抑制することができる。また、ハブ輪１の端面１ ９にグリース溜まり部２０を設けることによって、摩耗とスティックスリップ音発生をさらに抑制することができる。Since grease is interposed abutment surface of the shoulder portion 16 of the end face 19 and the outer joint member 14 of the hub wheel 1, thereby suppressing the abrasion of the butt portion, when transmitting torque through the outer joint member 14 In addition, the shaft portion 17 of the outer joint member 14 is twisted, so that it is possible to suppress the generation of relative slip noise, so-called stick-slip noise, with the end surface 19 of the hub wheel 1 . Further, by providing the end face 1 9 grease reservoir portion 20 of the hub wheel 1, it is possible to further suppress the wear and stick-slip sound generation.

ハブ輪１の内側転走面１ａから軸方向に延びる円筒状のインロウ部１ｂを形成し、このインロウ部１ｂを含み、内側転走面１ａから端面１９に至る表面に硬化層１０を形成したので、過大な曲げモーメント荷重においても充分な耐久性を有すると共に、繰り返し曲げ荷重で端面１９が摩耗し、その摩耗粉が軸受内部に侵入して軸受寿命を低下させることはない。また、ハブ輪１の端面１９からインロウ部１ｂの端部内径に至る表面に硬化層１０を形成すれば、このインロウ部１ｂと円筒面で嵌合する外側継手部材１４の軸部１７との摩耗が抑制される。The cylindrical in-row part 1b extending in the axial direction from the inner raceway surface 1a of the hub wheel 1 is formed, and the hardened layer 10 is formed on the surface from the inner raceway surface 1a to the end face 19 including the in-row part 1b . Even when the bending moment load is excessive, it has sufficient durability, and the end face 19 is worn by repeated bending loads, and the wear powder does not enter the inside of the bearing to reduce the bearing life. Further, by forming the hardened layer 10 on the surface extending to the end inner diameter of the spigot portion 1b from the end face 19 of the hub wheel 1, the wear of the shaft portion 17 of the outer joint member 14 to be fitted in the spigot portion 1b and the cylindrical surface Is suppressed.

等速自在継手３は、図５に示すように、外側継手部材１４と図示しない継手内輪、ケージ、およびトルク伝達ボールとを備えている。外側継手部材１４はカップ状のマウス部１５と、このマウス部１５の底部をなす肩部１６と、この肩部１６から軸方向に延びる軸部１７を有し、マウス部１５の内周には軸方向に延びる曲線状のトラック溝１５ａを形成している。As shown in FIG. 5, the constant velocity universal joint 3 includes an outer joint member 14, a joint inner ring (not shown), a cage, and a torque transmission ball. The outer joint member 14 has a cup-shaped mouth portion 15, a shoulder portion 16 that forms the bottom portion of the mouth portion 15, and a shaft portion 17 that extends from the shoulder portion 16 in the axial direction. A curved track groove 15a extending in the axial direction is formed.

外側継手部材１４を中空に形成し、この肩部１６の外周には前記した内側転走面１４ａを形成している。また、外側継手部材１４の軸部１７は小径段部１７ａと嵌合部１７ｂを有している。小径段部１７ａに圧入したハブ輪１のインロウ部１ｂの端面１９を、外側継手部材１４の肩部１６に突合せ、嵌合部１７ｂをハブ輪１に内嵌する。その後この嵌合部１７ｂの内径にマンドレルを挿入・抜脱させる等、適宜な手段で嵌合部１７ｂを拡径してハブ輪１の凹凸部５に食い込ませ、ハブ輪１と外側継手部材１４とを塑性結合させる。これにより、この結合部はトルク伝達手段と、ハブ輪１と外側継手部材１４の結合手段とを併せ持つため、従来のセレーション等のトルク伝達手段をハブ輪１や外側継手部材１４に形成する必要はなく、また、締結ナット等の固定手段も不要となるため、装置の一層の軽量・コンパクト化を実現することができる。また、こうした塑性結合によって装置の軽量・コンパクト化が図れると共に、車両旋回時に過大な曲げモーメント荷重が生じても、外側継手部材１４の軸部１７、また軸部１７の隅部に過大な応力が発生するのを抑制することができ、充分な耐久性を有している。The outer joint member 14 is formed in a hollow shape, and the inner rolling surface 14 a described above is formed on the outer periphery of the shoulder portion 16. The shaft portion 17 of the outer joint member 14 has a small diameter step portion 17a and a fitting portion 17b. The end surface 19 of the inrow portion 1b of the hub wheel 1 press-fitted into the small diameter step portion 17a is abutted against the shoulder portion 16 of the outer joint member 14, and the fitting portion 17b is fitted into the hub wheel 1. Thereafter, the fitting portion 17b is expanded in diameter by an appropriate means such as inserting / withdrawing a mandrel into / from the inner diameter of the fitting portion 17b, so that the concave / convex portion 5 of the hub wheel 1 is bitten into the hub wheel 1 and the outer joint member 14. And are plastically connected. As a result, since this coupling portion has both the torque transmission means and the coupling means for the hub wheel 1 and the outer joint member 14, it is necessary to form torque transmission means such as conventional serrations on the hub wheel 1 and the outer joint member 14. In addition, since fixing means such as a fastening nut is not required, the apparatus can be further reduced in weight and size. In addition, the plastic connection can reduce the weight and size of the device, and even if an excessive bending moment load occurs when the vehicle turns, excessive stress is applied to the shaft portion 17 of the outer joint member 14 and the corner portion of the shaft portion 17. Generation | occurrence | production can be suppressed and it has sufficient durability.

また、図４（ａ）（ｂ）に示すように、受け台Ｂに内方部材８を構成するハブ輪１を載置し、マンドレルＭを外側継手部材１４のインボード側からアウトボード側方向に挿入することによって、その押込力でハブ輪１のインロウ部１ｂが、外側継手部材１４の肩部１６と受け台Ｂとで軸方向に圧縮され、この状態で嵌合部１７ｂ（クロスハッチング部）を拡径させるため、塑性結合後も圧縮応力が残留することになる。したがって、こうした塑性結合の際に、インロウ部１ｂと肩部１６との突き合せ部に軸方向のすきまは発生せず、複列の転がり軸受２の内部すきまは当初設定した負すきまを維持することができる。4A and 4B, the hub wheel 1 constituting the inner member 8 is placed on the cradle B, and the mandrel M is moved from the inboard side of the outer joint member 14 to the outboard side direction. The inrow portion 1b of the hub wheel 1 is compressed in the axial direction by the shoulder portion 16 and the cradle B of the outer joint member 14 by the pushing force, and in this state, the fitting portion 17b (cross-hatching portion) is compressed. ) Is expanded, compressive stress remains after plastic bonding. Therefore, at the time of such plastic coupling, there is no axial clearance at the butted portion of the inrow portion 1b and the shoulder portion 16, and the internal clearance of the double row rolling bearing 2 maintains the initially set negative clearance. Can do.

外側継手部材１４において、図５に示すように、マウス部１５の内周に形成したトラック溝１５ａと、シール１３が摺接するシールランド部２１から内側転走面１４ａ、および軸部１７の小径段部１７ａに亙って表面に硬化層１０”を形成している。硬化処理として高周波誘導加熱による焼入れが好適である。また、拡径する嵌合部１７ｂは、鍛造後の素材表面硬さ２４ＨＲＣ以下の未焼入れ部とし、前記したハブ輪１の凹凸部５の表面硬さ５４〜６４ＨＲＣとの硬度差を３０ＨＲＣ以上に設定するのが好ましい。これにより、嵌合部１７ｂが凹凸部５に容易に、かつ深く食い込み、凹凸部５の先端が潰れることなく強固に両者を塑性結合することができる。In the outer joint member 14, as shown in FIG. 5, a track groove 15 a formed in the inner periphery of the mouth portion 15, a seal land portion 21 in sliding contact with the seal 13, an inner rolling surface 14 a, and a small diameter step of the shaft portion 17. A hardened layer 10 ″ is formed on the surface over the portion 17a. Quenching by high-frequency induction heating is suitable as the hardening treatment. Further, the fitting portion 17b whose diameter is expanded has a material surface hardness after forging of 24 HRC. It is preferable to set the following unquenched portion, and set the hardness difference between the surface hardness 54 to 64 HRC of the uneven portion 5 of the hub wheel 1 to 30 HRC or more. In addition, it is possible to deeply bite and firmly plastically bond both of them without collapsing the tip of the uneven portion 5.

車両旋回時に過大な曲げモーメント荷重が生じた時、ハブ輪１と外側継手部材１４との突き合せ部が節となって繰り返し曲げ荷重を受けることになる。この時、ハブ輪１のインロウ部１ｂと外側継手部材１４の軸部１７、特に小径段部１７ａの隅部２２には過大な応力が発生し、耐久性が低下する恐れがある。また、繰り返し曲げ荷重によって、インロウ部１ｂや小径段部１７ａが変形して突合せ部に異常摩耗が発生し、軸受内部にその摩耗粉が混入して寿命低下を招来する恐れもある。しかし、本実施形態のように、内側転走面１４ａから隅部２２を含む小径段部１７ａの表面に硬化層１０”を形成することによって、捩じりトルクに対して強度、耐久性が向上すると共に、繰り返し曲げ荷重によってインロウ部１ｂと肩部１６の突き合せ部に相対滑りが生じても、摩耗の発生を抑制することができる。  When an excessive bending moment load is generated during turning of the vehicle, the butt portion between the hub wheel 1 and the outer joint member 14 becomes a node and receives a repeated bending load. At this time, excessive stress is generated in the in-row part 1b of the hub wheel 1 and the shaft part 17 of the outer joint member 14, particularly the corner part 22 of the small-diameter stepped part 17a, and the durability may be reduced. In addition, due to repeated bending loads, the inlay portion 1b and the small-diameter step portion 17a are deformed and abnormal wear occurs in the butt portion, and the wear powder may enter the inside of the bearing, leading to a decrease in the service life. However, the strength and durability against torsional torque are improved by forming the hardened layer 10 ″ on the surface of the small diameter step portion 17a including the corner portion 22 from the inner rolling surface 14a as in this embodiment. In addition, the occurrence of wear can be suppressed even if relative slip occurs in the butted portion of the inrow portion 1b and the shoulder portion 16 due to repeated bending loads.

図示はしていないが、中空状の外側継手部材１４の内径にエンドキャップを装着して、マウス部１５に封入された潤滑グリースの外部への漏洩と外部からのダスト侵入を防止している。  Although not shown, an end cap is attached to the inner diameter of the hollow outer joint member 14 to prevent leakage of the lubricating grease sealed in the mouth portion 15 to the outside and dust intrusion from the outside.

ハブ輪１のインロウ部１ｂと外側継手部材１４の小径段部１７ａは、それぞれ円筒面で嵌合し、繰り返し曲げ荷重に対して充分な剛性を有している。通常、嵌合するためのこの種のインロウ部には０．５〜１．０ｍｍの径方向すきまを設け、組込みの際の案内面とするのが一般的であるが、本実施形態では、組込み性を若干犠牲にし、この径方向すきまを可能な限り小さく設定している。インロウ部１ｂや小径段部１７ａの加工の工程能力、および耐久試験結果から、この嵌合部の径方向すきまを若干の締代も含む０．５ｍｍ〜−０．１ｍｍ、好ましくは０．３５〜−０．０５ｍｍに設定すれば耐久性向上に効果的であることを検証した。  The in-row portion 1b of the hub wheel 1 and the small-diameter step portion 17a of the outer joint member 14 are fitted on a cylindrical surface, and have sufficient rigidity against repeated bending loads. Normally, this type of in-row part for fitting is generally provided with a radial clearance of 0.5 to 1.0 mm as a guide surface during assembly. This radial clearance is set as small as possible, with a slight sacrifice in performance. From the processing capability of the in-row part 1b and the small-diameter stepped part 17a and the durability test results, the radial clearance of this fitting part includes 0.5 mm to -0.1 mm, preferably 0.35, including some tightening allowance. It was verified that setting to -0.05 mm is effective in improving durability.

ハブ輪１のインロウ部１ｂと外側継手部材１４の軸部１７との径方向すきまを０．５ｍｍ以下に設定した。これにより、繰り返し曲げ荷重に対し、インロウ部１ｂの変形を抑制し、その荷重を円筒面で確実に受けることができるので、装置の耐久性を格段に向上させることができる。The radial clearance between the in-row part 1b of the hub wheel 1 and the shaft part 17 of the outer joint member 14 was set to 0.5 mm or less. Thereby, it is possible to suppress the deformation of the in-row part 1b with respect to repeated bending loads, and to reliably receive the load on the cylindrical surface, so that the durability of the apparatus can be significantly improved.

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

本発明に係る駆動車輪用軸受装置の製造方法は、ハブ輪と等速自在継手と複列の転がり軸受とをユニット化した駆動車輪用軸受装置の製造方法に適用できる。  The drive wheel bearing device manufacturing method according to the present invention can be applied to a drive wheel bearing device manufacturing method in which a hub wheel, a constant velocity universal joint, and a double row rolling bearing are unitized.

本発明に係る駆動車輪用軸受装置の実施形態を示す縦断面図である。It is a longitudinal section showing an embodiment of a bearing device for drive wheels concerning the present invention. （ａ）は本発明に係るハブ輪の凹凸部形状を示す縦断面図で、互いに傾斜した螺旋溝で構成したアヤメローレット形状を示す。 （ｂ）は同上、軸方向溝と独立した環状溝との交叉溝で構成したアヤメローレット形状を示す。(A) is a longitudinal cross-sectional view which shows the uneven | corrugated | grooved part shape of the hub ring which concerns on this invention, and shows the iris knurl shape comprised by the mutually inclined helical groove. (B) shows the iris knurl shape comprised by the crossing groove | channel of an annular groove independent of an axial direction groove | channel same as the above. （ａ）は、本発明に係る駆動車輪用軸受装置のハブ輪の縦断面図である。 （ｂ）は、（ａ）の要部拡大断面図である。(A) is a longitudinal cross-sectional view of the hub wheel of the bearing apparatus for drive wheels which concerns on this invention. (B) is a principal part expanded sectional view of (a). （ａ）は、本発明に係る駆動車輪用軸受装置の塑性結合方法を示す説明図である。 （ｂ）は、（ａ）の要部拡大図である。(A) is explanatory drawing which shows the plastic coupling method of the bearing apparatus for drive wheels which concerns on this invention. (B) is the principal part enlarged view of (a). 本発明に係る駆動車輪用軸受装置の外側継手部材の縦断面図である。It is a longitudinal cross-sectional view of the outer joint member of the bearing apparatus for drive wheels which concerns on this invention. 従来の駆動車輪用軸受装置を示す縦断面図である。It is a longitudinal cross-sectional view which shows the conventional bearing apparatus for drive wheels.

符号の説明Explanation of symbols

１・・・・・・・・・・・・ハブ輪
１ａ、１４ａ・・・・・・・内側転走面
１ｂ・・・・・・・・・・・インロウ部
２・・・・・・・・・・・・複列の転がり軸受
３・・・・・・・・・・・・等速自在継手
４・・・・・・・・・・・・車輪取付フランジ
５・・・・・・・・・・・・凹凸部
６、６’・・・・・・・・・・溝
７・・・・・・・・・・・・外方部材
７ａ・・・・・・・・・・・車体取付フランジ
７ｂ・・・・・・・・・・・外側転走面
８・・・・・・・・・・・・内方部材
９・・・・・・・・・・・・転動体
１０、１０’、１０”・・・・硬化層
１１・・・・・・・・・・・保持器
１２、１３・・・・・・・・シール
１４・・・・・・・・・・・外側継手部材
１５・・・・・・・・・・・マウス部
１５ａ・・・・・・・・・・トラック溝
１６・・・・・・・・・・・肩部
１７・・・・・・・・・・・軸部
１７ａ・・・・・・・・・・小径段部
１７ｂ・・・・・・・・・・嵌合部
１８、２１・・・・・・・・シールランド部
１９・・・・・・・・・・・端面
２０・・・・・・・・・・・グリース溜まり部
２２・・・・・・・・・・・隅部
５０・・・・・・・・・・・ハブ輪
５０ａ、６１ａ、７１ａ・・転走面
５１・・・・・・・・・・・車輪取付フランジ
５２・・・・・・・・・・・ハブボルト
５３・・・・・・・・・・・凹凸部
６０・・・・・・・・・・・軸受部
６１・・・・・・・・・・・外方部材
６２・・・・・・・・・・・内方部材
６３・・・・・・・・・・・転動体
６４・・・・・・・・・・・車体取付フランジ
６５・・・・・・・・・・・保持器
６６、６７・・・・・・・・シール
７０・・・・・・・・・・・等速自在継手
７１・・・・・・・・・・・外側継手部材
７２・・・・・・・・・・・マウス部
７２ａ・・・・・・・・・・トラック溝
７３・・・・・・・・・・・軸部
Ｂ・・・・・・・・・・・・受け台
Ｍ・・・・・・・・・・・・マンドレル

1. Hub wheel 1a, 14a ... Inner rolling surface 1b ... In-row part 2 ... ········ Double row rolling bearing 3 ··············································· Wheel mounting flange 5 ········ Uneven portion 6, 6 '········································ · · Body mounting flange 7b · · · Outer rolling surface 8 · · · · · Inner member 9 ··· Rolling elements 10, 10 ', 10 "... Hardened layer 11 ... Cage 12, 13 ... Seal 14 ... ... Outer joint member 15 ... Mouse part 15a ... Truck Groove 16 ... shoulder 17 ... shaft 17a ... small diameter step 17b ... ······ Fitting portions 18, 21 ······· Seal land portion 19 ···································································・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Corner 50 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Hub wheels 50a, 61a, 71a ・ ・ Rolling surface 51 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Wheel Mounting flange 52 ········································································ ... outer member 62 ... inner member 63 ... rolling element 64 ... car body Mounting flange 65 ... Cage 66, 67 ...・ ・ ・ ・ ・ Seal 70 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Constant velocity universal joint 71 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Outer joint member 72 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Mouse Part 72a ... Track groove 73 ... Shaft part B ... Base M ... .... Mandrels

Claims (1)

車輪取付フランジを一端に有するハブ輪と、カップ状のマウス部、このマウス部の底部をなす肩部、この肩部から軸方向に延びる軸部をそれぞれ一体に有する中空状の外側継手部材を備える等速自在継手と、車体に対して車輪を回転自在に支承する複列の転がり軸受とをユニット化し、この複列の転がり軸受における内側転走面のうち一方を前記ハブ輪の外周面に、他方を前記外側継手部材の外周面にそれぞれ形成し、前記ハブ輪の端面を前記外側継手部材の肩部に衝合させて両部材を嵌合し、この嵌合部で、前記ハブ輪の内周面に硬化させた凹凸部を形成し、この凹凸部に前記外側継手部材の嵌合部を拡径させて食い込ませることにより、前記ハブ輪と前記外側継手部材とを一体に塑性結合した駆動車輪用軸受装置の製造方法において、
前記ハブ輪を受け台に載置する工程と、マンドレルを前記外側継手部材のインボード側からアウトボード側方向に挿入して前記ハブ輪との嵌合部を拡径させる工程を備えたことを特徴とする駆動車輪用軸受装置の製造方法。
A hub wheel having a wheel mounting flange at one end, a cup-shaped mouth portion, a shoulder portion forming the bottom portion of the mouth portion, and a hollow outer joint member integrally including a shaft portion extending in the axial direction from the shoulder portion are provided. A constant velocity universal joint and a double row rolling bearing that rotatably supports a wheel with respect to the vehicle body are unitized, and one of the inner rolling surfaces of the double row rolling bearing is an outer peripheral surface of the hub wheel. The other is formed on the outer peripheral surface of the outer joint member, the end surface of the hub ring is abutted against the shoulder of the outer joint member, and the two members are fitted together. A drive in which the hub wheel and the outer joint member are integrally plastically bonded by forming a hardened concave and convex portion on the peripheral surface and expanding the fitting portion of the outer joint member into the concave and convex portion. In the manufacturing method of the wheel bearing device,
Placing the hub wheel on a cradle, and inserting a mandrel from the inboard side of the outer joint member in the outboard side direction to expand the fitting portion with the hub wheel. A manufacturing method of a bearing device for a drive wheel, which is characterized.
JP2007122508A 2007-05-07 2007-05-07 Method for manufacturing drive wheel bearing device Expired - Fee Related JP4530291B2 (en)

Priority Applications (1)

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Publication number Priority date Publication date Assignee Title
JP5323337B2 (en) * 2007-10-15 2013-10-23 Ｎｔｎ株式会社 Wheel bearing device
DE112008002714T5 (en) 2007-10-15 2010-10-07 NTN Corporation, Osaka-shi Bearing device for a wheel
JP5323339B2 (en) * 2007-10-17 2013-10-23 Ｎｔｎ株式会社 Wheel bearing device
JP5323338B2 (en) * 2007-10-17 2013-10-23 Ｎｔｎ株式会社 Wheel bearing device
JP2010047042A (en) * 2008-08-19 2010-03-04 Ntn Corp Bearing device for driving wheel

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001018605A (en) * 1999-07-06 2001-01-23 Ntn Corp Bearing device for driving wheel
JP2002106592A (en) * 2000-09-29 2002-04-10 Koyo Seiko Co Ltd Bearing device for axle

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Publication number Priority date Publication date Assignee Title
JP3849240B2 (en) * 1997-05-09 2006-11-22 日本精工株式会社 Rolling bearing unit for wheels

Patent Citations (2)

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Publication number Priority date Publication date Assignee Title
JP2001018605A (en) * 1999-07-06 2001-01-23 Ntn Corp Bearing device for driving wheel
JP2002106592A (en) * 2000-09-29 2002-04-10 Koyo Seiko Co Ltd Bearing device for axle

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