JP2006132711A - Method of manufacturing hub unit for supporting wheel - Google Patents

Method of manufacturing hub unit for supporting wheel Download PDF

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Publication number
JP2006132711A
JP2006132711A JP2004323928A JP2004323928A JP2006132711A JP 2006132711 A JP2006132711 A JP 2006132711A JP 2004323928 A JP2004323928 A JP 2004323928A JP 2004323928 A JP2004323928 A JP 2004323928A JP 2006132711 A JP2006132711 A JP 2006132711A
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load
collision
caulking
mold
hub
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JP2006132711A5 (en
Inventor
Nobuyuki Hagiwara
信行 萩原
Eiichi Kitabayashi
栄一 北林
Chitose Konishi
知戸世 小西
Kazumasa Hasegawa
和昌 長谷川
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NSK Ltd
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NSK Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
    • B21J9/00—Forging presses
    • B21J9/02—Special design or construction
    • B21J9/025—Special design or construction with rolling or wobbling dies
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21K—MAKING FORGED OR PRESSED METAL PRODUCTS, e.g. HORSE-SHOES, RIVETS, BOLTS OR WHEELS
    • B21K25/00—Uniting components to form integral members, e.g. turbine wheels and shafts, caulks with inserts, with or without shaping of the components
    • 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
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/38—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers
    • F16C19/383—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • F16C19/385—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings
    • F16C19/386—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings in O-arrangement
    • 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

Abstract

<P>PROBLEM TO BE SOLVED: To stabilize service life of a metal mold by reducing damage of the metal mold by collision, by determining conditions of "collision load" and "set load". <P>SOLUTION: As a ratio (P1/P0) of "collision load (P1)" and "set load (P0)" is determined to be 1-1.3 when a hollow projecting portion at an inner end portion of a hub main body, axially projecting from an inner end face of an inner ring externally fitted to a step portion of the hub main body is caulked toward a radial outer portion, the damage of the metal mold caused by collision can be reduced, and the service life of the metal mold can be stabilized. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

本発明は、自動車の車輪を懸架装置に対して回転自在に支持する車輪支持用ハブユニットに於いて、加締めを行う車輪支持用ハブユニットの製造方法に関する。   The present invention relates to a method for manufacturing a wheel support hub unit that performs caulking in a wheel support hub unit that rotatably supports a vehicle wheel with respect to a suspension device.

自動車の車輪を懸架装置に対して回転自在に支持するため、特許文献１に開示してあるように、車輪支持用転がり軸受ユニットを使用している。   In order to rotatably support the wheel of an automobile with respect to a suspension device, as disclosed in Patent Document 1, a wheel bearing rolling bearing unit is used.

図５は、車輪支持用転がり軸受ユニットの断面図である。外輪１の内径側に、転動体である複数の円錐ころ３，３を介して、ハブ２が回転自在に支持してある。外輪１の内周面には、１対の外輪軌道４，４が形成してあると共に、外周面には、懸架装置に支持固定するための取付部５が設けてある。   FIG. 5 is a cross-sectional view of the wheel-supporting rolling bearing unit. A hub 2 is rotatably supported on the inner diameter side of the outer ring 1 via a plurality of tapered rollers 3 and 3 that are rolling elements. A pair of outer ring raceways 4, 4 are formed on the inner peripheral surface of the outer ring 1, and an attachment portion 5 for supporting and fixing to the suspension device is provided on the outer peripheral surface.

ハブ２は、軸部材であるハブ本体６と、一対の内輪７，７とを組み合わせてなる。ハブ本体６は、車輪を支持するためのフランジ８を外周面の外端（図５の左方）部に形成している。   The hub 2 is a combination of a hub body 6 that is a shaft member and a pair of inner rings 7 and 7. The hub body 6 has a flange 8 for supporting the wheel formed on the outer end (left side in FIG. 5) of the outer peripheral surface.

ハブ本体６には、小径の段部１０が形成してある。この段部１０には、夫々内輪軌道９ａ，９ｂを有する一対の内輪７ａ，７ｂが圧入・嵌合してある。   The hub body 6 is formed with a step portion 10 having a small diameter. A pair of inner rings 7a and 7b having inner ring raceways 9a and 9b are press-fitted and fitted to the stepped portion 10, respectively.

一方の内輪７ｂは、ハブ本体６の内端部に設けた加締め部１１により、段部１０に向けて押圧してある。   One inner ring 7 b is pressed toward the stepped portion 10 by a caulking portion 11 provided at the inner end portion of the hub body 6.

この加締め部１１は、ハブ本体６の内端部であって、段部１０に圧入・外嵌した内輪７ｂの内端面よりも軸方向に突出する部分の中空突出部１３を、揺動プレス装置により、径方向外方に向けて、ローリング加締め加工して、形成してある。   The caulking portion 11 is an inner end portion of the hub body 6, and a hollow projecting portion 13, which protrudes in the axial direction from the inner end surface of the inner ring 7 b press-fitted and externally fitted to the stepped portion 10, It is formed by rolling caulking toward the outside in the radial direction by the apparatus.

このようなローリング加締め加工では、ワークには金型を介して荷重（力）が加わる。加工開始直後、金型とワークが衝突すると、金型は、準静的または静的な荷重（Fstatic＝Ｐ０）に加えて、慣性力による荷重（ΔFinertia）を受ける。慣性力による荷重は次式で表せる。
ΔFinertia＝Ｍ・Ｖ／Δｔ
Ｍ：質量（機械本体に対して動く側、本明細書ではワーク側の昇降する部分）
Ｖ：相対速度（本明細書ではワーク側の装置が金型に近づく速さ）
Δｔ：相対速度がＶからゼロになるまでの時間
本明細書において準静的または静的な荷重（Fstatic＝Ｐ０）を「設定荷重」と呼ぶことにし、設定荷重に慣性力を加えた荷重（Fstatic＋ΔFinertia＝Ｐ１）を「衝突荷重」と呼ぶことにする。 In such rolling caulking, a load (force) is applied to the work through a mold. When the mold collides with the workpiece immediately after the start of machining, the mold receives a load (ΔFinertia) due to inertial force in addition to a quasi-static or static load (Fstatic = P0). The load due to inertial force can be expressed by the following equation.
ΔFinertia = MVV / Δt
M: Mass (the moving side with respect to the machine body, in this specification, the part that moves up and down on the workpiece side)
V: Relative speed (in this specification, the speed at which the device on the workpiece side approaches the mold)
Δt: Time until the relative speed becomes zero from V In this specification, a quasi-static or static load (Fstatic = P0) is referred to as a “set load”, and a load obtained by adding an inertial force to the set load ( Fstatic + ΔFinertia = P1) will be referred to as “impact load”.

従来、ローリング加締め加工においては、「設定荷重」についでは管理していたが、「衝突荷重」については管理していなかった。すなわち、慣性力による荷重については、考慮されていなかった。
特開２００３−７４５７１号公報 Conventionally, in rolling caulking, the “set load” was managed, but the “collision load” was not managed. That is, the load due to inertial force was not taken into consideration.
JP 2003-74571 A

ところが、同じ「設定荷重」でも、あるレベルより「衝突荷重」が高いと、金型表面は、ワークと衝突する個所が損傷して、金型の寿命が短くなるという問題が発生した。   However, even if the “set load” is the same, if the “collision load” is higher than a certain level, there is a problem in that the mold surface is damaged at the location where it collides with the workpiece, and the life of the mold is shortened.

本発明は、上述したような事情に鑑みてなされたものであって、「衝突荷重」と「設定荷重」の条件を設定することによって、衝突による金型の損傷を減少して、金型の寿命を安定することができる、車輪支持用ハブユニットの製造方法を提供することを目的とする。   The present invention has been made in view of the above-described circumstances, and by setting the conditions of “impact load” and “set load”, damage to the mold due to the collision is reduced, and the mold It is an object of the present invention to provide a method for manufacturing a wheel-supporting hub unit that can stabilize the service life.

上記の目的を達成するため、本発明の請求項１に係る車輪支持用ハブユニットの製造方法は、ハブ本体の内端部であり、ハブ本体の段部に外嵌した内輪の内端面よりも軸方向内方に突出する中空突出部を、径方向外方に向けて加締め加工する車輪支持用ハブユニットの製造方法に於いて、
前記加締め加工時、「衝突荷重（Ｐ１）」／「設定荷重（Ｐ０）」の比（Ｐ１／Ｐ０）は、１〜１．３に設定してあることを特徴とする。 In order to achieve the above object, a method for manufacturing a hub unit for supporting a wheel according to claim 1 of the present invention is an inner end portion of a hub main body, which is more than an inner end surface of an inner ring fitted on a step portion of the hub main body. In a method for manufacturing a wheel-supporting hub unit, in which a hollow projecting portion projecting inward in the axial direction is crimped toward the radially outward direction,
During the caulking process, the ratio (P1 / P0) of “collision load (P1)” / “set load (P0)” is set to 1 to 1.3.

本発明によれば、加締め加工時、「衝突荷重（Ｐ１）」／「設定荷重（Ｐ０）」の比（Ｐ１／Ｐ０）は、１〜１．３に設定してあることから、衝突による金型の損傷を減少して、金型の寿命を安定することができる。   According to the present invention, at the time of caulking, the ratio (P1 / P0) of “collision load (P1)” / “set load (P0)” is set to 1 to 1.3. The damage of the mold can be reduced and the life of the mold can be stabilized.

以下、本発明の実施の形態に係る車輪支持用ハブユニットの製造方法を図面を参照しつつ説明する。   Hereinafter, a manufacturing method of a wheel supporting hub unit according to an embodiment of the present invention will be described with reference to the drawings.

図１は、ローリング加締め加工時に於ける、時間と荷重との関係を示すグラフである。   FIG. 1 is a graph showing the relationship between time and load during rolling caulking.

ハブのローリング加締め加工において、「衝突荷重（Ｐ１）」と「設定荷重（Ｐ０）」の比（Ｐ１／Ｐ０）と、金型寿命の関係を調べた。   In the rolling caulking process of the hub, the relationship between the ratio (P1 / P0) between the “impact load (P1)” and the “set load (P0)” and the mold life was examined.

「衝突荷重（Ｐ１）」と「設定荷重（Ｐ０）」の比（Ｐ１／Ｐ０）は、金型形状やワーク加締め部形状を変えることで、いろいろな値を準備した。   Various values were prepared for the ratio (P1 / P0) of the “collision load (P1)” and the “set load (P0)” by changing the shape of the mold and the shape of the work caulking part.

Figure 2006132711
Figure 2006132711

実験結果を表１に示す。表１の左側は、「衝突荷重（Ｐ１）」と「設定荷重（Ｐ０）」の比（Ｐ１／Ｐ０）を、上から小さい順に並べている。   The experimental results are shown in Table 1. On the left side of Table 1, the ratio (P1 / P0) of “collision load (P1)” and “set load (P0)” is arranged in ascending order from the top.

表１右側は、ワークと金型の衝突によって、金型表面に損傷が発生したかどうかの評価結果である。金型寿命の評価は、ある所定個数加締めた後に、金型表面の損傷が肉眼で観察できない場合は○、損傷が観察できる場合は×、としている。   The right side of Table 1 is an evaluation result of whether or not the mold surface is damaged due to the collision between the workpiece and the mold. The evaluation of the mold life is ◯ when damage to the mold surface cannot be observed with the naked eye after caulking a predetermined number, and x when damage can be observed.

表１の通り、（Ｐ１／Ｐ０）が１．３７以上の場合、ワークと金型の衝突による損傷が金型表面に発生したのを確認した。   As shown in Table 1, when (P1 / P0) was 1.37 or more, it was confirmed that damage due to collision between the workpiece and the mold occurred on the mold surface.

（Ｐｌ／Ｐ０）が１．２９以下の場合、衝突を原因とする損傷が金型表面に観察できなかった。   When (Pl / P0) was 1.29 or less, damage due to collision could not be observed on the mold surface.

実際の生産では、小数点以下第２位を四捨五入して、（Ｐ１／Ｐ０）を１．３以下という条件で管理している。   In actual production, the second decimal place is rounded off, and (P1 / P0) is managed under the condition of 1.3 or less.

以上から、本実施の形態によれば、ローリング加締め加工時、「衝突荷重（Ｐ１）」／「設定荷重（Ｐ０）」の比（Ｐ１／Ｐ０）は、１〜１．３に設定してあることから、衝突による金型の損傷を減少して、金型の寿命を安定することができる。   From the above, according to the present embodiment, during rolling caulking, the ratio (P1 / P0) of “collision load (P1)” / “set load (P0)” is set to 1 to 1.3. As a result, damage to the mold due to the collision can be reduced, and the life of the mold can be stabilized.

なお、図１に於いて、「設定荷重（Ｐ０）」の値は、金型（後述する押型１５）の揺動角によって変化する。   In FIG. 1, the value of “set load (P0)” varies depending on the swing angle of a mold (a pressing mold 15 described later).

例えば、揺動角が５度の時、「設定荷重（Ｐ０）」の値は、７〜１３であり、揺動角が２度の時、「設定荷重（Ｐ０）」の値は、１３〜２５である。   For example, when the swing angle is 5 degrees, the value of “set load (P0)” is 7 to 13, and when the swing angle is 2 degrees, the value of “set load (P0)” is 13 to 13. 25.

ここで、（Ｐ１／Ｐ０）を小さくするには、「衝突荷重（Ｐ１）」のうち、慣性力による荷重を減らすことが重要である。慣性力による荷重はΔFinertia＝Ｍ・Ｖ／Δｔで表されるので、Δｔを大きくする、Ｖを小さくする、Ｍを小さくすることが慣性力による荷重を減らす方法になる。以下、「衝突荷重（Ｐ１）」を減らす方法を記す。   Here, in order to reduce (P1 / P0), it is important to reduce the load caused by the inertia force among the “collision load (P1)”. Since the load due to inertial force is expressed by ΔFinertia = M · V / Δt, increasing Δt, decreasing V, and decreasing M are methods for reducing the load due to inertial force. Hereinafter, a method of reducing the “collision load (P1)” will be described.

I − Δｔを大きくする（ワークと金型の衝突を緩和させること）
（１） 金型のＲ形状の部分でワークと衝突するようにする。
（２） 金型表面を鏡面（Ｒａ０．２μｍまたはＲｙ０．８μｍ以下、かつ加工目が肉眼で見えないこと）にして、ワークが変形しやすいようにする。
（３） ワークの内径側をテーパーにし、ワーク先端が変形しやすいようにする。
（４） 内輪端面からワーク先端の突き出る長さ（ｈ）と厚さ（ｔ）の比ｈ／ｔを１．６以上にする（図３参照）。
（５） ワーク先端の硬さをＨＲＣ２５以下にする。
（６） ワークをバネで浮かせる。
II − Ｖを小さくする
（７） 金型とワークの衝突する速度を小さくする。
III − Ｍを小さくする
（８） 昇降する部分の質量を小さくする。
以下にその詳細を示す。 Increase I-Δt (to reduce collision between workpiece and mold)
(1) Collide with the workpiece at the R-shaped part of the mold.
(2) The surface of the mold is mirror-finished (Ra 0.2 μm or Ry 0.8 μm or less and the processed eyes cannot be seen with the naked eye) so that the workpiece is easily deformed.
(3) Tap the inner diameter of the workpiece so that the tip of the workpiece is easily deformed.
(4) The ratio h / t of the length (h) and thickness (t) at which the tip of the workpiece protrudes from the inner ring end face is set to 1.6 or more (see FIG. 3).
(5) The hardness of the workpiece tip is made HRC25 or less.
(6) Lift the work with a spring.
II-V is reduced (7) The speed at which the mold collides with the work is reduced.
III-M Reduce (8) Reduce the mass of the part that moves up and down.
The details are shown below.

（第１実施の形態）
図２は、本発明の第１実施の形態に係り、（ａ）は、ローリング加締め加工時に於いて、「衝突荷重（Ｐ１）」の発生時を示し、（ｂ）は、「衝突荷重（Ｐ１）」の終了時を示す。ここで、ワーク内径をテーパーにし、また金型表面をＲ形状にし、ワークは金型のＲ形状部分と衝突する。 (First embodiment)
2A and 2B relate to the first embodiment of the present invention. FIG. 2A shows the occurrence of “collision load (P1)” during rolling caulking, and FIG. P1) ”ends. Here, the work inner diameter is tapered and the surface of the mold is formed in an R shape, and the work collides with the R-shaped portion of the mold.

図２（ａ）に於いて、「衝突荷重（Ｐ１）」の発生時、ワーク（後述する加締め部１１）と、金型（後述する押型１５）の衝突をワーク（加締め部１１）の変形で緩和させる（Δｔを大きくする）ため、金型（押型１５）のＲ形状部分（１５ａ）でワーク（加締め部１１）と衝突するようにしてある。   In FIG. 2A, when the “collision load (P1)” is generated, the collision between the workpiece (clamping portion 11 to be described later) and the mold (pressing die 15 to be described later) is caused by the workpiece (clamping portion 11). In order to relieve the deformation (increase Δt), the R-shaped portion (15a) of the die (pressing die 15) collides with the workpiece (caulking portion 11).

また、図２（ａ）に於いて、「衝突荷重（Ｐ１）」の発生時、ワーク（後述する加締め部１１）と、金型（後述する押型１５）の衝突をワーク（加締め部１１）の変形で緩和させる（Δｔを大きくする）ため、ワーク（加締め部１１）の内径側（１１ａ）をテーパーにし、ワーク（加締め部１１）先端が変形しやすいようにしてある。   Further, in FIG. 2A, when the “collision load (P1)” is generated, the collision between the workpiece (clamping portion 11 to be described later) and the mold (pressing die 15 to be described later) is detected. ) Is relaxed (increases Δt), the inner diameter side (11a) of the workpiece (caulking portion 11) is tapered so that the tip of the workpiece (caulking portion 11) is easily deformed.

図２（ｂ）に於いて、「衝突荷重（Ｐ１）」の終了時、ワーク（後述する加締め部１１）と、金型（後述する押型１５）の衝突をワーク（加締め部１１）の変形で緩和させる（Δｔを大きくする）ため、金型（押型１５）のＲ形状部分（１５ａ）表面の面粗度を良く、できれば鏡面にして、ワーク（加締め部１１）が変形しやすいようにしてある。   2B, at the end of the “collision load (P1)”, the collision between the workpiece (clamping portion 11 to be described later) and the mold (pressing die 15 to be described later) is caused by the workpiece (clamping portion 11). In order to ease the deformation (increase Δt), the surface roughness of the R-shaped portion (15a) of the die (pressing die 15) is improved, and if possible, the surface is made mirror-like so that the workpiece (caulking portion 11) is easily deformed. It is.

（第２実施の形態）
図３は、本発明の第２実施の形態に係り、（ａ）は、ローリング加締め加工時に於いて、「衝突荷重（Ｐ１）」の発生時を示し、（ｂ）は、「衝突荷重（Ｐ１）」の終了時を示す。 (Second Embodiment)
FIG. 3 relates to a second embodiment of the present invention, wherein (a) shows the occurrence of “collision load (P1)” during rolling caulking, and (b) shows “collision load ( P1) ”ends.

図３（ａ）に於いて、「衝突荷重（Ｐ１）の発生時、ワーク（加締め部１１）と金型（押型１５）の衝突をワークの突き出た部分の形状をｈ／ｔ≧１．６とすることで、ワーク（加締め部１１）先端が変形しやすいようにしてある。   In FIG. 3A, “when the collision load (P1) is generated, the shape of the part where the workpiece protrudes due to the collision between the workpiece (clamping portion 11) and the die (pressing die 15) is h / t ≧ 1. By setting it to 6, the tip of the workpiece (caulking portion 11) is easily deformed.

また、図３（ａ）に於いて、ワーク（後述する加締め部１１）と、金型（後述する押型１５）の衝突時に発生する面圧を減ずるため、ハブ本体６の中空突出部１３（即ち、加締め部１１）の内径側の先端には、Ｒ面取り部１１ｂが形成してある。   Further, in FIG. 3A, in order to reduce the surface pressure generated when the workpiece (clamping portion 11 described later) and the mold (pressing die 15 described later) collide, the hollow protruding portion 13 ( That is, an R chamfered portion 11b is formed at the inner diameter side tip of the caulking portion 11).

なお、本実施の形態では、加締め部１１の内径側（１１ａ）も、円筒形状に形成してある。   In the present embodiment, the inner diameter side (11a) of the caulking portion 11 is also formed in a cylindrical shape.

図３（ｂ）は、ワーク（後述する加締め部１１）と、金型（後述する押型１５）の衝突が終了し、加工が始まった状態を示している。   FIG. 3B shows a state where the collision between the workpiece (clamping portion 11 to be described later) and the mold (pressing die 15 to be described later) is finished and machining is started.

なお、各実施例で、ワーク材料はＳ５０〜５５Ｃの材料を使用するのが望ましい。硬さはＨＲＣ１５〜２７である。この硬さを熱間鍛造後、コントロールクーリングして、ＨＲＣ２５以下にすることで、塑性変形しやすくし、ワーク（加締め部１１）先端が変形しやすいようにしてある。   In each embodiment, it is desirable to use a material of S50 to 55C as the work material. Hardness is HRC15-27. This hardness is controlled for cooling after hot forging to HRC25 or less, so that plastic deformation is facilitated and the tip of the workpiece (caulking portion 11) is easily deformed.

（第３実施の形態）
図４は、本発明の第３実施の形態に係り、製造装置である揺動プレス装置の断面図である。 (Third embodiment)
FIG. 4 is a sectional view of an oscillating press apparatus as a manufacturing apparatus according to the third embodiment of the present invention.

なお、以下に、ローリング加締めを行う揺動プレス装置を説明するが、これは、一例にすぎず、本発明は、この揺動プレス装置に限定されないことは、勿論である。   In addition, although the rocking press apparatus which performs rolling caulking is demonstrated below, this is only an example and it cannot be overemphasized that this invention is not limited to this rocking press apparatus.

揺動プレス装置１４は、昇降台２３を有する。この昇降台２３は、油圧シリンダ等の押圧装置（図示略）の出力ロッド２４の上端部に固定されており、加締め部１１の加工時に、押圧装置により上方に押し上げられる。   The swing press device 14 has a lifting platform 23. The lifting platform 23 is fixed to the upper end portion of the output rod 24 of a pressing device (not shown) such as a hydraulic cylinder, and is pushed upward by the pressing device when the caulking portion 11 is processed.

この様な昇降台２３の上面には、図４の表裏方向に水平移動するスライドテーブル２５を設け、更にこのスライドテーブル２５の上面に、ホルダ２６を介して支持ブロック２７を載置している。   A slide table 25 that horizontally moves in the front and back direction of FIG. 4 is provided on the upper surface of such a lift 23, and a support block 27 is placed on the upper surface of the slide table 25 via a holder 26.

尚、昇降台２３の上面で１対のスライダ２８、２８の間部分にバックアッププレート２９を固定し、このバックアッププレート２９の上面を、スライドテーブル２５の下面に摺接若しくは近接対向させている。   A backup plate 29 is fixed on the upper surface of the lift 23 between the pair of sliders 28, 28, and the upper surface of the backup plate 29 is slidably contacted or closely opposed to the lower surface of the slide table 25.

支持ブロック２７は、ハブ２を構成するハブ本体６の外端（図４で下方）部を支える為のもので、上面中央部に支持円筒部３０を固設している。   The support block 27 is for supporting the outer end (downward in FIG. 4) portion of the hub main body 6 constituting the hub 2, and a support cylindrical portion 30 is fixed at the center of the upper surface.

この支持円筒部３０は、ホイールの内周縁部を外嵌する為に、ハブ本体６の外端面に設けた位置決め筒部３１をほぼがたつきなく内嵌自在な内径と、ハブ本体６の外周面に設けたフランジ８の外側面にほぼ密接自在な上端面形状とを有する。   The supporting cylindrical portion 30 has an inner diameter that allows the positioning cylinder portion 31 provided on the outer end surface of the hub main body 6 to be fitted without being loose, and an outer circumference of the hub main body 6 so as to fit the inner peripheral edge of the wheel. It has an upper end surface shape that can be brought into close contact with the outer surface of the flange 8 provided on the surface.

支持ブロック２７の上方には、ハブ本体６の内端部に形成した中空突出部１３を塑性変形する為の加圧部材である押型１５を設けている。この押型１５は、例えば、揺動角５度であって、図示しない支持ヘッドの下端部に支持されている。   Above the support block 27, there is provided a pressing die 15 that is a pressing member for plastically deforming the hollow protrusion 13 formed at the inner end of the hub body 6. The pressing die 15 has, for example, a swing angle of 5 degrees and is supported by a lower end portion of a support head (not shown).

この押型１５の中心軸αは、ハブ本体６の中心軸βに対し、小さな角度θだけ傾斜している。ハブ本体６の内端部に加締め部１１を加工する際に押型１５は、その中心軸αをハブ本体６の中心軸βの回りで振れ回り運動させる。   The center axis α of the die 15 is inclined by a small angle θ with respect to the center axis β of the hub body 6. When the caulking portion 11 is processed at the inner end portion of the hub body 6, the pressing die 15 swings its center axis α around the center axis β of the hub body 6.

そして、この状態で昇降台２３を上方に押し上げる事により、中空突出部１３の上端縁を押型１５の下面に押し付ける。そして、この押型１５からこの中空突出部１３の円周方向の一部に、軸方向に関して外方（図４の下方）に、径方向に関して外方に、それぞれ向いた荷重を加える。この様にして中空突出部１３に荷重を加える位置は、中心軸αの振れ回り運動に伴って、この中空突出部１３の円周方向に関して連続的に変化する。   In this state, the lifting platform 23 is pushed upward to press the upper end edge of the hollow protrusion 13 against the lower surface of the pressing die 15. Then, loads directed from the pressing die 15 to a part in the circumferential direction of the hollow protrusion 13 are directed outward in the axial direction (downward in FIG. 4) and outward in the radial direction. In this way, the position at which the load is applied to the hollow protruding portion 13 continuously changes in the circumferential direction of the hollow protruding portion 13 with the swinging motion of the central axis α.

尚、押型１５は、この中空突出部１３を加圧するのに伴う反力により亀裂等の損傷が発生しない様に剛性を高くすべく、加締め部１１を形成する為の先端部から離れるに従って（上方程）外径が大きくなる方向に傾斜したテーパ形状としている。   In addition, as the die 15 is separated from the tip for forming the crimping portion 11 so as to increase rigidity so that damage such as cracks does not occur due to a reaction force accompanying pressurization of the hollow protruding portion 13 ( The upward direction is a tapered shape inclined in the direction of increasing the outer diameter.

押型１５の周囲に、円輪状の支持枠３２（内輪クランプ）を設けている。この支持枠３２の中央部には、この押型１５の振れ回り運動を許容すべく、上方に向かう程内径が大きくなる方向に傾斜した内周面を有する、摺鉢状の通孔３３を設けている。   An annular support frame 32 (inner ring clamp) is provided around the pressing die 15. In the central portion of the support frame 32, a mortar-shaped through-hole 33 having an inner peripheral surface inclined in a direction in which the inner diameter increases toward the upper side is provided so as to allow the swinging movement of the pressing die 15. Yes.

そして、支持枠３２の下面でこの通孔３３を囲む部分に、略短円筒状の押圧筒部３４を形成している。この押圧筒部３４は、押型１５により中空突出部１３を加締め部１１に加工する際に、ハブ本体６が径方向に振れ動くのを規制する役目を有する。   Then, a press cylinder portion 34 having a substantially short cylindrical shape is formed in a portion surrounding the through hole 33 on the lower surface of the support frame 32. The pressing cylinder portion 34 has a function of restricting the hub body 6 from swinging in the radial direction when the hollow protrusion 13 is processed into the crimped portion 11 by the pressing die 15.

この為に押圧筒部３４の下端部内周面は、ハブ本体６の内端部に外嵌した内輪７の外周面に、０．１〜０．５ｍ程度の微小な大きさの隙間を介して対向させている。それにより、内輪の外周面に傷をつけにくくなる。   For this purpose, the inner peripheral surface of the lower end portion of the pressing cylinder portion 34 is disposed on the outer peripheral surface of the inner ring 7 fitted on the inner end portion of the hub body 6 through a gap having a small size of about 0.1 to 0.5 m. They are facing each other. Thereby, it becomes difficult to damage the outer peripheral surface of the inner ring.

尚、支持枠３２は、図示しないフレームの一部に、やはり図示しない３本の油圧アクチュエータにより、若干の昇降自在に支持している。   The support frame 32 is supported on a part of a frame (not shown) by three hydraulic actuators (not shown) so that the support frame 32 can be slightly raised and lowered.

支持枠３２の下面外周寄り部分に、上下１対の連結環３５ａ、３５ｂを介して、欠円筒状の保持筒３６を、吊り下げ固定している。この保持筒６は、昇降台２３が上昇し、支持枠３２が下降した状態で、ホルダ２６に外嵌される。   A holding cylinder 36 having a non-cylindrical shape is suspended and fixed to a portion near the outer periphery of the lower surface of the support frame 32 via a pair of upper and lower connecting rings 35a and 35b. The holding cylinder 6 is externally fitted to the holder 26 in a state in which the lifting platform 23 is raised and the support frame 32 is lowered.

連結環３５ｂの内径側に駆動環３７を、転がり軸受３８により、回転自在に支持している。この転がり軸受３８は、旋回輪の如く、ラジアル荷重及びスラスト荷重を支承自在な構造を有する。駆動環３７は、押型１５により加締め部１１を加工する際に、外輪１を所定速度で回転させる為のもので、この外輪１の外周面に設けた取付部５に、円輪伏の駆動治具３９（割出しプレート）を外嵌した状態で、モータ４０により、回転駆動される。   A drive ring 37 is rotatably supported by a rolling bearing 38 on the inner diameter side of the coupling ring 35b. The rolling bearing 38 has a structure capable of supporting a radial load and a thrust load like a swirling wheel. The drive ring 37 is for rotating the outer ring 1 at a predetermined speed when the caulking part 11 is processed by the die 15, and the mounting part 5 provided on the outer peripheral surface of the outer ring 1 is used to drive the annular ring. The jig 39 (index plate) is rotationally driven by the motor 40 while being externally fitted.

駆動治具３９は、駆動環３７に駆動環３７に対する若干の昇降を自在に、且つ、駆動環３７と同期した回転を自在に組み合わせている。この為に本例の場合には、この駆動環３７の円周方向複数個所（例えば４〜６個所）に、それぞれがこの駆動環３７の中心軸と平行な支持孔４１、４１を形成している。   The drive jig 39 is combined with the drive ring 37 so that the drive ring 37 can be moved up and down slightly with respect to the drive ring 37 and can rotate in synchronization with the drive ring 37. For this reason, in this example, support holes 41 and 41 are formed at a plurality of circumferential positions (for example, 4 to 6 locations) of the drive ring 37 in parallel with the central axis of the drive ring 37. Yes.

駆動治具３９の外周面上端部に固定した取付フランジ４２の一部で各支持孔４１、４１に整合する部分に、それぞれが駆動治具３９の中心軸と平行に配置されたガイドピン４３、４３の基端部を結合固定している。そして、これら各ガイドピン４３、４３を各支持孔４１、４１に挿通し、更に、これら各ガイドピン４３、４３の下端部に形成した鍔部の上面と取付フランジ４２の下面との間に、圧縮ばねを設けている。   Guide pins 43 arranged in parallel to the center axis of the drive jig 39 in portions of the mounting flange 42 fixed to the upper end portion of the outer peripheral surface of the drive jig 39 and aligned with the support holes 41, 41. The base end portion of 43 is fixedly coupled. Then, the guide pins 43, 43 are inserted into the support holes 41, 41, and further, between the upper surface of the flange formed at the lower end of each guide pin 43, 43 and the lower surface of the mounting flange 42, A compression spring is provided.

この構成により、駆動治具３９は、下方に向かう弾力を付与された状態で、駆動環３７に対し若干の昇降自在に、且つ、この駆動環３７と同期した回転自在に支持されている。   With this configuration, the driving jig 39 is supported so as to be able to move up and down slightly relative to the driving ring 37 and to be rotatable in synchronization with the driving ring 37 in a state in which a downward elastic force is applied.

この様な駆動治具３９の下面内周寄り部分には、取付部５の外周縁と非円形嵌合する凹部４４を形成している。   A concave portion 44 that is non-circularly fitted to the outer peripheral edge of the mounting portion 5 is formed on the inner peripheral portion of the lower surface of the driving jig 39.

一方、駆動環３７を回転駆動する為のモータ４０は、保持筒３６の一部外周面に、連結ブラケット４７と保持ブラケット４８とにより支持固定している。   On the other hand, the motor 40 for rotationally driving the drive ring 37 is supported and fixed to a partial outer peripheral surface of the holding cylinder 36 by a connection bracket 47 and a holding bracket 48.

従って、モータ４０は、支持枠３２と共に昇降する。この様なモータ４０の出力軸４９と駆動環３７とは、歯車減速機構５０により結合して、この駆動環３７を所定方向に所定速度で回転駆動自在としている。   Therefore, the motor 40 moves up and down together with the support frame 32. The output shaft 49 and the drive ring 37 of such a motor 40 are coupled by a gear reduction mechanism 50 so that the drive ring 37 can be rotationally driven at a predetermined speed in a predetermined direction.

歯車減速機構５０を構成する為に、連結ブラケット４７に中間軸５１を、出力軸４９及び駆動環３７の中心軸と平行に配置した状態で、回転自在に支持している。この駆動環３７の下面外周寄り部分に、減速大歯車５２を固定している。   In order to configure the gear reduction mechanism 50, the intermediate shaft 51 is rotatably supported on the connection bracket 47 in a state where the intermediate shaft 51 is disposed in parallel with the output shaft 49 and the central axis of the drive ring 37. A reduction large gear 52 is fixed to a portion near the outer periphery of the lower surface of the drive ring 37.

そして、この減速大歯車５２と、出力軸４９の先端部（図示の場合上端部）に固定した減速小歯車５３とを、中間軸５１の上端部に固定した中間歯車５４を介して噛合させている。   Then, the reduction large gear 52 and the reduction small gear 53 fixed to the tip end portion (the upper end portion in the figure) of the output shaft 49 are engaged with each other via an intermediate gear 54 fixed to the upper end portion of the intermediate shaft 51. Yes.

この構成により駆動環３７を、出力軸４９と同方向に、この出力軸４９よりも低速で回転駆動自在としている。   With this configuration, the drive ring 37 can be driven to rotate in the same direction as the output shaft 49 at a lower speed than the output shaft 49.

更に、支持ブロック２７の上方には、回転制限部材である押圧ロッド５５を、外輪１の外周面に対する進退自在に設けている。この為に本例の場合には、ホルダ２６の外周面で保持筒３６の不連続部に対応する部分に、エアシリンダ等のアクチュエ一タ５６（ブレーキマウント）を固定し、このアクチュエータ５６により押圧ロッド５５を、外輪１の径方向に変位自在としている。なお、符号５７は、シリンダーマウントを示している。   Further, above the support block 27, a pressing rod 55, which is a rotation limiting member, is provided so as to freely advance and retreat with respect to the outer peripheral surface of the outer ring 1. For this reason, in the case of this example, an actuator 56 (brake mount) such as an air cylinder is fixed to a portion corresponding to the discontinuous portion of the holding cylinder 36 on the outer peripheral surface of the holder 26, and is pressed by this actuator 56. The rod 55 is displaceable in the radial direction of the outer ring 1. Reference numeral 57 denotes a cylinder mount.

また、押圧ロッド５５の先端部に、硬質ゴム、合成樹脂、軟質金属等、外輪１を構成する金属材料（炭素鋼）よりも軟らかい材料を設置する事が、外輪１の外周面の損傷防止の面から好ましい。   In addition, it is possible to prevent damage to the outer peripheral surface of the outer ring 1 by installing a material softer than the metal material (carbon steel) constituting the outer ring 1 such as hard rubber, synthetic resin, or soft metal at the tip of the pressing rod 55. From the aspect, it is preferable.

また、ハブ本体６の下方と、支持ブロック２７との間には、ガタつきなく且つ若干の揺動変位自在に支持する受治具６１が設けてあり、受治具６１は、外ネジ式ストッパーボルト６２により、支持ブロック２７の中央部に揺動自在に設けてある。この受治具６１により、加締め加工時に、ハブ２にモーメントが作用せず、ハブ２に曲り変形等が生じることを防止することができる。   Further, a receiving jig 61 is provided between the lower portion of the hub body 6 and the support block 27 so as to be supported in a manner that can be slightly swung and displaced. The receiving jig 61 is an external screw type stopper. The bolt 62 is swingably provided at the center of the support block 27. The receiving jig 61 can prevent a moment from acting on the hub 2 during the caulking process, thereby preventing the hub 2 from being bent or deformed.

さらに、ハブ２のフランジ８の下方側を支持するように、フランジサポート６３が設けてあり、このフランジサポート６３と、支持ブロック２７の外周部の受けガイド部６６との間に、外ネジ式ストッパーボルト６４とコイルスプリング６５とが設けてある。また、支持ブロック２７の外周部の受けガイド部６６は極低頭六角穴付ボルト６７により取付けてある。このような弾性支持構成により、治具（押型１５）とワーク（加締め部１１）が衝突する時の衝撃を吸収することができる。   Further, a flange support 63 is provided so as to support the lower side of the flange 8 of the hub 2, and an external screw type stopper is provided between the flange support 63 and the receiving guide portion 66 on the outer peripheral portion of the support block 27. A bolt 64 and a coil spring 65 are provided. Further, the receiving guide portion 66 on the outer peripheral portion of the support block 27 is attached by a very low head hexagon socket head bolt 67. With such an elastic support structure, it is possible to absorb an impact when the jig (the pressing die 15) and the workpiece (the caulking portion 11) collide with each other.

次に、上述の様に構成する揺動プレス装置１４を使用し、ハブ本体６の内端部に設けた中空突出部１３を塑性変形させて加締め部１１とする際の作用に就いて説明する
先ず、昇降台２３を下降させ、且つ、スライドテーブル２５を図４の表裏方向にずらせて押型１５の下方から支持ブロック２７を抜き出した状態で、この支持ブロック２７の上面にハブ本体６を載置する。このハブ本体６の内端部には、予め内輪７を外嵌しておく。 Next, an explanation will be given of the operation when the hollow projecting portion 13 provided at the inner end portion of the hub body 6 is plastically deformed to form the crimped portion 11 by using the swing press device 14 configured as described above. First, the hub body 6 is mounted on the upper surface of the support block 27 in a state in which the lift table 23 is lowered and the slide table 25 is shifted in the front and back direction of FIG. Put. An inner ring 7 is fitted on the inner end of the hub body 6 in advance.

次いで、スライドテーブル２５を押型１５の下方に、ハブ本体６の中心軸と支持枠３２の中心軸とが一致する状態まで入り込ませる。その後、この支持枠３２を下降させ、押圧筒部３４の下端部を内輪７に外嵌する。   Next, the slide table 25 is inserted below the pressing die 15 until the center axis of the hub body 6 and the center axis of the support frame 32 coincide with each other. Thereafter, the support frame 32 is lowered, and the lower end portion of the pressing cylinder portion 34 is externally fitted to the inner ring 7.

取付部５と凹部４４とを嵌合させて、駆動治具３９により外輪１を回転駆動自在とする事により、加締め部１１を加工する為の準備作業が完了する。   By fitting the mounting portion 5 and the recessed portion 44 so that the outer ring 1 can be rotationally driven by the driving jig 39, the preparatory work for processing the caulking portion 11 is completed.

そこで、モータ４０により外輪１を、例えば数百ｍｉｎ−１程度で回転させると共に、昇降台２３を上昇させつつ、押型１５によりハブ本体６の内端部に形成した中空突出部１３を塑性変形させる。 Accordingly, the outer ring 1 is rotated by, for example, about several hundred min −1 by the motor 40, and the hollow protrusion 13 formed at the inner end of the hub body 6 is plastically deformed by the pressing die 15 while the elevator 23 is raised. .

そして、加締め部１１を形成し、この加締め部１１により内輪７の内端面を押圧する。この際、押型１５は、その中心軸αを上記ハブ本体６の中心軸βの回りで振れ回り運動させる。   Then, a caulking portion 11 is formed, and the inner end surface of the inner ring 7 is pressed by the caulking portion 11. At this time, the pressing die 15 swings its central axis α around the central axis β of the hub body 6.

中空突出部１３は、この様に振れ回り運動する押型１５の下面に、油圧シリンダ等の押圧装置の出力ロッド２４の押し上げ力に基づいて、押し付けられる。この際、中空突出部１３を設けたハブ本体６は回転しない為、この中空突出部１３の円周方向の一部に、軸方向に関して外端側に、径方向に関して外方に、それぞれ向いた荷重が加えられ、且つ、この荷重を加えられる部分が、中空突出部１３の円周方向に関して連続的に変化する。   The hollow protruding portion 13 is pressed against the lower surface of the pressing die 15 that swings in this manner based on the pushing force of the output rod 24 of a pressing device such as a hydraulic cylinder. At this time, since the hub body 6 provided with the hollow projecting portion 13 does not rotate, the hub projecting portion 13 is directed to a part of the circumferential direction of the hollow projecting portion 13 toward the outer end side in the axial direction and outward in the radial direction. A load is applied, and a portion to which this load is applied continuously changes in the circumferential direction of the hollow protrusion 13.

この結果、この中空突出部１３が、円周方向に関して連続的に、且つ、徐々に塑性変形して、加締め部１１となる。この様に中空突出部１３が加締め部１１となるのに伴って、ハブ本体６及びこのハブ本体６を載置した昇降台２３、並びに支持枠３２、モータ４０、歯車減速機構５０等が少しずつ上昇する。   As a result, the hollow projecting portion 13 is continuously and gradually plastically deformed in the circumferential direction to form the crimped portion 11. As the hollow projecting portion 13 becomes the caulking portion 11 in this way, the hub body 6 and the elevator 23 on which the hub body 6 is placed, the support frame 32, the motor 40, the gear reduction mechanism 50, and the like are a little. It rises one by one.

尚、加締め部１１の加工に伴ってスライドテーブル２５に加わるスラスト荷重は、バックアッププレート２９を介して、出力ロッド２４により支承する。従って、スライダ２８に過大な力が作用する事はなく、このスライダ２８の耐久性を十分に確保できる。   Note that the thrust load applied to the slide table 25 as the caulking portion 11 is processed is supported by the output rod 24 via the backup plate 29. Therefore, an excessive force does not act on the slider 28, and the durability of the slider 28 can be sufficiently ensured.

特に、本実施の形態では、上述したように、ハブ２のフランジ８の下方側を支持するように、フランジサポート６３が設けてあり、このフランジサポート６３と、支持ブロック２７の外周部の受けガイド部６６との間に、外ネジ式ストッパーボルト６４とコイルスプリング６５とが設けてある。また、支持ブロック２７の外周部の受けガイド部６６は極低頭六角穴付ボルト６７により取付けてある。このような弾性支持構成により、治具（押型１５）とワーク（加締め部１１）が衝突する時の衝撃を吸収することができる。   In particular, in the present embodiment, as described above, the flange support 63 is provided so as to support the lower side of the flange 8 of the hub 2, and the flange support 63 and the receiving guide on the outer peripheral portion of the support block 27. Between the portion 66, an external screw type stopper bolt 64 and a coil spring 65 are provided. Further, the receiving guide portion 66 on the outer peripheral portion of the support block 27 is attached by a very low head hexagon socket head bolt 67. With such an elastic support structure, it is possible to absorb an impact when the jig (the pressing die 15) and the workpiece (the caulking portion 11) collide with each other.

また、昇降台２３の上昇速度を衝突直前に減速する制御をすることによって、治具（押型１５）とワーク（加締め部１１）が衝突するときの衝撃を吸収することができる。   Further, by controlling to reduce the ascending speed of the lifting platform 23 immediately before the collision, it is possible to absorb an impact when the jig (the pressing die 15) and the workpiece (the caulking portion 11) collide with each other.

また、昇降台２３を含む昇降する部分の質量を軽くすることによって、治具（押型１５）とワーク（加締め部１１）が衝突するときの衝撃を吸収することができる。   Moreover, by reducing the mass of the part to be moved up and down including the lifting platform 23, it is possible to absorb an impact when the jig (the pressing die 15) and the workpiece (the caulking part 11) collide with each other.

なお、本願発明は、治具のみが揺動回転する加締め方法だけでなく、ワーク本体が回転し、加締め固定させる場合にも適用することができる。   The present invention can be applied not only to a caulking method in which only a jig swings and rotates, but also to a case where the work body is rotated and fixed by caulking.

なお、本発明は、上述した実施の形態に限定されず、種々変形可能である。   In addition, this invention is not limited to embodiment mentioned above, A various deformation | transformation is possible.

本発明に係り、ローリング加締め加工時に於ける、時間と荷重との関係を示すグラフである。It is a graph which shows the relationship between time and a load in the rolling caulking process according to the present invention. 本発明の第１実施の形態に係り、（ａ）は、ローリング加締め加工時に於いて、「衝突荷重（Ｐ１）」の発生時を示し、（ｂ）は、「衝突荷重（Ｐ１）」の終了時を示す。According to the first embodiment of the present invention, (a) shows the occurrence of “collision load (P1)” during rolling caulking, and (b) shows the “collision load (P1)”. Indicates the end time. 本発明の第２実施の形態に係り、（ａ）は、ローリング加締め加工時に於いて、「衝突荷重（Ｐ１）」の発生時を示し、（ｂ）は、「衝突荷重（Ｐ１）」の終了時を示す。According to the second embodiment of the present invention, (a) shows the occurrence of “collision load (P1)” during rolling caulking, and (b) shows “collision load (P1)”. Indicates the end time. 本発明の第３実施の形態に係り、製造装置である揺動プレス装置の断面図である。It is sectional drawing of the rocking press apparatus which is related with 3rd Embodiment of this invention and is a manufacturing apparatus. 車輪支持用転がり軸受ユニットの断面図である。It is sectional drawing of the rolling bearing unit for wheel support.

符号の説明Explanation of symbols

１ 外輪
２ ハブ
３ 円錐ころ
４ 外輪軌道
５ 取付部
６ ハブ本体
７ａ，７ｂ 内輪
８ フランジ
９ａ，９ｂ 内輪軌道
１０ 段部
１１ 加締め部
１１ａ 加締め部１１の内径側
１１ｂ Ｒ面取り部
１３ 中空突出部
１４ 揺動プレス装置
１５ 押型
１５ａ Ｒ形状部分
２３ 昇降台
２４ 出力ロッド
２５ スライドテーブル
２６ ホルダ
２７ 支持ブロック
２８ スライダ
２９ バックアッププレート
３０ 支持円筒部
３１ 位置決め筒部
３２ 支持枠
３３ 通孔
３４ 押圧筒部
３５ａ、３５ｂ 連結環
３６ 保持筒
３７ 駆動環
３８ 転がり軸受
３９ 駆動治具
４０ モータ
４１ 支持孔
４２ 取付フランジ
４３ ガイドピン
４４ 凹部
４７ 連結ブラケット
４８ 保持ブラケット
４９ 出力軸
５０ 歯車減速機構
５１ 中間軸
５２ 減速大歯車
５３ 減速小歯車
５４ 中間歯車
５５ 押圧ロッド
５６ アクチュエータ
５７ シリンダーマウント
６１ 受治具
６２ 外ネジ式ストッパーボルト
６３ フランジサポート
６４ 外ネジ式ストッパーボルト
６５ コイルスプリング
６６ 受けガイド部
６７ 極低頭六角穴付ボルト DESCRIPTION OF SYMBOLS 1 Outer ring 2 Hub 3 Tapered roller 4 Outer ring raceway 5 Mounting part 6 Hub body 7a, 7b Inner ring 8 Flange 9a, 9b Inner ring raceway 10 Step part 11 Clamping part 11a Inner diameter side of the caulking part 11 11b R chamfered part 13 Hollow protrusion part DESCRIPTION OF SYMBOLS 14 Oscillating press apparatus 15 Stamping die 15a R-shaped part 23 Lifting stand 24 Output rod 25 Slide table 26 Holder 27 Support block 28 Slider 29 Backup plate 30 Support cylindrical part 31 Positioning cylinder part 32 Support frame 33 Through-hole 34 Pressing cylinder part 35a, 35b Connection ring 36 Holding cylinder 37 Drive ring 38 Rolling bearing 39 Drive jig 40 Motor 41 Support hole 42 Mounting flange 43 Guide pin 44 Recess 47 Connection bracket 48 Holding bracket 49 Output shaft 50 Gear reduction mechanism 51 Intermediate shaft 52 Reduction large gear 53 Reduction gear 54 During the gear 55 push rod 56 the actuator 57 cylinder mount 61 receiving jig 62 outer threaded stopper bolt 63 flange support 64 outer threaded stopper bolt 65 the coil spring 66 receiving the guide portion 67 pole low head hexagon socket head cap screws

Claims (1)

ハブ本体の内端部であり、ハブ本体の 段部に外嵌した内輪の内端面よりも軸方向内方に突出する中空突出部を、径方向外方に向けて加締め加工する車輪支持用ハブユニットの製造方法に於いて、
前記加締め加工時、「衝突荷重（Ｐ１）」／「設定荷重（Ｐ０）」の比（Ｐ１／Ｐ０）は、１〜１．３に設定してあることを特徴とする車輪支持用ハブユニットの製造方法。 For wheel support, which is the inner end of the hub body and caulks the hollow projecting part that protrudes inward in the axial direction from the inner end surface of the inner ring that is externally fitted to the stepped part of the hub body. In the manufacturing method of the hub unit,
The wheel support hub unit, wherein a ratio (P1 / P0) of “impact load (P1)” / “set load (P0)” is set to 1 to 1.3 during the caulking process. Manufacturing method.
JP2004323928A 2004-11-08 2004-11-08 Method of manufacturing hub unit for supporting wheel Withdrawn JP2006132711A (en)

Priority Applications (1)

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Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2004323928A JP2006132711A (en) 2004-11-08 2004-11-08 Method of manufacturing hub unit for supporting wheel

Publications (2)

Publication Number Publication Date
JP2006132711A true JP2006132711A (en) 2006-05-25
JP2006132711A5 JP2006132711A5 (en) 2007-10-04

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008190692A (en) * 2007-02-07 2008-08-21 Nsk Ltd Method for manufacturing bearing device
WO2018179192A1 (en) * 2017-03-29 2018-10-04 不二商事株式会社 Inner race constraining device for vehicular hub bearing
WO2019097972A1 (en) * 2017-11-20 2019-05-23 日本精工株式会社 Rotary swaging device, method for manufacturing hub unit bearing, and method for manufacturing vehicle
CN112566803A (en) * 2018-06-12 2021-03-26 日本发条株式会社 Stabilizer and method for manufacturing the same

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4552951B2 (en) * 2007-02-07 2010-09-29 日本精工株式会社 Manufacturing method of bearing device
JP2008190692A (en) * 2007-02-07 2008-08-21 Nsk Ltd Method for manufacturing bearing device
US10914340B2 (en) 2017-03-29 2021-02-09 Fuji Shoji Co., Ltd. Inner-ring restraint device of hub bearing for vehicle
WO2018179192A1 (en) * 2017-03-29 2018-10-04 不二商事株式会社 Inner race constraining device for vehicular hub bearing
CN110461492B (en) * 2017-03-29 2021-07-23 不二商事株式会社 Inner ring restraint device for hub bearing of vehicle
CN110461492A (en) * 2017-03-29 2019-11-15 不二商事株式会社 The inner ring restraint device of hub bearing for vehicle
WO2019097972A1 (en) * 2017-11-20 2019-05-23 日本精工株式会社 Rotary swaging device, method for manufacturing hub unit bearing, and method for manufacturing vehicle
JP6558517B1 (en) * 2017-11-20 2019-08-14 日本精工株式会社 Swing caulking device, hub unit bearing manufacturing method, and vehicle manufacturing method
US11077484B2 (en) 2017-11-20 2021-08-03 Nsk Ltd. Rotary caulking device, method of manufacturing hub unit bearing and method of manufacturing vehicle
US20210268568A1 (en) * 2017-11-20 2021-09-02 Nsk Ltd. Rotary caulking device, method of manufacturing hub unit bearing and method of manufacturing vehicle
US11745249B2 (en) 2017-11-20 2023-09-05 Nsk Ltd. Rotary caulking device, method of manufacturing hub unit bearing and method of manufacturing vehicle
CN112566803A (en) * 2018-06-12 2021-03-26 日本发条株式会社 Stabilizer and method for manufacturing the same
CN112566803B (en) * 2018-06-12 2023-10-20 日本发条株式会社 Stabilizer and method for manufacturing the same
US11827068B2 (en) 2018-06-12 2023-11-28 Nhk Spring Co., Ltd. Stabilizer and method of manufacturing same

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