JP5742982B2 - Joint part between shaft and universal joint yoke and method for manufacturing the same - Google Patents
Joint part between shaft and universal joint yoke and method for manufacturing the same Download PDFInfo
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- JP5742982B2 JP5742982B2 JP2014030502A JP2014030502A JP5742982B2 JP 5742982 B2 JP5742982 B2 JP 5742982B2 JP 2014030502 A JP2014030502 A JP 2014030502A JP 2014030502 A JP2014030502 A JP 2014030502A JP 5742982 B2 JP5742982 B2 JP 5742982B2
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- 238000004519 manufacturing process Methods 0.000 title claims description 5
- 238000000034 method Methods 0.000 title description 3
- 230000008878 coupling Effects 0.000 claims description 58
- 238000010168 coupling process Methods 0.000 claims description 58
- 238000005859 coupling reaction Methods 0.000 claims description 58
- 230000002093 peripheral effect Effects 0.000 claims description 51
- 239000007769 metal material Substances 0.000 claims description 7
- 230000007423 decrease Effects 0.000 claims description 4
- 230000035515 penetration Effects 0.000 description 10
- 238000003466 welding Methods 0.000 description 9
- 239000002184 metal Substances 0.000 description 7
- 229910000831 Steel Inorganic materials 0.000 description 6
- 238000005242 forging Methods 0.000 description 6
- 239000010959 steel Substances 0.000 description 6
- 230000002542 deteriorative effect Effects 0.000 description 3
- 238000009826 distribution Methods 0.000 description 3
- 238000010438 heat treatment Methods 0.000 description 3
- 238000004080 punching Methods 0.000 description 3
- 230000015572 biosynthetic process Effects 0.000 description 2
- 238000001816 cooling Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000003672 processing method Methods 0.000 description 2
- 238000005452 bending Methods 0.000 description 1
- 230000000149 penetrating effect Effects 0.000 description 1
- 230000002265 prevention Effects 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
Description
本発明の対象となるシャフトと自在継手のヨークとの結合部は、例えばステアリング装置に於いて、このステアリング装置を構成する各種シャフトの端部と自在継手のヨークとを結合する為に利用する。 The coupling portion between the shaft and the universal joint yoke, which is the subject of the present invention, is used, for example, in a steering apparatus to couple the ends of various shafts constituting the steering apparatus and the universal joint yoke.
自動車のステアリング装置は、図１０に示す様に構成している。運転者が操作するステアリングホイール１の動きは、ステアリングシャフト２、自在継手３、中間シャフト４、別の自在継手３を介して、ステアリングギヤユニット５の入力軸６に伝達される。そして、このステアリングギヤユニット５に内蔵したラック＆ピニオン機構により左右１対のタイロッド７、７を押し引きし、左右１対の操舵輪に、上記ステアリングホイール１の操作量に応じて、適切な舵角を付与する様に構成している。 The automobile steering apparatus is configured as shown in FIG. The movement of the steering wheel 1 operated by the driver is transmitted to the input shaft 6 of the steering gear unit 5 through the steering shaft 2, the universal joint 3, the intermediate shaft 4, and another universal joint 3. Then, a pair of left and right tie rods 7, 7 are pushed and pulled by a rack and pinion mechanism built in the steering gear unit 5, and an appropriate rudder is applied to the pair of left and right steering wheels according to the operation amount of the steering wheel 1. It is configured to give corners.
この様なステアリング装置に組み込む前記各自在継手３、３として、一般的には、カルダン継手と呼ばれる十字軸継手が、広く使用されている。又、この様な十字軸継手を構成するヨークとシャフト（前記ステアリングシャフト２、前記中間シャフト４）との結合部の構造に就いては、例えば特許文献１〜２等に記載されている様に、従来から各種知られている。図１１〜１３は、この様なヨークとシャフトとの結合部の従来構造の１例を示している。図示の例の場合、十字軸継手を構成するヨーク８は、鋼板等の金属板ではなく、鋼製丸棒等の金属素材に鍛造加工、打ち抜き加工等を施す事により造られたもので、基部１０と、１対の腕部１１、１１とを備える。このうちの基部１０の径方向｛図１１、１２、１３の（ａ）（ｂ）に於ける上下方向｝中心部には、この基部１０を軸方向｛図１１、１２、１３の（ａ）（ｂ）に於ける左右方向｝に貫通する状態で、結合孔であるセレーション孔１２が形成されている。又、前記両腕部１１、１１は、前記基部１０の径方向反対側となる２箇所位置から軸方向片側｛図１１、１２、１３の（ａ）（ｂ）に於ける左側｝に向け延出する状態で設けられている。これら両腕部１１、１１の先端部には、それぞれ互いに同心の円孔１３、１３が形成されている。前記十字軸継手を組み立てた状態で、これら両円孔１３、１３内には、それぞれ有底円筒状の軸受カップが内嵌固定される。これと共に、これら両軸受カップ内に、それぞれ複数本のニードルを介して、十字軸の端部が回動自在に支持される。又、図示の例の場合、前記基部１０の肉厚は、前記両腕部１１、１１の肉厚よりも大きくなっている。更に、この基部１０の軸方向他側面｛図１１、１２、１３の（ａ）（ｂ）に於ける右側面｝は、軸方向に対して直角な平面になっている。 As the universal joints 3 and 3 incorporated in such a steering apparatus, generally, a cross shaft joint called a cardan joint is widely used. Further, regarding the structure of the coupling portion between the yoke and the shaft (the steering shaft 2 and the intermediate shaft 4) constituting such a cross joint, as described in Patent Documents 1 and 2, for example. Various types have been conventionally known. FIGS. 11 to 13 show an example of a conventional structure of such a joint between the yoke and the shaft. In the case of the illustrated example, the yoke 8 constituting the cross joint is not a metal plate such as a steel plate, but is made by subjecting a metal material such as a steel round bar to forging, punching, etc. 10 and a pair of arm portions 11 and 11. Of these, the base 10 is arranged in the radial direction {vertical direction in FIGS. 11, 12, 13 (a) and 13 (b)}. A serration hole 12 which is a coupling hole is formed in a state penetrating in the left-right direction in (b). The arms 11 and 11 extend from two positions on the opposite side in the radial direction of the base 10 toward one axial side (the left side in FIGS. 11, 12 and 13 (a) and (b)). It is provided in the state where it comes out. Concentric circular holes 13 and 13 are formed at the distal ends of both arms 11 and 11, respectively. In a state where the cross joint is assembled, a bottomed cylindrical bearing cup is fitted and fixed in each of the circular holes 13 and 13. At the same time, the ends of the cross shafts are rotatably supported in the bearing cups via a plurality of needles. In the case of the illustrated example, the thickness of the base 10 is larger than the thickness of the arms 11 and 11. Further, the other side surface in the axial direction of the base portion 10 (the right side surface in FIGS. 11, 12 and 13 (a) and (b)) is a plane perpendicular to the axial direction.
一方、前記ヨーク８に結合したシャフト９は、二次衝突時に全長を収縮可能とした、前記ステアリングシャフト２或いは前記中間シャフト４を構成する、互いにテレスコープ状に組み合わされた１対のシャフトのうちの一方のシャフトであり、鋼材等の金属製で、円管状に造られている。この様なシャフト９の軸方向片端部｛図１１、１２、１３の（ａ）（ｂ）に於ける左側の端部｝である先端部の外周面には、雄セレーション部１４が形成されている。そして、この様なシャフト９の先端部を、前記セレーション孔１２の内側に、軸方向他側から圧入して、このセレーション孔１２に前記雄セレーション部１４を、締め代を持たせた状態で係合させている。更に、この状態で、前記基部１０の軸方向他側面と、前記シャフト９の外周面との間の隅部に溶接を施す事により、これら基部１０とシャフト９の先端寄り部分とを、溶接金属１５を介して結合している。これにより、前記ヨーク８と前記シャフト９とを、回転力の伝達を可能に結合固定している。 On the other hand, the shaft 9 coupled to the yoke 8 is one of a pair of shafts that are combined in a telescopic manner and that constitute the steering shaft 2 or the intermediate shaft 4 that can contract the entire length in a secondary collision. One of the shafts is made of metal such as steel and is formed in a circular tube shape. A male serration portion 14 is formed on the outer peripheral surface of the tip portion which is one end portion in the axial direction of the shaft 9 (the left end portion in FIGS. 11, 12 and 13 (a) and (b)). Yes. Then, the tip end portion of such a shaft 9 is press-fitted into the serration hole 12 from the other side in the axial direction, and the male serration portion 14 is engaged with the serration hole 12 with a tightening margin. It is combined. Furthermore, in this state, by welding the corner between the other axial side surface of the base 10 and the outer peripheral surface of the shaft 9, the base 10 and the portion near the tip of the shaft 9 are welded metal. 15 is connected. Thereby, the yoke 8 and the shaft 9 are coupled and fixed so as to be able to transmit rotational force.
上述した様な従来構造の場合、前記基部１０のうちで前記セレーション孔１２の周囲部分の肉厚は、軸方向に関して変化していない為、この周囲部分の剛性も、軸方向に関して変化していない。この様な基部１０のセレーション孔１２に、上述の様にシャフト９の先端部を軸方向他側から圧入すると、これらセレーション孔１２とシャフト９の先端部外周面に設けた雄セレーション部１４との係合部（嵌合部）の面圧が、図１１の下部に示す様に、この係合部の軸方向他端縁部分で集中的に高くなる。そして、この軸方向他端縁部分の面圧ＰEが集中的に高くなる結果、前記シャフト９の先端寄り部分で、前記面圧が作用している領域と作用していない領域との境界部分に加わる剪断応力が、相当に大きくなる。この為、この境界部分の耐久性を十分に確保する為の設計が必要になり、その分だけ、設計の自由度が低下する。 In the case of the conventional structure as described above, the thickness of the peripheral portion of the serration hole 12 in the base 10 does not change with respect to the axial direction, so the rigidity of the peripheral portion also does not change with respect to the axial direction. . When the tip of the shaft 9 is press-fitted into the serration hole 12 of the base 10 from the other side in the axial direction as described above, the serration hole 12 and the male serration 14 provided on the outer peripheral surface of the tip of the shaft 9 As shown in the lower part of FIG. 11, the surface pressure of the engaging portion (fitting portion) is intensively increased at the other axial end edge portion of the engaging portion. The boundary portion between the axial end edge portions result the surface pressure P E is increased intensively in the in the tip-sided portion of the shaft 9, the surface pressure is not applied with the area acting area The shear stress applied to is considerably increased. For this reason, a design for sufficiently ensuring the durability of the boundary portion is required, and the degree of design freedom is reduced accordingly.
又、上述した様な従来構造の場合には、互いに溶接する部分である、前記基部１０と前記シャフト９の先端寄り部分とのうち、この基部１０の肉厚ｔ10が、このシャフト９の先端寄り部分の肉厚ｔ9に比べて、大幅に大きく（ｔ10≫ｔ9）なっている。この為、前記基部１０側で、前記シャフト９側に比べて、溶接部の溶け込み量を確保するのが難しい。即ち、前記基部１０側では、前記シャフト９側に比べて、図１２に矢印で示す様に、加えた熱が内部に分散し易く、集中した加熱を行いにくい為、溶接部の溶け込み量を確保するのが難しい。これに対し、この溶接部の強度を確保する為には、前記基部１０側と前記シャフト９側との、双方の溶け込み量を確保する事が重要となる。但し、前記基部１０側の溶け込み量を確保すべく、単純に溶接部の加熱量を増大させると、前記シャフト９側の加熱量が過大になって、このシャフト９側の機械的性質を悪化させる可能性がある。この為、上述した従来構造の場合には、前記溶接部の強度を確保する為の溶接条件を設定する事が難しいと言う問題がある。 Further, in the case of the conventional structure as described above, the thickness t 10 of the base portion 10 of the base portion 10 and the portion near the tip end of the shaft 9 that are welded to each other is the tip end of the shaft 9. It is significantly larger (t 10 >> t 9 ) than the wall thickness t 9 of the side portion. For this reason, it is difficult to ensure the amount of penetration of the welded portion on the base portion 10 side as compared with the shaft 9 side. That is, on the base 10 side, compared to the shaft 9 side, as shown by the arrows in FIG. 12, the applied heat is easily dispersed inside and it is difficult to perform concentrated heating, so the amount of penetration of the welded portion is ensured. Difficult to do. On the other hand, in order to ensure the strength of the welded portion, it is important to secure the amount of penetration of both the base 10 side and the shaft 9 side. However, if the heating amount of the welded portion is simply increased in order to ensure the amount of penetration on the base 10 side, the heating amount on the shaft 9 side becomes excessive, and the mechanical properties on the shaft 9 side are deteriorated. there is a possibility. For this reason, in the case of the conventional structure described above, there is a problem that it is difficult to set welding conditions for ensuring the strength of the welded portion.
本発明は、上述の様な事情に鑑み、ヨークの基部に設けた結合孔にシャフトの軸方向片端部を軸方向他側から圧入した構造に関して、このシャフトの軸方向片端寄り部分に加わる剪断応力を十分に抑える事ができ、更に、管状である、このシャフトと、前記基部とを溶接する場合には、このシャフトの機械的性質を悪化させる事なく、溶接部の強度を確保する事が容易な構造を実現すべく発明したものである。 In view of the circumstances as described above, the present invention relates to a structure in which one axial end portion of a shaft is press-fitted from the other axial side into a coupling hole provided in a base portion of a yoke. In addition, when the shaft, which is tubular, and the base are welded, it is easy to ensure the strength of the weld without deteriorating the mechanical properties of the shaft. Invented to realize a simple structure.
本発明のシャフトと自在継手のヨークとの結合部及びその製造方法のうち、請求項１〜３に記載したシャフトと自在継手のヨークとの結合部は、自在継手を構成するヨークと、シャフトとを備える。
このうちのヨークは、径方向中心部に軸方向に形成された結合孔を有する基部と、この基部の径方向反対側となる２箇所位置から軸方向片側に延出する状態で設けられた１対の腕部とを有する。
又、前記シャフトは、金属材により管状に造られたものであり、軸方向片端部を前記結合孔の軸方向他側からこの結合孔の内側に圧入している。
特に、本発明のシャフトと自在継手のヨークとの結合部に於いては、前記基部のうちで、前記結合孔の軸方向他端部の周囲部分に、この結合孔の残部の周囲部分に比べて径方向の肉厚が小さくなった張り出し筒部が設けられている。
又、前記シャフトのうち、前記結合孔よりも軸方向他側に存在して、この結合孔の外部に露出した部分である露出部のうちの、軸方向片端部に、軸方向他側に隣接する部分に比べて外径寸法が小さくなる事により、この軸方向他側に隣接する部分に比べて径方向の肉厚が小さくなった、薄肉部が設けられている。これと共に、前記シャフトのうち、この薄肉部の軸方向片側に隣接する部分であって、前記結合孔の内側に圧入した部分である圧入部の外径寸法が、前記薄肉部の外径寸法に比べて小さくなっている事により、この圧入部の径方向の肉厚が、この薄肉部の径方向の肉厚に比べて小さくなっている。
更に、請求項１に記載した発明の場合には、追加的に、前記張り出し筒部は、前記結合孔と前記基部の軸方向他側面の内周寄り部分に形成した円環状凹部とにより径方向両側から挟まれた部分に設けられており、前記基部の軸方向他側面のうちで前記円環状凹部よりも外径側の部分は、軸方向に対して直角な平面になっていて、この外径側の部分にこの平面よりも軸方向他側に突出する部分が存在していない。
これに対し、請求項２に記載した発明の場合には、追加的に、前記張り出し筒部は、その外周面の全体が軸方向他側に向かう程外径寸法が小さくなる方向に傾斜した部分円すい状凸面になっている事に基づいて、その径方向の肉厚が軸方向他側に向かう程小さくなっている。
これに対し、請求項３に記載した発明の場合には、追加的に、前記基部の径方向中心部に形成された結合孔がセレーション孔であり、且つ、このセレーション孔のうち軸方向に関して前記張り出し筒部に対応する部分が自由状態（このセレーション孔に前記シャフトの圧入部を圧入していない状態）で内径側に撓んでいる。
又、請求項２〜３に記載した発明を実施する場合に、請求項４に記載した発明の構成を採用する場合には、前記張り出し筒部を、前記基部の軸方向他側面の内周部分から軸方向他側に突出する状態で設ける。そして、この基部の軸方向他側面のうちで前記張り出し筒部よりも外径側の部分を、軸方向に対して直角な平面とし、この外径側の部分にこの平面よりも軸方向他側に突出する部分が存在しない様にする。
この様な本発明のシャフトと自在継手のヨークとの結合部を実施する場合には、例えば、前記ヨークを、金属素材に鍛造加工を施す事により造る事ができる。
Of the coupling portion between the shaft and the universal joint yoke and the manufacturing method thereof according to the present invention, the coupling portion between the shaft and the universal joint yoke according to claims 1 to 3 includes a yoke that constitutes the universal joint, and a shaft. Is provided.
Of these, the yoke is provided with a base portion having a coupling hole formed in the axial direction at the center portion in the radial direction, and extending in one axial direction from two positions opposite to the radial direction of the base portion. And a pair of arms.
The shaft is made of a metal material in a tubular shape, and one end in the axial direction is press-fitted into the inside of the coupling hole from the other axial side of the coupling hole.
In particular, in the connecting portion between the shaft of the present invention and the yoke of the universal joint, the peripheral portion of the other end portion in the axial direction of the connecting hole in the base portion is compared with the peripheral portion of the remaining portion of the connecting hole. An overhanging cylinder portion having a reduced radial thickness is provided.
Also, the shaft is located on the other side in the axial direction than the coupling hole, and is adjacent to the other side in the axial direction at one end in the axial direction of the exposed portion that is exposed to the outside of the coupling hole. A thin-walled portion is provided in which the outer-diameter dimension is smaller than that of the portion to be reduced, and the thickness in the radial direction is smaller than the portion adjacent to the other side in the axial direction. At the same time, the outer diameter dimension of the press-fitting part, which is a part adjacent to one side in the axial direction of the thin part of the shaft and is the part press-fitted inside the coupling hole, is the outer diameter dimension of the thin part. By being smaller, the radial thickness of the press-fit portion is smaller than the radial thickness of the thin portion.
Further, in the case of the invention described in claim 1, additionally, the projecting tube portion is radially formed by the coupling hole and an annular recess formed in an inner peripheral portion of the other axial side surface of the base portion. Of the other side surface in the axial direction of the base portion, the portion on the outer diameter side of the annular recess is a flat surface perpendicular to the axial direction. There is no portion projecting to the other side in the axial direction from this plane in the radial portion.
On the other hand, in the case of the invention described in claim 2, in addition, the overhanging cylindrical portion is a portion inclined in a direction in which the outer diameter decreases as the entire outer peripheral surface thereof moves toward the other side in the axial direction. Based on the conical convex surface, the radial thickness decreases toward the other side in the axial direction.
On the other hand, in the case of the invention described in claim 3, additionally, the coupling hole formed in the radial center portion of the base portion is a serration hole, and the axial direction of the serration holes is the above-mentioned A portion corresponding to the overhanging cylindrical portion is bent toward the inner diameter side in a free state (a state where the press-fitted portion of the shaft is not press-fitted into the serration hole).
Further, when the invention described in claims 2 to 3 is carried out and the configuration of the invention described in claim 4 is adopted, the overhanging cylinder portion is connected to the inner peripheral portion of the other side surface in the axial direction of the base portion. Provided in a state protruding from the other side in the axial direction. In the other axial side surface of the base portion, a portion on the outer diameter side of the projecting cylindrical portion is a plane perpendicular to the axial direction, and the outer diameter side portion is positioned on the outer diameter side portion on the other side in the axial direction. Make sure there are no protruding parts .
When such a joint portion between the shaft of the present invention and the yoke of the universal joint is implemented, for example, the yoke can be manufactured by forging a metal material.
又、前記張り出し筒部と前記シャフトとを溶接する事もできる。 Further, the projecting tube portion and the shaft can be welded.
又、本発明のうち、請求項５に記載したシャフトと自在継手のヨークとの結合部の製造方法は、前記セレーション孔を形成する為、前記基部の径方向中心部に円孔を形成した後、この円孔の内周面に、軸方向他側から軸方向片側に向けてブローチ加工を施す。そして、前記セレーション孔のうち軸方向に関して前記張り出し筒部に対応する部分を自由状態で内径側に撓ませる。 According to the fifth aspect of the present invention, in the method for manufacturing the joint portion between the shaft and the universal joint yoke, the serration hole is formed, so that a circular hole is formed in the central portion in the radial direction of the base portion. Then, broaching is performed on the inner peripheral surface of the circular hole from the other side in the axial direction toward one side in the axial direction. And the part corresponding to the said overhang | projection cylinder part regarding the axial direction among the said serration holes is bent to an internal diameter side in a free state.
上述の様に構成する本発明のシャフトと自在継手のヨークとの結合部の場合には、ヨークの基部に設けた張り出し筒部の存在に基づいて、この基部のうち、結合孔の軸方向他端部の周囲部分の径方向に関する剛性が、この結合孔の残部の周囲部分の同方向の剛性に比べて低くなっている。この為、前記結合孔とシャフトの軸方向片端部に設けられた圧入部との嵌合部の軸方向他端部に於ける面圧を抑えられる。この結果、前記シャフトの軸方向片端寄り部分で、この面圧が作用している領域と作用していない領域との境界部分に加わる剪断応力を抑えられる。 In the case of the coupling portion between the shaft of the present invention configured as described above and the yoke of the universal joint, the axial direction of the coupling hole in the base portion is determined based on the presence of the overhanging cylindrical portion provided at the base portion of the yoke. The rigidity in the radial direction of the peripheral portion of the end portion is lower than the rigidity in the same direction of the peripheral portion of the remaining portion of the coupling hole. For this reason, the surface pressure at the other axial end portion of the fitting portion between the coupling hole and the press-fit portion provided at one axial end portion of the shaft can be suppressed. As a result, the shear stress applied to the boundary portion between the region where the surface pressure is acting and the region where the surface pressure is not acting can be suppressed near the one end of the shaft in the axial direction.
又、請求項２に記載した発明の場合には、ヨークの基部に設けた張り出し筒部の存在に基づいて、この基部のうち、結合孔の軸方向他端部の周囲部分の径方向に関する剛性が、この結合孔の残部の周囲部分の同方向の剛性に比べて低くなっているだけでなく、軸方向他側に向かう程低くなっている。この為、前記結合孔とシャフトの圧入部との嵌合部の軸方向他端部に於ける面圧を、より効果的に抑えられる。即ち、前記張り出し筒部を有しない構造の場合、前記嵌合部の軸方向他端部に於ける面圧は、前記図１１の下部に示した様に、軸方向他端縁部分で、特に大きくなる。これに対して、請求項２に記載した発明の場合、前記結合孔の軸方向他端部の周囲部分の径方向に関する剛性は、この結合孔の残部の周囲部分の同方向の剛性に比べて低くなっているだけでなく、軸方向他側に向かう程低くなっている。この為、この様な剛性分布に基づいて、前記嵌合部の軸方向他端部に於ける面圧を抑えられる効果は、軸方向他側に向かう程大きくなる。従って、請求項２に記載した発明の場合には、嵌合部の軸方向他端部に於ける面圧を、より効果的に抑えられる。言い換えれば、この嵌合部の軸方向他端部に於ける面圧のうち、軸方向他端縁部分に於ける面圧を重点的に抑えられる。この結果、前記シャフトの軸方向片端寄り部分で、この面圧が作用している領域と作用していない領域との境界部分に加わる剪断応力を十分に抑えられる。又、請求項２に記載した発明の場合、前記張り出し筒部の径方向の肉厚は、軸方向他側に向かう程小さくなっている。この為、前記嵌合部の軸方向他端縁部分に於ける面圧を十分に抑えるべく、前記張り出し筒部の軸方向他端縁部分（先端部分）の径方向の肉厚を十分に小さくする場合でも、この張り出し筒部の軸方向片端縁部分（根元部分）の径方向の肉厚を十分に確保する事が容易となる。この結果、この根元部分の強度を十分に確保する事が容易となる。 Further, in the case of the invention described in claim 2 , on the basis of the presence of the overhanging cylindrical portion provided at the base portion of the yoke, the rigidity in the radial direction of the peripheral portion of the other end portion in the axial direction of the coupling hole in the base portion. However, it is not only lower than the rigidity in the same direction of the peripheral portion of the remaining portion of the coupling hole, but also becomes lower toward the other side in the axial direction. For this reason, the surface pressure at the other axial end of the fitting portion between the coupling hole and the press-fitting portion of the shaft can be more effectively suppressed. That is, in the case of the structure having no projecting cylindrical portion, the surface pressure at the other axial end portion of the fitting portion is particularly at the other axial end edge portion as shown in the lower part of FIG. growing. On the other hand, in the case of the invention described in claim 2 , the rigidity in the radial direction of the peripheral portion of the other end in the axial direction of the coupling hole is larger than the rigidity in the same direction of the peripheral portion of the remaining portion of the coupling hole. Not only is it lower, it is lower toward the other side in the axial direction. For this reason, the effect of suppressing the surface pressure at the other end in the axial direction of the fitting portion based on such a stiffness distribution becomes larger toward the other side in the axial direction. Therefore, in the case of the invention described in claim 2 , the surface pressure at the other axial end of the fitting portion can be more effectively suppressed. In other words, out of the surface pressure at the other axial end portion of the fitting portion, the surface pressure at the other axial end edge portion can be preferentially suppressed. As a result, the shear stress applied to the boundary portion between the region where the surface pressure is acting and the region where the surface pressure is not acting can be sufficiently suppressed at a portion near one end of the shaft in the axial direction. Further, in the case of the invention described in claim 2 , the radial thickness of the overhanging cylinder portion becomes smaller toward the other side in the axial direction. For this reason, in order to sufficiently suppress the surface pressure at the other end edge portion in the axial direction of the fitting portion, the radial thickness of the other end edge portion (tip portion) in the axial direction of the projecting tube portion is sufficiently small. Even in this case, it is easy to sufficiently secure the radial thickness of one end edge portion (root portion) in the axial direction of the projecting cylindrical portion. As a result, it becomes easy to sufficiently secure the strength of the root portion.
又、請求項４に記載した発明の場合には、ヨークの基部の軸方向他側面のうちで張り出し筒部よりも外径側の部分を、軸方向に対して直角な平面として、この平面よりも軸方向他側に突出する部分が存在しない様にしている。この為、当該外径側の部分を、内径側に向かう程軸方向他側に突出する方向に傾斜した凸曲面とする場合に比べて、前記各基部の軸方向寸法を短くできる。従って、その分だけ、前記ヨークを小型に構成できる。 Further, in the case of the invention described in claim 4 , of the other side surface in the axial direction of the base portion of the yoke, the portion on the outer diameter side of the projecting tube portion is a plane perpendicular to the axial direction. Also, there is no portion protruding on the other side in the axial direction. For this reason, the axial dimension of each said base part can be shortened compared with the case where the said outer diameter side part is made into the convex curved surface inclined in the direction which protrudes in an axial direction other side as it goes to an inner diameter side. Accordingly, the yoke can be made smaller by that amount.
又、請求項３に記載した発明の様に、結合孔をセレーション孔とする場合で、このセレーション孔を、請求項５に記載した製造方法により形成すれば、このセレーション孔の形成に伴い、基部のうちで比較的剛性の低い部分である張り出し筒部が、内径側に撓む。つまり、前記セレーション孔のうち、軸方向に関して前記張り出し筒部に対応する部分が、自由状態で内径側に撓んだ状態となる。この結果、使用に伴う摩耗によって、前記セレーション孔のセレーション山高さが減少した場合でも、前記張り出し筒部に対応する部分（内径側に撓んだ部分）で、前記セレーション孔とシャフトの圧入部の外周面とを、がたつきなく噛み合い続けさせる事ができる。即ち、使用に伴って生じた前記セレーション孔の摩耗に拘らず、このセレーション孔と前記シャフトの圧入部との嵌合部でがたつきが発生する事を抑制できる。 Further, as in the invention described in claim 3 , when the serration hole is formed as a serration hole and the serration hole is formed by the manufacturing method described in claim 5 , the base portion is formed along with the formation of the serration hole. Of these, the overhanging cylinder portion, which is a relatively low rigidity portion, bends toward the inner diameter side. In other words, a portion of the serration hole corresponding to the projecting tube portion in the axial direction is bent to the inner diameter side in a free state. As a result, even when the serration peak height of the serration hole is reduced due to wear caused by use, the serration hole and the press-fitting portion of the shaft are in a portion corresponding to the projecting cylindrical portion (a portion bent toward the inner diameter side). The outer peripheral surface can be continuously engaged without rattling. That is, it is possible to suppress the occurrence of rattling at the fitting portion between the serration hole and the press-fitting portion of the shaft regardless of the wear of the serration hole caused by use.
又、本発明の場合には、前記シャフトを管状のものとする為、このシャフトと張り出し筒部との径方向の肉厚差を、小さくする事ができる。この為、この様な構造を対象として、前記シャフトと前記張り出し筒部とを溶接すれば、これらシャフトと張り出し筒部との双方の側で、溶接部の溶け込み量をバランス良く確保する事が容易となる。更には、これら両部位の溶接後の冷却速度を同程度にする事も容易となる。この為、前記シャフトの機械的性質を悪化させる事なく、前記溶接部の強度を確保する事が容易となる。 In the case of the present invention, since the shaft is tubular, the radial thickness difference between the shaft and the overhanging cylindrical portion can be reduced. For this reason, if the shaft and the overhanging cylinder part are welded to such a structure, it is easy to ensure a good amount of penetration of the welded part on both sides of the shaft and the overhanging cylinder part. It becomes. Furthermore, it becomes easy to make the cooling rate after welding of these both parts comparable. For this reason, it becomes easy to ensure the strength of the welded portion without deteriorating the mechanical properties of the shaft.
［本発明の実施の形態の第１例］
図１〜４は、本発明の実施の形態の第１例を示している。尚、本例の特徴は、主として、ヨーク８ａを構成する基部１０ａの軸方向他端部の構造にある。その他の部分の構造及び作用は、前述の図１１〜１３に示した従来構造の場合と同様であるから、同等部分には同一符号を付して、重複する説明を省略若しくは簡略にし、以下、本例の特徴部分を中心に説明する。
[First example of embodiment of the present invention]
1 to 4 show a first example of an embodiment of the present invention. The feature of this example is mainly the structure of the other axial end portion of the base portion 10a constituting the yoke 8a. Since the structure and operation of the other parts are the same as in the case of the conventional structure shown in FIGS. 11 to 13 described above, the same parts are denoted by the same reference numerals, and redundant description is omitted or simplified. The description will focus on the features of this example.
本例の場合には、前記基部１０ａのうちで、セレーション孔１２の軸方向他端部の周囲部分に、このセレーション孔１２の残部（軸方向中間部乃至片端部）の周囲部分に比べて径方向の肉厚が小さくなった張り出し筒部１６を、鍛造加工により形成している。特に、本例の場合には、この張り出し筒部１６の外周面の全体を、軸方向他側に向かう程径寸法が小さくなる方向に傾斜した部分円すい状凸面とする事に基づいて、この張り出し筒部１６の径方向の肉厚ｔ16を、軸方向他側に向かう程小さくなる様にしている。従って、本例の場合、前記基部１０ａの径方向に関する剛性は、前記セレーション孔１２の軸方向他端部の周囲部分（前記張り出し筒部１６に対応する部分）で、このセレーション孔１２の残部の周囲部分に比べて低くなっている。更に、前記基部１０ａのうち、このセレーション孔１２の軸方向他端部の周囲部分の剛性は、軸方向他側に向かう程低くなっている。 In the case of this example, the diameter of the base portion 10a in the peripheral portion of the other axial end portion of the serration hole 12 is larger than the peripheral portion of the remaining portion of the serration hole 12 (the intermediate portion in the axial direction or one end portion). The overhanging cylinder portion 16 having a reduced thickness in the direction is formed by forging. In particular, in the case of the present example, the entire outer peripheral surface of the projecting cylindrical portion 16 is formed as a partially conical convex surface that is inclined in a direction in which the diameter dimension decreases toward the other side in the axial direction. the radial thickness t 16 of the cylindrical portion 16, and the like becomes smaller as toward the other axial side. Therefore, in the case of this example, the rigidity in the radial direction of the base portion 10a is the peripheral portion of the other end portion in the axial direction of the serration hole 12 (the portion corresponding to the projecting cylindrical portion 16). It is lower than the surrounding area. Furthermore, the rigidity of the peripheral part of the axial part other end part of this serration hole 12 among the said base parts 10a is so low that it goes to an axial direction other side.
又、本例の場合には、前記張り出し筒部１６の径方向の肉厚ｔ16を、前記基部１０ａの残部の径方向の肉厚ｔ10aの、１／３〜１／２程度｛ｔ16≒（１／３〜１／２）ｔ10a｝としている。これにより、前記張り出し筒部１６の径方向の肉厚ｔ16を、シャフト９ａの軸方向片端寄り部分の径方向の肉厚ｔ9に近づける事で、これら両肉厚の差ｔ16−ｔ9が、十分に小さくなる様にしている。又、本例の場合、前記基部１０ａの軸方向他側面のうちで、前記張り出し筒部１６よりも外径側の部分を、軸方向に対して直角な平面１７として、この外径側の部分に、この平面１７よりも軸方向他側に突出する部分が存在しない様にしている。
又、本例の場合、前記シャフト９ａのうち、結合孔である前記セレーション孔１２よりも軸方向他側に存在して、このセレーション孔１２の外部に露出した部分を、露出部２０としている。又、この露出部２０のうちの、軸方向片端部を、軸方向他側に隣接する部分に比べて外径寸法が小さくなる事により、この軸方向他側に隣接する部分に比べて径方向の肉厚が小さくなった、薄肉部２１としている。これと共に、前記シャフト９ａのうち、この薄肉部２１の軸方向片側に隣接する部分であって、前記セレーション孔１２の内側に圧入した部分である圧入部２２の外径寸法を、前記薄肉部２１の外径寸法よりも小さくする事により、この圧入部２２の径方向の肉厚を、この薄肉部２１の径方向の肉厚よりも小さくしている。
又、本例の場合、前記張り出し筒部１６の外周面と前記シャフト９ａの軸方向片端寄り部分の外周面との間に溶接金属１５を掛け渡す状態で、これら張り出し筒部１６とシャフト９ａとを溶接している。
In the case of this example, the radial thickness t 16 of the overhanging cylinder portion 16 is about 1/3 to 1/2 of the radial thickness t 10a of the remaining portion of the base portion 10a {t 16 ≈ (1/3 to 1/2) t 10a }. Thus, the radial thickness t 16 of the projecting tubular portion 16, by which close to the radial direction of the wall thickness t 9 of the axial one end portion close of the shaft 9a, the difference t 16 -t 9 of both wall thickness However, it is made small enough. In the case of this example, of the other side surface in the axial direction of the base portion 10a, a portion on the outer diameter side of the projecting cylindrical portion 16 is a plane 17 perpendicular to the axial direction, and this outer diameter side portion. In addition, there is no portion protruding from the plane 17 to the other side in the axial direction.
In the case of this example, a portion of the shaft 9 a that is present on the other side in the axial direction than the serration hole 12 that is a coupling hole and is exposed to the outside of the serration hole 12 is an exposed portion 20. Moreover, the axial direction one end part of this exposed part 20 becomes radial direction compared with the part adjacent to this axial direction other side by reducing an outer diameter dimension compared with the part adjacent to the axial direction other side. The thickness of the thin portion 21 is reduced. At the same time, the outer diameter dimension of the press-fitted portion 22, which is a portion adjacent to one side in the axial direction of the thin-walled portion 21 of the shaft 9 a and is a portion press-fitted inside the serration hole 12, is set to The thickness in the radial direction of the press-fit portion 22 is made smaller than the thickness in the radial direction of the thin-walled portion 21 by making it smaller than the outer diameter dimension of the thin-walled portion 21.
In the case of this example, in the state where the weld metal 15 is stretched between the outer peripheral surface of the projecting cylindrical portion 16 and the outer peripheral surface of the shaft 9a near one end in the axial direction, the projecting cylindrical portion 16 and the shaft 9a Welding.
上述の様に構成する本例のシャフトと自在継手のヨークとの結合部の場合には、前記ヨーク８ａの基部１０ａに設けた張り出し筒部１６の存在に基づいて、この基部１０ａのうち、前記セレーション孔１２の軸方向他端部の周囲部分の径方向に関する剛性が、このセレーション孔１２の残部の周囲部分の同方向の剛性に比べて低くなっているだけでなく、軸方向他側に向かう程低くなっている。この為、図１の下部に示す様に、前記セレーション孔１２と前記雄セレーション部１４との係合部の軸方向他端部に於ける面圧を、効果的に抑えられる。即ち、前記張り出し筒部１６を有しない構造の場合、前記係合部の軸方向他端部に於ける面圧は、前記図１１の下部に示した様に、軸方向他端縁部分で、特に大きくなる。これに対して、本例の場合、前記セレーション孔１２の軸方向他端部の周囲部分の径方向に関する剛性は、このセレーション孔１２の残部の周囲部分の同方向の剛性に比べて低くなっているだけでなく、軸方向他側に向かう程低くなっている。この為、この様な剛性分布に基づいて、前記係合部の軸方向他端部に於ける面圧を抑えられる効果は、軸方向他側に向かう程大きくなる。従って、本例の場合には、前記係合部の軸方向他端部に於ける面圧を、効果的に抑えられる。言い換えれば、この係合部の軸方向他端部に於ける面圧のうち、軸方向他端縁部分に於ける面圧ＰEを重点的に抑えられる。この結果、前記シャフト９ａの軸方向片端寄り部分で、この面圧が作用している領域と作用していない領域との境界部分に加わる剪断応力を十分に抑えられる。又、本例の場合、前記張り出し筒部１６の径方向の肉厚は、軸方向他側に向かう程小さくなっている。この為、前記係合部の軸方向他端縁部分に於ける面圧ＰEを十分に抑えるべく、前記張り出し筒部１６の軸方向他端縁部分（先端部分）の径方向の肉厚を十分に小さくする場合でも、この張り出し筒部１６の軸方向片端縁部分（根元部分）の径方向の肉厚を十分に確保する事が容易となる。この結果、この根元部分の強度を十分に確保する事が容易となる。
尚、本例を実施する場合、前記基部１０ａの中心軸に対する前記張り出し筒部１６の外周面の傾斜角度θ（図１）は、１０〜８０度程度の任意の角度で良く、４５度程度（例えば４０〜５０度）が望ましい。
In the case of the joint portion between the shaft of this example configured as described above and the yoke of the universal joint, the base portion 10a includes the overhanging cylindrical portion 16 provided on the base portion 10a. The rigidity in the radial direction of the peripheral portion of the other axial end portion of the serration hole 12 is not only lower than the rigidity in the same direction of the peripheral portion of the remaining portion of the serration hole 12, but also toward the other side in the axial direction. It is so low. For this reason, as shown in the lower part of FIG. 1, the surface pressure at the other axial end of the engaging portion between the serration hole 12 and the male serration portion 14 can be effectively suppressed. That is, in the case of the structure not having the overhanging cylinder portion 16, the surface pressure at the other axial end portion of the engaging portion is, as shown in the lower part of FIG. Especially big. On the other hand, in this example, the rigidity in the radial direction of the peripheral portion of the other axial end portion of the serration hole 12 is lower than the rigidity in the same direction of the peripheral portion of the remaining portion of the serration hole 12. Not only that, but it goes lower toward the other side in the axial direction. For this reason, the effect of suppressing the surface pressure at the other axial end portion of the engaging portion based on such a rigidity distribution becomes larger toward the other side in the axial direction. Therefore, in the case of this example, the surface pressure at the other axial end of the engaging portion can be effectively suppressed. In other words, among the in surface pressure in the axial direction other end portion of the engaging portion, is suppressed emphatically in surface pressure P E in the axial end edge portions. As a result, the shear stress applied to the boundary portion between the region where the surface pressure is acting and the region where the surface pressure is not acting can be sufficiently suppressed at the portion near one end of the shaft 9a in the axial direction. Further, in the case of this example, the radial thickness of the overhanging cylinder portion 16 becomes smaller toward the other side in the axial direction. Therefore, in order to suppress the engagement of in surface pressure P E in sufficient axial end edge portion of the engagement portion, the radial thickness of the other axial end edge portions of the projecting tubular portion 16 (tip portion) Even when it is made sufficiently small, it is easy to secure a sufficient radial thickness of one end edge portion (root portion) in the axial direction of the overhanging cylinder portion 16. As a result, it becomes easy to sufficiently secure the strength of the root portion.
In the case of implementing this example, the inclination angle θ (FIG. 1) of the outer peripheral surface of the overhanging cylinder portion 16 with respect to the central axis of the base portion 10a may be an arbitrary angle of about 10 to 80 degrees, and about 45 degrees ( For example, 40 to 50 degrees) is desirable.
又、本例の場合には、前記基部１０ａの軸方向他側面のうちで、前記張り出し筒部１６よりも外径側の部分を、軸方向に対して直角な平面１７としている。この為、当該外径側の部分を、内径側に向かう程軸方向他側に突出する方向に傾斜した凸曲面とする場合に比べて、前記基部１０ａの軸方向寸法を短くできる。従って、その分だけ、前記ヨーク８ａを小型に構成できる。 In the case of this example, of the other axial side surface of the base portion 10a, a portion on the outer diameter side of the projecting cylindrical portion 16 is a plane 17 perpendicular to the axial direction. For this reason, the axial dimension of the base portion 10a can be shortened as compared with the case where the outer diameter side portion is a convex curved surface that is inclined in a direction protruding toward the other side in the axial direction toward the inner diameter side. Therefore, the yoke 8a can be reduced in size accordingly.
又、本例の場合には、前記張り出し筒部１６と前記シャフト９ａの軸方向片端寄り部分との径方向の肉厚差ｔ16−ｔ9を十分に小さくする（シャフト９ａの軸方向片端寄り部分の肉厚に比べて、張り出し筒部１６の肉厚が大きい程度を少なくする）と共に、これら張り出し筒部１６の外周面とシャフト９ａの軸方向片端寄り部分の外周面との間に溶接金属１５を掛け渡す状態で、これら張り出し筒部１６とシャフト９ａとを溶接している。この為、前記面圧ＰEを抑えられるだけでなく、これらシャフト９ａと張り出し筒部１６との双方の側で、溶接部の溶け込み量をバランス良く確保する事が容易となる。即ち、本例の場合には、図２に矢印で示す様に、前記張り出し筒部１６を集中的に加熱する事ができる為、この張り出し筒部１６の外周面及び先端面の溶け込み量を、前記シャフト９ａの軸方向片端寄り部外周面の溶け込み量と同程度に多くする事が容易となる。更には、これら両部位の溶接後の冷却速度を同程度にする事も容易となる。この為、前記シャフト９ａの機械的性質を悪化させる事なく、このシャフト９ａと前記張り出し筒部１６との溶接部の強度を確保する事が容易となる。 In the case of this example, the radial thickness difference t 16 -t 9 between the overhanging cylinder portion 16 and the portion near the one axial end of the shaft 9a is made sufficiently small (near the one axial end of the shaft 9a). The thickness of the overhanging cylinder portion 16 is reduced compared to the thickness of the portion), and the weld metal between the outer peripheral surface of the overhanging cylinder portion 16 and the outer peripheral surface of the shaft 9a near one end in the axial direction. These overhanging cylinder parts 16 and the shaft 9a are welded in a state where 15 is applied. Therefore, not only suppress the surface pressure P E, at both sides of these shafts 9a and projecting tubular portion 16, it is easy to be good balance ensure penetration of the weld. That is, in the case of this example, as shown by the arrow in FIG. 2, the overhanging cylinder part 16 can be heated intensively. It becomes easy to increase to the same extent as the amount of penetration of the outer peripheral surface near the one end of the shaft 9a in the axial direction. Furthermore, it becomes easy to make the cooling rate after welding of these both parts comparable. For this reason, it becomes easy to ensure the strength of the welded portion between the shaft 9a and the overhanging cylinder portion 16 without deteriorating the mechanical properties of the shaft 9a.
尚、上述した実施の形態の第１例の構造を実施する場合で、図５の上部に示す様に、張り出し筒部１６の外周面とシャフト９ａの軸方向片端寄り部外周面との溶接部の溶け込み量を、前記図１の上部に示した場合よりも多くする溶接条件を設定すれば、溶け込み量が増えた分だけ、張り出し筒部１６の径方向の肉厚をより小さくする事ができる。この結果、図５の下部に示す様に、前記セレーション孔１２と前記雄セレーション部１４との係合部の軸方向他端縁部分に於ける面圧ＰEをより低く抑え、前記シャフト９ａの軸方向片端寄り部分に作用する剪断応力をより十分に抑えられる。 In the case of implementing the structure of the first example of the above-described embodiment, as shown in the upper part of FIG. 5, the welded portion between the outer peripheral surface of the overhanging cylindrical portion 16 and the outer peripheral surface of the shaft 9a near one end in the axial direction. If the welding conditions are set to increase the amount of penetration of the steel tube more than that shown in the upper part of FIG. 1, the thickness in the radial direction of the overhanging cylinder portion 16 can be made smaller by the amount of the penetration. . As a result, as shown in the lower part of FIG. 5, further suppressed low in surface pressure P E in the axial end edge portions of the engaging portion between the serration hole 12 and the male serration portion 14, the shaft 9a The shear stress acting on the portion near one end in the axial direction can be more sufficiently suppressed.
又、本発明を実施する場合には、上述した実施の形態の第１例の構造で、前記溶接を省略する事もできる。この場合に、好ましくは、請求項５に記載した発明の様に、前記セレーション孔１２を、次の様に形成する。先ず、前記基部１０ａの径方向中心部に円孔を形成する。その後、図６の（ａ）に示す様に、この円孔内にセレーション形成用の工具であるブローチ１８を、軸方向他側から押し込む。これにより、この円孔の内周面に、軸方向他側から軸方向片側に向けてブローチ加工を施す事で、前記セレーション孔１２を形成する。この様にしてセレーション孔１２を形成すると、図６の（ｂ）に誇張して示す様に、前記基部１０ａのうちで比較的剛性の低い部分である、前記張り出し筒部１６が、内径側に撓んだ状態となる。つまり、請求項３に記載した発明の様に、前記セレーション孔１２のうち、軸方向に関して前記張り出し筒部１６に対応する部分が、自由状態で内径側に撓んだ状態となる。この結果、使用に伴う摩耗によって、前記セレーション孔１２及び前記雄セレーション部１４のセレーション山高さが減少した場合でも、前記張り出し筒部１６に対応する部分（内径側に撓んだ部分）で、前記セレーション孔１２と前記雄セレーション部１４とを、がたつきなく噛み合い続けさせる事ができる。即ち、使用に伴って生じた前記セレーション孔１２と前記雄セレーション部１４との摩耗に拘らず、これらセレーション孔１２と雄セレーション部１４との係合部でがたつきが発生する事を抑制できる。
尚、上述の図６に示した様なセレーション孔１２の形成方法は、前記溶接を省略しない構造を得る場合に実施する事もできる。
Moreover, when implementing this invention, the said welding can also be abbreviate | omitted by the structure of the 1st example of embodiment mentioned above. In this case, preferably, as in the invention described in claim 5 , the serration hole 12 is formed as follows. First, a circular hole is formed in the radial center of the base 10a. Thereafter, as shown in FIG. 6A, a broach 18 as a serration forming tool is pushed into the circular hole from the other side in the axial direction. Thus, the serration hole 12 is formed by performing broaching on the inner peripheral surface of the circular hole from the other axial side to the one axial side. When the serration hole 12 is formed in this way, as shown in an exaggerated manner in FIG. 6 (b), the overhanging cylinder portion 16, which is a relatively low rigidity portion of the base portion 10a, is formed on the inner diameter side. It will be in a bent state. That is, as in the invention described in claim 3 , a portion of the serration hole 12 corresponding to the projecting cylindrical portion 16 in the axial direction is bent to the inner diameter side in a free state. As a result, even when the serration height of the serration hole 12 and the male serration portion 14 is reduced due to wear caused by use, the portion corresponding to the overhanging cylinder portion 16 (the portion bent toward the inner diameter side) The serration hole 12 and the male serration portion 14 can be continuously engaged with each other without rattling. That is, it is possible to suppress the occurrence of rattling in the engaging portion between the serration hole 12 and the male serration portion 14 regardless of the wear of the serration hole 12 and the male serration portion 14 that occurs with use. .
Note that the method of forming the serration hole 12 as shown in FIG. 6 can also be carried out when obtaining a structure that does not omit the welding.
［本発明の実施の形態の第２例］
図７〜９は、本発明の実施の形態の第２例を示している。本例の場合も、ヨーク８ｂを構成する基部１０ｂの軸方向他端部の内周部分に、上述した実施の形態の第１例の場合と同様の張り出し筒部１６を設けている。但し、本例の場合には、この張り出し筒部１６の加工方法が、上述した実施の形態の第１例の場合と異なる。即ち、本例の場合には、先ず、鍛造加工により、前記基部１０ｂの軸方向他側面の全体を、軸方向に対して直角な平面１７とする。その後、旋削加工により、この平面１７の内周寄り部分に円環状凹部１９を形成する事で、この円環状凹部１９とセレーション孔１２とにより径方向両側から挟まれた部分を、前記張り出し筒部１６とする。
[Second example of the embodiment of the present invention]
7 to 9 show a second example of the embodiment of the present invention. Also in the case of this example, the overhanging cylindrical portion 16 similar to that in the first example of the above-described embodiment is provided on the inner peripheral portion of the other axial end portion of the base portion 10b constituting the yoke 8b. However, in the case of this example, the processing method of this overhanging cylinder part 16 is different from the case of the first example of the embodiment described above. That is, in the case of this example, first, the entire other side surface in the axial direction of the base portion 10b is made into a plane 17 perpendicular to the axial direction by forging. Thereafter, an annular recess 19 is formed in a portion near the inner periphery of the flat surface 17 by turning, so that a portion sandwiched from both sides in the radial direction by the annular recess 19 and the serration hole 12 can be 16
この様な本例の場合には、前記張り出し筒部１６の加工方法を、鍛造から旋削に変更した事に伴い、この張り出し筒部１６を設計通りの所望形状に造る事が容易となる。又、本例の場合には、前記張り出し筒部１６を形成した後の、前記基部１０ｂの軸方向他側面のうちで、前記円環状凹部１９よりも外径側の部分（つまり、前記張り出し筒部１６を形成する前の、前記基部１０ｂの軸方向他側面）を、軸方向に対して直角な平面１７として、
当該外径側の部分に、この平面１７よりも軸方向他側に突出する部分が存在しない様にしている。この為、当該外径側の部分を、内径側に向かう程軸方向他側に突出する方向に傾斜した凸曲面とする場合に比べて、前記基部１０ｂの軸方向寸法を短くできる。従って、その分だけ、前記ヨーク８ｂを小型に構成できる。その他の部分の構造及び作用は、上述した実施の形態の第１例の場合と同様である。
In the case of this example, as the processing method of the overhang cylinder portion 16 is changed from forging to turning, it becomes easy to make the overhang cylinder portion 16 into a desired shape as designed. Further, in the case of this example, the portion on the outer diameter side of the annular recess 19 in the other axial side surface of the base portion 10b after the projecting tube portion 16 is formed (that is, the projecting tube). The other side surface in the axial direction of the base portion 10b before forming the portion 16 is defined as a plane 17 perpendicular to the axial direction.
In the outer diameter side portion, there is no portion protruding from the flat surface 17 to the other side in the axial direction. For this reason, the axial dimension of the base portion 10b can be shortened as compared with the case where the outer diameter side portion is a convex curved surface that is inclined in a direction protruding toward the other side in the axial direction toward the inner diameter side. Therefore, the yoke 8b can be reduced in size accordingly. The structure and operation of the other parts are the same as in the case of the first example of the embodiment described above.
上述した実施の形態の各例では、結合孔をセレーション孔とし、シャフトの軸方向片端部外周面を雄セレーション部として、これらセレーション孔と雄セレーション部とを締め代を持たせて係合させる構造を採用した。但し、本発明を実施する場合には、結合孔の内周面とシャフトの軸方向片端部外周面とをそれぞれ円筒面とし、これら両円筒面同士を締り嵌めで嵌合させる構成や、結合孔の内周面とシャフトの軸方向片端部外周面とのうちの一方の周面を円筒面とし、他方の周面にセレーションを形成して、この円筒面にこのセレーションを圧入に基づいて食い込ませる構成を採用する事もできる。
又、本発明を実施する場合、ヨークとシャフトとを溶接する事は、必須の要件ではない。これらヨークとシャフトとの分離防止は、これらヨークの結合孔とシャフトの軸方向片端部との嵌合部に作用する摩擦力のみによって図る事もできるし、或いは、この摩擦力に加えて、前記シャフトの軸方向片端部に形成したかしめ部と前記結合孔の開口周縁部との係合によって図る事もできる。
又、本発明を実施する場合、ヨークは、鋼製丸棒等の金属素材に鍛造加工、打ち抜き加工等を施す事により造られたものに限らず、鋼板等の金属板に曲げ加工、打ち抜き加工等を施す事により造られたものとする事もできる。
又、本発明を実施する場合には、前述の図１〜４に示した実施の形態の第１例の張り出し筒部１６を旋削により加工する事もできる。
In each example of the above-described embodiments, the coupling hole is a serration hole, the outer peripheral surface of one axial end portion of the shaft is a male serration portion, and the serration hole and the male serration portion are engaged with a tightening margin. It was adopted. However, when carrying out the present invention, the inner circumferential surface of the coupling hole and the outer circumferential surface of one end of the shaft in the axial direction are respectively cylindrical surfaces, and the two cylindrical surfaces are fitted together by an interference fit, One of the inner peripheral surface of the shaft and the outer peripheral surface of the one axial end portion of the shaft is a cylindrical surface, and serrations are formed on the other peripheral surface, and the serrations are bitten into the cylindrical surface based on press-fitting. A configuration can also be adopted.
Further, when the present invention is implemented, it is not an essential requirement to weld the yoke and the shaft. The prevention of separation between the yoke and the shaft can be achieved only by the frictional force acting on the fitting portion between the coupling hole of the yoke and the one axial end of the shaft, or in addition to the frictional force, It can also be achieved by engaging a caulking portion formed at one axial end portion of the shaft with an opening peripheral edge portion of the coupling hole.
Moreover, when practicing the present invention, the yoke is not limited to a metal material such as a steel round bar, which is made by forging or punching, but bending or punching a metal plate such as a steel plate. It can also be made by applying etc.
Moreover, when implementing this invention, the overhang | projection cylinder part 16 of the 1st example of embodiment shown to above-mentioned FIGS. 1-4 can also be processed by turning.
１ ステアリングホイール
２ ステアリングシャフト
３ 自在継手
４ 中間シャフト
５ ステアリングギヤユニット
６ 入力軸
７ タイロッド
８、８ａ、８ｂ ヨーク
９、９ａ シャフト
１０、１０ａ、１０ｂ 基部
１１ 腕部
１２ セレーション孔
１３ 円孔
１４ 雄セレーション部
１５ 溶接金属
１６ 張り出し筒部
１７ 平面
１８ ブローチ
１９ 円環状凹部
２０ 露出部
２１ 薄肉部
２２ 圧入部
DESCRIPTION OF SYMBOLS 1 Steering wheel 2 Steering shaft 3 Universal joint 4 Intermediate shaft 5 Steering gear unit 6 Input shaft 7 Tie rod 8, 8a, 8b Yoke 9, 9a Shaft 10, 10a, 10b Base part 11 Arm part 12 Serration hole 13 Circular hole 14 Male serration part DESCRIPTION OF SYMBOLS 15 Weld metal 16 Overhang | projection cylinder part 17 Plane 18 Broach 19 Circular recessed part 20 Exposed part 21 Thin part 22 Press-fit part
Claims (5)
このうちのヨークは、径方向中心部に軸方向に形成された結合孔を有する基部と、この基部の径方向反対側となる２箇所位置から軸方向片側に延出する状態で設けられた１対の腕部とを有するものであり、
前記シャフトは、金属材により管状に造られたものであり、軸方向片端部を前記結合孔の軸方向他側からこの結合孔の内側に圧入している
シャフトと自在継手のヨークとの結合部に於いて、
前記基部のうちで、前記結合孔の軸方向他端部の周囲部分に、この結合孔の残部の周囲部分に比べて径方向の肉厚が小さくなった張り出し筒部が設けられており、
前記シャフトのうち、前記結合孔よりも軸方向他側に存在して、この結合孔の外部に露出した部分である露出部のうちの、軸方向片端部に、軸方向他側に隣接する部分に比べて外径寸法が小さくなる事により、この軸方向他側に隣接する部分に比べて径方向の肉厚が小さくなった、薄肉部が設けられていると共に、前記シャフトのうち、この薄肉部の軸方向片側に隣接する部分であって、前記結合孔の内側に圧入した部分である圧入部の外径寸法が、前記薄肉部の外径寸法に比べて小さくなっている事により、この圧入部の径方向の肉厚が、この薄肉部の径方向の肉厚に比べて小さくなっており、
前記張り出し筒部は、前記結合孔と前記基部の軸方向他側面の内周寄り部分に形成した円環状凹部とにより径方向両側から挟まれた部分に設けられており、前記基部の軸方向他側面のうちで前記円環状凹部よりも外径側の部分は、軸方向に対して直角な平面になっていて、この外径側の部分にこの平面よりも軸方向他側に突出する部分が存在していない、
事を特徴とするシャフトと自在継手のヨークとの結合部。 It includes a yoke that forms a universal joint, and a shaft.
Of these, the yoke is provided with a base portion having a coupling hole formed in the axial direction at the center portion in the radial direction, and extending in one axial direction from two positions opposite to the radial direction of the base portion. A pair of arms,
The shaft is made of a metal material in a tubular shape, and one end portion in the axial direction is press-fitted into the inside of the coupling hole from the other axial side of the coupling hole. A coupling portion between the shaft and the yoke of the universal joint In
Of the base, an overhanging cylinder part having a radial thickness smaller than that of the peripheral part of the remaining part of the coupling hole is provided in a peripheral part of the other axial end part of the coupling hole,
Of the exposed portion of the shaft that is on the other side in the axial direction than the coupling hole and exposed to the outside of the coupling hole, a portion adjacent to the other axial direction end on one axial end Compared to the portion adjacent to the other side in the axial direction, the outer diameter is smaller, and the thickness in the radial direction is smaller than the portion adjacent to the other side in the axial direction. This is because the outer diameter dimension of the press-fitting part, which is a part adjacent to one side in the axial direction of the part and is the part press-fitted inside the coupling hole, is smaller than the outer diameter dimension of the thin-walled part. The radial thickness of the press-fit part is smaller than the radial thickness of this thin part ,
The projecting cylindrical portion is provided in a portion sandwiched from both sides in the radial direction by the coupling hole and an annular recess formed in an inner circumferential portion of the other axial side surface of the base portion. Of the side surface, the portion on the outer diameter side of the annular recess is a plane perpendicular to the axial direction, and the portion protruding on the other side in the axial direction from this plane is formed on the outer diameter side portion. Does not exist,
The joint between the shaft and the universal joint yoke.
このうちのヨークは、径方向中心部に軸方向に形成された結合孔を有する基部と、この基部の径方向反対側となる２箇所位置から軸方向片側に延出する状態で設けられた１対の腕部とを有するものであり、
前記シャフトは、金属材により管状に造られたものであり、軸方向片端部を前記結合孔の軸方向他側からこの結合孔の内側に圧入している
シャフトと自在継手のヨークとの結合部に於いて、
前記基部のうちで、前記結合孔の軸方向他端部の周囲部分に、この結合孔の残部の周囲部分に比べて径方向の肉厚が小さくなった張り出し筒部が設けられており、
前記シャフトのうち、前記結合孔よりも軸方向他側に存在して、この結合孔の外部に露出した部分である露出部のうちの、軸方向片端部に、軸方向他側に隣接する部分に比べて外径寸法が小さくなる事により、この軸方向他側に隣接する部分に比べて径方向の肉厚が小さくなった、薄肉部が設けられていると共に、前記シャフトのうち、この薄肉部の軸方向片側に隣接する部分であって、前記結合孔の内側に圧入した部分である圧入部の外径寸法が、前記薄肉部の外径寸法に比べて小さくなっている事により、この圧入部の径方向の肉厚が、この薄肉部の径方向の肉厚に比べて小さくなっており、
前記張り出し筒部は、その外周面の全体が軸方向他側に向かう程外径寸法が小さくなる方向に傾斜した部分円すい状凸面になっている事に基づいて、その径方向の肉厚が軸方向他側に向かう程小さくなっている、
事を特徴とするシャフトと自在継手のヨークとの結合部。 It includes a yoke that forms a universal joint, and a shaft.
Of these, the yoke is provided with a base portion having a coupling hole formed in the axial direction at the center portion in the radial direction, and extending in one axial direction from two positions opposite to the radial direction of the base portion. A pair of arms,
The shaft is made of a metal material in a tubular shape, and one end portion in the axial direction is press-fitted into the inside of the coupling hole from the other axial side of the coupling hole. A coupling portion between the shaft and the yoke of the universal joint In
Of the base, an overhanging cylinder part having a radial thickness smaller than that of the peripheral part of the remaining part of the coupling hole is provided in a peripheral part of the other axial end part of the coupling hole,
Of the exposed portion of the shaft that is on the other side in the axial direction than the coupling hole and exposed to the outside of the coupling hole, a portion adjacent to the other axial direction end on one axial end Compared to the portion adjacent to the other side in the axial direction, the outer diameter is smaller, and the thickness in the radial direction is smaller than the portion adjacent to the other side in the axial direction. This is because the outer diameter dimension of the press-fitting part, which is a part adjacent to one side in the axial direction of the part and is the part press-fitted inside the coupling hole, is smaller than the outer diameter dimension of the thin-walled part. The radial thickness of the press-fit part is smaller than the radial thickness of this thin part ,
The overhanging cylindrical portion is a partial conical convex surface that is inclined in a direction in which the outer diameter dimension decreases as the entire outer peripheral surface moves toward the other side in the axial direction. The direction becomes smaller toward the other side,
The joint between the shaft and the universal joint yoke.
このうちのヨークは、径方向中心部に軸方向に形成された結合孔を有する基部と、この基部の径方向反対側となる２箇所位置から軸方向片側に延出する状態で設けられた１対の腕部とを有するものであり、
前記シャフトは、金属材により管状に造られたものであり、軸方向片端部を前記結合孔の軸方向他側からこの結合孔の内側に圧入している
シャフトと自在継手のヨークとの結合部に於いて、
前記基部のうちで、前記結合孔の軸方向他端部の周囲部分に、この結合孔の残部の周囲部分に比べて径方向の肉厚が小さくなった張り出し筒部が設けられており、
前記シャフトのうち、前記結合孔よりも軸方向他側に存在して、この結合孔の外部に露出した部分である露出部のうちの、軸方向片端部に、軸方向他側に隣接する部分に比べて外径寸法が小さくなる事により、この軸方向他側に隣接する部分に比べて径方向の肉厚が小さくなった、薄肉部が設けられていると共に、前記シャフトのうち、この薄肉部の軸方向片側に隣接する部分であって、前記結合孔の内側に圧入した部分である圧入部の外径寸法が、前記薄肉部の外径寸法に比べて小さくなっている事により、この圧入部の径方向の肉厚が、この薄肉部の径方向の肉厚に比べて小さくなっており、
前記基部の径方向中心部に形成された結合孔がセレーション孔であり、且つ、このセレーション孔のうち軸方向に関して前記張り出し筒部に対応する部分が自由状態で内径側に撓んでいる、
事を特徴とするシャフトと自在継手のヨークとの結合部。 It includes a yoke that forms a universal joint, and a shaft.
Of these, the yoke is provided with a base portion having a coupling hole formed in the axial direction at the center portion in the radial direction, and extending in one axial direction from two positions opposite to the radial direction of the base portion. A pair of arms,
The shaft is made of a metal material in a tubular shape, and one end portion in the axial direction is press-fitted into the inside of the coupling hole from the other axial side of the coupling hole. A coupling portion between the shaft and the yoke of the universal joint In
Of the base, an overhanging cylinder part having a radial thickness smaller than that of the peripheral part of the remaining part of the coupling hole is provided in a peripheral part of the other axial end part of the coupling hole,
Of the exposed portion of the shaft that is on the other side in the axial direction than the coupling hole and exposed to the outside of the coupling hole, a portion adjacent to the other axial direction end on one axial end Compared to the portion adjacent to the other side in the axial direction, the outer diameter is smaller, and the thickness in the radial direction is smaller than the portion adjacent to the other side in the axial direction. This is because the outer diameter dimension of the press-fitting part, which is a part adjacent to one side in the axial direction of the part and is the part press-fitted inside the coupling hole, is smaller than the outer diameter dimension of the thin-walled part. The radial thickness of the press-fit part is smaller than the radial thickness of this thin part ,
The coupling hole formed in the radial center of the base is a serration hole, and a portion of the serration hole corresponding to the projecting cylindrical portion with respect to the axial direction is flexed to the inner diameter side in a free state.
The joint between the shaft and the universal joint yoke.
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