JP4773233B2 - Universal joint - Google Patents

Universal joint Download PDF

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Publication number
JP4773233B2
JP4773233B2 JP2006066370A JP2006066370A JP4773233B2 JP 4773233 B2 JP4773233 B2 JP 4773233B2 JP 2006066370 A JP2006066370 A JP 2006066370A JP 2006066370 A JP2006066370 A JP 2006066370A JP 4773233 B2 JP4773233 B2 JP 4773233B2
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trunnion
contact
curved surface
convex
outer ring
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JP2007239953A (en
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禎弘 川原
和浩 花谷
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JTEKT Corp
Koyo Machine Industries Co Ltd
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JTEKT Corp
Koyo Machine Industries Co 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
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
    • F16C17/08—Sliding-contact bearings for exclusively rotary movement for axial load only for supporting the end face of a shaft or other member, e.g. footstep bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/26—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected
    • F16D3/38—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected with a single intermediate member with trunnions or bearings arranged on two axes perpendicular to one another
    • F16D3/382—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected with a single intermediate member with trunnions or bearings arranged on two axes perpendicular to one another constructional details of other than the intermediate member
    • F16D3/385—Bearing cup; Bearing construction; Bearing seal; Mounting of bearing on the intermediate member
    • 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
    • F16C21/00—Combinations of sliding-contact bearings with ball or roller bearings, for exclusively rotary movement
    • F16C21/005—Combinations of sliding-contact bearings with ball or roller bearings, for exclusively rotary movement the external zone of a bearing with rolling members, e.g. needles, being cup-shaped, with or without a separate thrust-bearing disc or ring, e.g. for universal joints
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/26—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected
    • F16D3/38—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected with a single intermediate member with trunnions or bearings arranged on two axes perpendicular to one another
    • F16D3/40—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected with a single intermediate member with trunnions or bearings arranged on two axes perpendicular to one another with intermediate member provided with two pairs of outwardly-directed trunnions on intersecting axes
    • F16D3/41—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected with a single intermediate member with trunnions or bearings arranged on two axes perpendicular to one another with intermediate member provided with two pairs of outwardly-directed trunnions on intersecting axes with ball or roller bearings

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sliding-Contact Bearings (AREA)

Description

この発明は、例えば自動車に用いられる自在継手に関する。   The present invention relates to a universal joint used for an automobile, for example.

自在継手は、例えば十字軸の各トラニオンを、ヨークの対応する嵌合孔に嵌合された有底円筒状の外輪カップによって針状ころを介して支持している。これら針状ころおよび外輪カップが軸受をなしている。
従来、外輪カップの内底部に球面状の凸部を形成し、トラニオンの端面に円錐状の凹部を形成し、凸部と凹部とを摺接させた自在継手がある（例えば、特許文献１の図１参照。）。 In the universal joint, for example, each trunnion of the cross shaft is supported via needle rollers by a bottomed cylindrical outer ring cup fitted in a corresponding fitting hole of the yoke. These needle rollers and the outer ring cup form a bearing.
Conventionally, there is a universal joint in which a spherical convex portion is formed on the inner bottom portion of the outer ring cup, a conical concave portion is formed on the end surface of the trunnion, and the convex portion and the concave portion are slidably contacted (for example, Patent Document 1). (See FIG. 1).

また、従来、外輪カップの内底部に凹部が形成され、トラニオンの端面に円錐台形状の凸部が形成された自在継手がある（例えば、特許文献１の図２参照。）。
特開２０００−１７０７８６号公報 Conventionally, there is a universal joint in which a concave portion is formed on the inner bottom portion of the outer ring cup and a truncated cone-shaped convex portion is formed on the end surface of the trunnion (see, for example, FIG. 2 of Patent Document 1).
JP 2000-170786 A

通例、回転抵抗トルクの上昇を抑えるために、トラニオンと外輪カップの内底面との間に隙間が設けられ、トラニオンの外周面と外輪カップとの間の径方向隙間が針状ころの直径よりも大きくされている。このため、トラニオンが軸方向や径方向にがたつき、騒音を発生する虞がある。
逆に、各部品の寸法のばらつきにより、トラニオンと外輪カップとの間に軸方向や径方向に締め代を生ずる場合には、トラニオンと外輪カップとが相対回転するときの回転抵抗トルクが大きくなるという問題がある。 Usually, a gap is provided between the trunnion and the inner bottom surface of the outer ring cup in order to suppress an increase in rotational resistance torque, and the radial gap between the outer peripheral surface of the trunnion and the outer ring cup is larger than the diameter of the needle roller. It has been enlarged. For this reason, there is a possibility that the trunnion rattles in the axial direction or the radial direction and generates noise.
On the other hand, when there is an allowance in the axial direction or radial direction between the trunnion and the outer ring cup due to variations in the dimensions of each part, the rotational resistance torque when the trunnion and the outer ring cup rotate relative to each other increases. There is a problem.

また、特許文献１では、トラニオンの端面と外輪カップの内底面とを接触させるので、その間の環状の接触部に摩擦が生じる結果、上述の回転抵抗トルクがより一層大きくなる。
また、車両用操舵装置においては、スムーズな操舵感を得ることが要請されている。このためにも、回転抵抗トルクを小さくすることが求められている。 Moreover, in patent document 1, since the end surface of a trunnion and the inner bottom face of an outer ring cup are made to contact, as a result of friction arising in the annular contact part between them, the above-mentioned rotation resistance torque becomes still larger.
Further, in a vehicle steering device, it is required to obtain a smooth steering feeling. For this reason, it is required to reduce the rotational resistance torque.

そこで、この発明の目的は、騒音を低減できて且つ回転抵抗トルクが小さくて、さらに車両用操舵装置に適用されたときにスムーズな操舵感を得ることができる自在継手を提供することである。   SUMMARY OF THE INVENTION Accordingly, an object of the present invention is to provide a universal joint that can reduce noise, have a small rotational resistance torque, and can obtain a smooth steering feeling when applied to a vehicle steering system.

本願発明者は、各部品の寸法のばらつきの悪影響を抑制しつつ、がたつきの発生を抑制し、さらに回転抵抗トルクを低減するために、トラニオンの端面と外輪カップの内底面との上述の環状の接触部を備える構造において、環状の接触部での摩擦トルクと接触角との関係に着目した。すなわち、摩擦トルクは、接触部に生じる摩擦力と、環状の接触部の環の半径との積として求められる。上述の摩擦力は、環状の接触部において、これの周方向の所定位置に作用する押圧力の方向とトラニオンの中心軸線とのなす角度である接触角に反比例する傾向にある。その一方で、上述の環の半径は接触角に比例する傾向にあり、結局は、摩擦トルクは上述の接触角に比例する傾向にある。   The inventor of the present application suppresses the adverse effects of variations in the dimensions of each part, suppresses the occurrence of rattling, and further reduces the rotational resistance torque, so that the above-described annular shape between the end surface of the trunnion and the inner bottom surface of the outer ring cup In the structure including the contact portion, attention was paid to the relationship between the friction torque and the contact angle at the annular contact portion. That is, the friction torque is obtained as a product of the friction force generated in the contact portion and the radius of the ring of the annular contact portion. The aforementioned frictional force tends to be inversely proportional to the contact angle, which is the angle formed by the direction of the pressing force acting on a predetermined position in the circumferential direction of the annular contact portion and the central axis of the trunnion. On the other hand, the radius of the ring tends to be proportional to the contact angle, and eventually the friction torque tends to be proportional to the contact angle.

そこで、接触角を所定範囲内に限定することにより、環状の接触部の半径を小さく抑制し、ひいては、回転抵抗トルクを、スムーズな操舵感を得ることができるような範囲内に小さく抑制している。
本発明の自在継手は、十字軸に設けられたトラニオンと、このトラニオンの外周面の周囲を取り囲んで環状に配置された複数の針状ころと、ヨークの嵌合孔に保持され、上記針状ころを介して上記トラニオンを回転自在に支持する有底円筒状の外輪カップと、上記トラニオンの端面および外輪カップの内底面の何れか一方に設けられた凸部、および他方に設けられ上記凸部を受ける凹部とを備え、上記凸部および凹部は、トラニオンの中心軸線を中心とする環状の接触部で互いに押圧状態で接触しており、上記接触部で凸部および凹部間に働く押圧力の方向と、トラニオンの中心軸線とのなす角度である接触角は、０度を越え４０度未満の範囲にあり、上記凸部は、凸湾曲面を含み、上記凹部は、上記凸湾曲面の曲率半径よりも大きい曲率半径を有する凹湾曲面と、この凹湾曲面の底部に設けられ凸湾曲面の先端から逃げるように窪んだ逃げ部とを含み、上記接触部は、逃げ部の周縁を含むことを特徴とする。 Therefore, by limiting the contact angle within a predetermined range, the radius of the annular contact portion is suppressed to be small, and thus the rotational resistance torque is suppressed to be small within a range where a smooth steering feeling can be obtained. Yes.
The universal joint of the present invention includes a trunnion provided on the cross shaft, a plurality of needle rollers arranged in an annular shape so as to surround the periphery of the trunnion, and held in a fitting hole of the yoke. A bottomed cylindrical outer ring cup that rotatably supports the trunnion via rollers, a convex portion provided on one of the end surface of the trunnion and an inner bottom surface of the outer ring cup, and the convex portion provided on the other side The convex portion and the concave portion are in contact with each other in a pressed state at an annular contact portion centered on the central axis of the trunnion, and the pressing force acting between the convex portion and the concave portion at the contact portion. and direction, the contact angle is an angle between the center axis line of the trunnion, Ri range near less than 40 degrees beyond the 0 °, the convex portion includes a convex curved surface, the recess is, of the convex curved surface Curvature half greater than radius of curvature A concave curved surface having, and a recessed escape portion to escape from the tip of the convex curved surface provided in the bottom of the concave curved surface, the contact portion, characterized in that it comprises a peripheral edge of the relief portion.

本発明によれば、外輪カップが、環状の接触部を介して、トラニオンの軸方向および径方向に弾性的にトラニオンを付勢できるので、トラニオンの軸方向および径方向のがたをなくすことができ、ひいては、騒音を低減することができる。しかも、環状の接触部は、ベタ当たりしないことから、接触部に生じる摩擦トルクを小さくでき、ひいては回転抵抗トルクを小さく抑制することができる。また、がたつきの発生を防止できるので、トラニオンの外周面と外輪カップとの間の径方向隙間を針状ころの直径よりも大きくすることも可能であり、この点でも回転抵抗トルクを小さく抑制することができる。特に、上述の接触角が０度を越え４０度未満の範囲内にあることにより、接触部の環の半径を小さくできるので、回転抵抗トルクを、本自在継手が車両用操舵装置に適用された場合にスムーズな操舵感を得るための所定値以下に小さく抑制でき、しかも、がたつきの発生を防止することができる。   According to the present invention, the outer ring cup can elastically bias the trunnion in the axial direction and the radial direction of the trunnion via the annular contact portion, so that the axial direction and the radial direction of the trunnion can be eliminated. As a result, noise can be reduced. In addition, since the annular contact portion does not make a solid contact, the friction torque generated in the contact portion can be reduced, and the rotation resistance torque can be reduced. Moreover, since the occurrence of rattling can be prevented, the radial clearance between the outer peripheral surface of the trunnion and the outer ring cup can be made larger than the diameter of the needle roller, and in this respect also, the rotational resistance torque is suppressed to be small. can do. In particular, since the above contact angle is in the range of more than 0 degrees and less than 40 degrees, the radius of the ring of the contact portion can be reduced. Therefore, the rotational joint torque is applied to the vehicle steering apparatus. In this case, it can be suppressed to a value equal to or less than a predetermined value for obtaining a smooth steering feeling, and rattling can be prevented.

なお、接触角が４０度を越えて大きくなると、接触部の環の半径が大きくなる結果、接触部間の摩擦トルク、ひいては回転抵抗トルクが大きくなる。また、接触角が０度の場合には、接触部が１点で点接触するので、がたつきが発生する。
また、本発明において、上記凸部は、凸湾曲面を含み、上記凹部は、上記凸湾曲面の曲率半径よりも大きい曲率半径を有する凹湾曲面と、この凹湾曲面の底部に設けられ凸湾曲面の先端から逃げるように窪んだ逃げ部とを含み、上記接触部は、逃げ部の周縁を含んでいる。これにより、環状の接触部を簡素な構造で実現できる。 When the contact angle increases beyond 40 degrees, the radius of the ring of the contact portion increases, and as a result, the friction torque between the contact portions, and thus the rotation resistance torque increases. Further, when the contact angle is 0 degree, the contact portion makes point contact at one point, and thus rattling occurs.
In the present invention, the convex portion includes a convex curved surface, and the concave portion has a concave curved surface having a radius of curvature larger than the radius of curvature of the convex curved surface, and a convex portion provided at the bottom of the concave curved surface. and a recessed escape portion to escape from the tip of the curved surface, the contact portion is Nde including a peripheral edge of the relief portion. This ensures that the contact portion of the annular be realized with a simple structure.

また、本発明において、上記凸湾曲面および凹湾曲面は、それぞれ球面を含む場合がある。この場合、凸湾曲面および凹湾曲面を安価に形成できる。   In the present invention, the convex curved surface and the concave curved surface may each include a spherical surface. In this case, the convex curved surface and the concave curved surface can be formed at low cost.

以下では、この発明の実施の形態を、添付図面を参照して詳細に説明する。
本実施形態では、自在継手が車両用操舵装置に適用される場合に則して説明するが、本発明はこれに限らず、例えば、自在継手を、車両用操舵装置以外の各種の機械装置に適用することもできる。
図１は、本発明の一実施形態の自在継手を含む車両用操舵装置の模式図である。図１を参照して、車両用操舵装置１は、一端３ａがステアリングホイール等の操舵部材２に連結されたステアリングシャフト３と、一端５ａがステアリングシャフト３の他端３ｂに本実施の形態の自在継手４を介して連結された中間軸５と、中間軸５の他端５ｂに本実施の形態の自在継手６を介して連結されたピニオンシャフト７と、ピニオンシャフト７の端部近傍に設けられたピニオン７ａに噛み合うラック歯８ａを有して車幅方向（左右方向）に延びる操舵軸としてのラックバー８とを有している。 Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings.
In the present embodiment, the universal joint is described as applied to a vehicle steering apparatus. However, the present invention is not limited to this. For example, the universal joint may be applied to various mechanical devices other than the vehicle steering apparatus. It can also be applied.
FIG. 1 is a schematic view of a vehicle steering apparatus including a universal joint according to an embodiment of the present invention. Referring to FIG. 1, a vehicular steering apparatus 1 includes a steering shaft 3 whose one end 3 a is connected to a steering member 2 such as a steering wheel, and one end 5 a that is connected to the other end 3 b of the steering shaft 3. An intermediate shaft 5 connected through a joint 4, a pinion shaft 7 connected to the other end 5 b of the intermediate shaft 5 through a universal joint 6 of the present embodiment, and an end portion of the pinion shaft 7. The rack bar 8 has a rack tooth 8a that meshes with the pinion 7a and extends in the vehicle width direction (left-right direction).

ピニオンシャフト７およびラックバー８により操舵機構としてのラックアンドピニオン機構Ａが構成されている。ラックバー８は、車体に固定されるハウジング９内に複数の軸受（図示せず）を介して直線往復動自在に支持されている。ラックバー８の両端部は、ハウジング９の両側へ突出し、各端部には、それぞれタイロッド１０が結合されている。各タイロッド１０は対応するナックルアーム（図示せず）を介して対応する操向輪１１に連結されている。   The pinion shaft 7 and the rack bar 8 constitute a rack and pinion mechanism A as a steering mechanism. The rack bar 8 is supported in a housing 9 fixed to the vehicle body so as to be capable of linear reciprocation through a plurality of bearings (not shown). Both end portions of the rack bar 8 protrude to both sides of the housing 9, and tie rods 10 are coupled to the respective end portions. Each tie rod 10 is connected to a corresponding steering wheel 11 via a corresponding knuckle arm (not shown).

操舵部材２が操作されてステアリングシャフト３が回転されると、この回転がピニオン７ａおよびラック歯８ａによって、自動車の左右方向に沿ってのラックバー８の直線運動に変換される。これにより、操向輪１１が操舵される。
図２は、図１に示す車両用操舵装置の要部の側面図である。図２を参照して、自在継手４は、ステアリングシャフト３の他端３ｂに設けられたヨーク２０と、中間軸５の一端５ａに設けられたヨーク２１と、両ヨーク間を連結する十字軸２２とを備える。 When the steering member 2 is operated and the steering shaft 3 is rotated, this rotation is converted into a linear motion of the rack bar 8 along the left-right direction of the automobile by the pinion 7a and the rack teeth 8a. Thereby, the steered wheel 11 is steered.
FIG. 2 is a side view of a main part of the vehicle steering apparatus shown in FIG. Referring to FIG. 2, the universal joint 4 includes a yoke 20 provided at the other end 3 b of the steering shaft 3, a yoke 21 provided at one end 5 a of the intermediate shaft 5, and a cross shaft 22 that connects the two yokes. With.

同様に、自在継手６は、ピニオンシャフト７の端部に設けられたヨーク２０と、中間軸５の他端５ｂに設けられたヨーク２１と、両ヨーク２０，２１間を連結する十字軸２２とを備える。
各ヨーク２０，２１はＵ字状をなし、それぞれ一対のタブ２３を有している。一対のタブ２３は互いに平行である。なお、図２には、自在継手４のヨーク２０のタブ２３はひとつのみ図示され、自在継手６のヨーク２１のタブ２３もひとつのみが図示されている。 Similarly, the universal joint 6 includes a yoke 20 provided at the end of the pinion shaft 7, a yoke 21 provided at the other end 5 b of the intermediate shaft 5, and a cross shaft 22 that connects the yokes 20, 21. Is provided.
Each yoke 20, 21 is U-shaped and has a pair of tabs 23. The pair of tabs 23 are parallel to each other. In FIG. 2, only one tab 23 of the yoke 20 of the universal joint 4 is illustrated, and only one tab 23 of the yoke 21 of the universal joint 6 is illustrated.

自在継手４，６は、全く同様の構成であるので、自在継手４に則して説明する。
図３は、自在継手４の一部断面図である。図３を参照して、十字軸２２は、十字形形状の中央部に配置される胴部２２ａと、この胴部２２ａから十字形形状をなして突出する４つの軸部としてのトラニオン２４とを有している。各トラニオン２４には、それぞれ軸受２６が取り付けられている。 Since the universal joints 4 and 6 have exactly the same configuration, the universal joint 4 will be described.
FIG. 3 is a partial cross-sectional view of the universal joint 4. Referring to FIG. 3, the cross shaft 22 includes a trunk portion 22a disposed at the center of the cross shape, and a trunnion 24 as four shaft portions protruding in a cross shape from the trunk portion 22a. Have. A bearing 26 is attached to each trunnion 24.

各タブ２３には、十字軸２２の対応するトラニオン２４のための嵌合孔２５が形成されている。（図３では、簡略化のため、１つのタブ２３のみを示す。）この嵌合孔２５に嵌合され保持された軸受２６を介して十字軸２２の対応するトラニオン２４が回転自在に支持されている。
軸受２６は、トラニオン２４の周囲に環状に並べて配置された複数の針状ころ２７と、これらの針状ころ２７を保持するとともに嵌合孔２５に嵌合され固定された有底円筒形状の外輪カップ２８とを含んでいる。外輪カップ２８は、例えば金属の薄板をプレス加工されてなる一端密閉型のシェル形外輪である。 Each tab 23 is formed with a fitting hole 25 for the corresponding trunnion 24 of the cross shaft 22. (In FIG. 3, only one tab 23 is shown for simplification.) The corresponding trunnion 24 of the cross shaft 22 is rotatably supported via a bearing 26 fitted and held in the fitting hole 25. ing.
The bearing 26 includes a plurality of needle rollers 27 arranged in a ring around the trunnion 24, and a bottomed cylindrical outer ring that holds the needle rollers 27 and is fitted and fixed in the fitting holes 25. Cup 28. The outer ring cup 28 is a shell-shaped outer ring having a sealed end, for example, formed by pressing a metal thin plate.

図４は、図３に示す自在継手の要部の断面図である。図３と図４を参照して、トラニオン２４の端面２４ａには、ボール保持孔２９が形成されている。このボール保持孔２９は、トラニオン２４と同心の円孔からなり、ボール３０を圧入状態で保持している。
ボール３０は、トラニオン２４の径方向についての締め代を有してボール保持孔２９に保持され、トラニオン２４に対してトラニオン２４の軸方向Ａ１および径方向Ｒ１への移動が規制されている。また、トラニオン２４の軸方向Ａ１について、ボール３０の一部は、ボール保持孔２９から外輪カップ２８の内底面２８ａのある側へ突出し、トラニオン２４の端面２４ａに設けられた凸部として機能する。ボール３０の突出した上記一部の表面３０ｂは、曲率半径Ｒａの凸湾曲面としての球面に形成されている。また、ボール保持孔２９の奥部には、当該ボール保持孔２９としての円孔を加工するときに設けられたセンタ孔が連なっている。 FIG. 4 is a cross-sectional view of a main part of the universal joint shown in FIG. With reference to FIGS. 3 and 4, a ball holding hole 29 is formed in the end surface 24 a of the trunnion 24. The ball holding hole 29 is a circular hole concentric with the trunnion 24, and holds the ball 30 in a press-fitted state.
The ball 30 is held in the ball holding hole 29 with a tightening margin in the radial direction of the trunnion 24, and the movement of the trunnion 24 in the axial direction A1 and the radial direction R1 is restricted with respect to the trunnion 24. Further, in the axial direction A1 of the trunnion 24, a part of the ball 30 protrudes from the ball holding hole 29 toward the side where the inner bottom surface 28a of the outer ring cup 28 is located, and functions as a convex portion provided on the end surface 24a of the trunnion 24. The part of the surface 30b from which the ball 30 protrudes is formed as a spherical surface as a convex curved surface having a radius of curvature Ra. Further, a center hole provided when processing a circular hole as the ball holding hole 29 is connected to the inner part of the ball holding hole 29.

また、ボール保持孔２９に保持されたボール３０を弾性的に受けるためのボール受け部３１が、外輪カップ２８の内底面２８ａに形成されている。外輪カップ２８の中心軸線Ｃ１（トラニオン２４の中心軸線２４ｃと一致する。）の延びる方向について、外輪カップ２８は、ボール３０を弾力的に付勢するように軸方向の締め代を付与された状態で、嵌合孔２５に圧入されて保持されている。これにより、外輪カップ２８は、ボール３０を介して、トラニオン２４を軸方向および径方向に弾力的に押圧している。   A ball receiving portion 31 for elastically receiving the ball 30 held in the ball holding hole 29 is formed on the inner bottom surface 28 a of the outer ring cup 28. With respect to the direction in which the center axis C1 of the outer ring cup 28 extends (which coincides with the center axis 24c of the trunnion 24), the outer ring cup 28 is given an axial tightening allowance to elastically bias the ball 30. Thus, the fitting hole 25 is press-fitted and held. Thus, the outer ring cup 28 elastically presses the trunnion 24 in the axial direction and the radial direction via the ball 30.

本実施形態では、ボール保持孔２９に保持されたボール３０が、ボール受け部３１により弾性的に受けとめられた状態において、トラニオン２４と外輪カップ２８とは同心に配置されている。このときのトラニオン２４の外周面２４ｂと外輪カップ２８の内周面との間の径方向隙間は、針状ころ２７の直径よりも大きくされている。
ボール受け部３１は、外輪カップ２８の内底面２８ａに設けられた凹部であって、上記凸部としてのボール３０を受ける凹部として機能する。ボール受け部３１は、外輪カップ２８の中心軸線Ｃ１を中心とする球面状の凹湾曲面３２と、この凹湾曲面３２の底部に設けられた逃げ部３３とを含んでいる。 In the present embodiment, the trunnion 24 and the outer ring cup 28 are concentrically arranged in a state where the ball 30 held in the ball holding hole 29 is elastically received by the ball receiving portion 31. At this time, the radial gap between the outer peripheral surface 24 b of the trunnion 24 and the inner peripheral surface of the outer ring cup 28 is made larger than the diameter of the needle rollers 27.
The ball receiving portion 31 is a concave portion provided on the inner bottom surface 28a of the outer ring cup 28 and functions as a concave portion that receives the ball 30 as the convex portion. The ball receiving portion 31 includes a spherical concave curved surface 32 centered on the central axis C <b> 1 of the outer ring cup 28, and a relief portion 33 provided at the bottom of the concave curved surface 32.

凹湾曲面３２は、ボール３０の曲率半径Ｒａよりも大きい曲率半径Ｒｂを有する凹湾曲面、例えば球面からなる。この球面の中心は、外輪カップ２８の中心軸線Ｃ１上に配置されている。
逃げ部３３は、窪み状の丸孔であり、外輪カップ２８の軸方向からみたときに外輪カップ２８の中心軸線Ｃ１を中心とした円形をなしている。逃げ部３３は、ボール３０の突出した先端３０ｃから逃げるように窪んでいて、ボール３０の表面３０ｂとの接触を回避されている。 The concave curved surface 32 is a concave curved surface having a radius of curvature Rb larger than the radius of curvature Ra of the ball 30, for example, a spherical surface. The center of the spherical surface is disposed on the central axis C1 of the outer ring cup 28.
The escape portion 33 is a concave round hole and has a circular shape centered on the central axis C <b> 1 of the outer ring cup 28 when viewed from the axial direction of the outer ring cup 28. The escape portion 33 is recessed so as to escape from the protruding tip 30 c of the ball 30, thereby avoiding contact with the surface 30 b of the ball 30.

凸部としてのボール３０および凹部としてのボール受け部３１は、トラニオン２４の中心軸線２４ｃを中心とする環状の接触部３０ａ，３１ａで互いに押圧状態で接触している。ボール３０の接触部３０ａは、トラニオン２４の中心軸線２４ｃを中心とした環状をなしている。ボール受け部３１の接触部３１ａは、外輪カップ２８の中心軸線Ｃ１を中心とした環状をなしている。接触部３１ａは、凹湾曲面３２の内周縁部であり且つ逃げ部３３の周縁を有し、ボール３０の接触部３０ａに線接触している。   The ball 30 as a convex portion and the ball receiving portion 31 as a concave portion are in contact with each other in a pressed state at annular contact portions 30 a and 31 a centering on the central axis 24 c of the trunnion 24. The contact portion 30 a of the ball 30 has an annular shape centered on the central axis 24 c of the trunnion 24. The contact portion 31 a of the ball receiving portion 31 has an annular shape centering on the central axis C <b> 1 of the outer ring cup 28. The contact portion 31 a is an inner peripheral edge portion of the concave curved surface 32 and has a peripheral edge of the escape portion 33, and is in line contact with the contact portion 30 a of the ball 30.

上記接触部３０ａ，３１ａで凸部としてのボール３０および凹部としてのボール受け部３１間に働く押圧力の方向Ｆ１と、トラニオン２４の中心軸線２４ｃとのなす角度である接触角Ｄは、０度を越え４０度未満の範囲にある。
本実施形態の自在継手４において、例えばトラニオン２４から外輪カップ２８へ伝達トルクが伝わる場合を考える。この場合、伝達トルクが小さいときには、トラニオン２４からボール３０およびボール受け部３１を介して外輪カップ２８にトルクが伝達される一方、伝達トルクが大きいときは、トラニオン２４から針状ころ２７を介しても外輪カップ２８にトルクが伝達される。 A contact angle D, which is an angle formed between the direction F1 of the pressing force acting between the ball 30 as the convex portion and the ball receiving portion 31 as the concave portion in the contact portions 30a and 31a, and the central axis 24c of the trunnion 24 is 0 degree. Is in the range of less than 40 degrees.
In the universal joint 4 of the present embodiment, for example, a case where transmission torque is transmitted from the trunnion 24 to the outer ring cup 28 is considered. In this case, when the transmission torque is small, the torque is transmitted from the trunnion 24 to the outer ring cup 28 via the ball 30 and the ball receiving portion 31, while when the transmission torque is large, the trunnion 24 is passed through the needle rollers 27. Also, torque is transmitted to the outer ring cup 28.

本実施形態の自在継手４は、十字軸２２に設けられたトラニオン２４と、このトラニオン２４の外周面の周囲を取り囲んで環状に配置された複数の針状ころ２７と、ヨーク２０，２１の嵌合孔２５に保持され、上記針状ころ２７を介して上記トラニオン２４を回転自在に支持する有底円筒状の外輪カップ２８と、上記トラニオン２４の端面２４ａおよび外輪カップ２８の内底面２８ａの何れか一方としてのトラニオン２４の端面２４ａに設けられた凸部としてのボール３０と、および他方としての外輪カップ２８の内底面２８ａに設けられ上記凸部を受ける凹部としてのボール受け部３１とを備えている。上記凸部および凹部は、トラニオン２４の中心軸線２４ｃを中心とする環状の接触部３０ａ，３１ａで互いに押圧状態で接触している。上記接触部３０ａ，３１ａで凸部および凹部間に働く押圧力の方向Ｆ１と、トラニオン２４の中心軸線２４ｃとのなす角度である接触角Ｄは、０度を越え４０度未満の範囲にあることを特徴としている。   The universal joint 4 of the present embodiment includes a trunnion 24 provided on the cross shaft 22, a plurality of needle rollers 27 arranged in an annular shape surrounding the periphery of the trunnion 24, and fittings of yokes 20 and 21. Any one of a bottomed cylindrical outer ring cup 28 held in the joint hole 25 and rotatably supporting the trunnion 24 via the needle rollers 27, an end face 24a of the trunnion 24, and an inner bottom face 28a of the outer ring cup 28. A ball 30 as a convex portion provided on the end surface 24a of the trunnion 24 as one of them, and a ball receiving portion 31 as a concave portion provided on the inner bottom surface 28a of the outer ring cup 28 as the other to receive the convex portion. ing. The convex portion and the concave portion are in contact with each other in a pressed state at annular contact portions 30 a and 31 a centering on the central axis 24 c of the trunnion 24. The contact angle D, which is the angle formed between the direction F1 of the pressing force acting between the convex portions and the concave portions at the contact portions 30a and 31a and the central axis 24c of the trunnion 24, is in the range of more than 0 degree and less than 40 degrees. It is characterized by.

これにより、外輪カップ２８が、環状の接触部３０ａ，３１ａを介して、トラニオン２４の軸方向および径方向に弾性的にトラニオン２４を付勢できるので、トラニオン２４の軸方向および径方向のがたをなくすことができ、ひいては、騒音を低減することができる。しかも、環状の接触部３０ａ，３１ａは、ベタ当たりしないことから、接触部３０ａ，３１ａに生じる摩擦トルクを小さくでき、ひいては回転抵抗トルクを小さく抑制することができる。また、がたつきの発生を防止できるため、トラニオン２４の外周面２４ｂと外輪カップ２８の内周面との間の径方向隙間を針状ころ２７の直径よりも大きくすることも可能であり、この点でも回転抵抗トルクを小さく抑制することができる。   As a result, the outer ring cup 28 can elastically bias the trunnion 24 in the axial direction and radial direction of the trunnion 24 via the annular contact portions 30a and 31a. As a result, noise can be reduced. In addition, since the annular contact portions 30a and 31a do not make a solid contact, the friction torque generated in the contact portions 30a and 31a can be reduced, and consequently, the rotational resistance torque can be suppressed to be small. Further, since the occurrence of rattling can be prevented, the radial clearance between the outer peripheral surface 24b of the trunnion 24 and the inner peripheral surface of the outer ring cup 28 can be made larger than the diameter of the needle rollers 27. Even at this point, the rotational resistance torque can be suppressed small.

なお、本実施形態では、トラニオン２４の外周面２４ｂと外輪カップ２８の内周面との間の径方向隙間が針状ころ２７の直径よりも大きくされていたが、そのように構成されていない場合も考えられる。
また、接触部３０ａ，３１ａが、互いに環状に線接触する場合には、回転抵抗トルクの上昇を抑制するのに好ましい。 In the present embodiment, the radial gap between the outer peripheral surface 24b of the trunnion 24 and the inner peripheral surface of the outer ring cup 28 is made larger than the diameter of the needle roller 27, but it is not configured as such. Cases are also conceivable.
Further, when the contact portions 30a and 31a are in linear contact with each other, it is preferable to suppress an increase in rotational resistance torque.

特に、上述の接触角Ｄが０度を越えて４０度未満の範囲内にあることにより、接触部３０ａ，３１ａの環の直径（２・Ｒ）を小さくできるので、回転抵抗トルクを、本自在継手４が車両用操舵装置１に適用された場合にスムーズな操舵感を得るための所定値以下に小さく抑制でき、しかも、がたつきの発生を防止することができる。
また、上述の接触角Ｄが１０度〜３０度の範囲内にある場合には、接触部３０ａ，３１ａの環の直径（２・Ｒ）をより小さくできるので、回転抵抗トルクを、本自在継手４が車両用操舵装置１に適用された場合にスムーズな操舵感を得るための所定値以下に確実に小さく抑制でき、しかも、環状の接触部３０ａ，３１ａを、ひいては逃げ部３３を過度に小さくせずに済むので、実用的に実現することができる。 In particular, when the contact angle D is within the range of more than 0 degrees and less than 40 degrees, the ring diameter (2.R) of the contact portions 30a and 31a can be reduced, so that the rotational resistance torque can be controlled freely. When the joint 4 is applied to the vehicle steering apparatus 1, it can be suppressed to a predetermined value or less for obtaining a smooth steering feeling, and the occurrence of rattling can be prevented.
Further, when the contact angle D is in the range of 10 degrees to 30 degrees, the diameter (2R) of the rings of the contact portions 30a and 31a can be further reduced. 4 is applied to the vehicle steering apparatus 1, it can be surely suppressed below a predetermined value for obtaining a smooth steering feeling, and the annular contact portions 30 a, 31 a and the escape portion 33 are excessively small. This can be realized practically.

また、より好ましくは接触角Ｄが１０〜２０度の範囲内にあることにより、さらにより好ましくは１０〜１２度の範囲内にあることにより、回転抵抗トルクを確実に小さくすることができる。
なお、接触角Ｄが４０度以上に大きくなると、接触部３０ａ，３１ａの環の半径が大きくなる結果、接触部３０ａ，３１ａ間の摩擦トルク、ひいては回転抵抗トルクが大きくなる。その結果、自在継手４が車両用操舵装置１に適用されたときに、操舵感の劣化、すなわち、スムーズな操舵感を実現できない虞がある。また、接触角Ｄが０度の場合には、接触部３０ａ，３１ａが１箇所で点接触するので、がたつきが発生する。また、接触角Ｄが１０度未満になると、環状の接触部３０ａ，３１ａの半径が小さくなり過ぎるので、自在継手４を安価に製造できない。 More preferably, when the contact angle D is in the range of 10 to 20 degrees, and even more preferably in the range of 10 to 12 degrees, the rotational resistance torque can be reliably reduced.
When the contact angle D increases to 40 degrees or more, the radius of the ring of the contact portions 30a and 31a increases, and as a result, the friction torque between the contact portions 30a and 31a, and thus the rotational resistance torque increases. As a result, when the universal joint 4 is applied to the vehicle steering apparatus 1, there is a possibility that the deterioration of the steering feeling, that is, the smooth steering feeling cannot be realized. Further, when the contact angle D is 0 degree, the contact portions 30a and 31a make point contact at one place, and thus rattling occurs. If the contact angle D is less than 10 degrees, the radius of the annular contact portions 30a and 31a becomes too small, and the universal joint 4 cannot be manufactured at low cost.

また、本実施形態では、凸部としてのボール３０は、凸湾曲面を含む。また、上記凹部としてのボール受け部３１は、凸湾曲面の曲率半径Ｒａよりも大きい曲率半径Ｒｂを有する凹湾曲面３２と、この凹湾曲面３２の底部に設けられた逃げ部３３とを含む。接触部３１ａは、逃げ部３２の周縁を含むようにしている。この場合、環状の接触部３１ａを簡素な構造で実現できる。   In the present embodiment, the ball 30 as the convex portion includes a convex curved surface. Further, the ball receiving portion 31 as the concave portion includes a concave curved surface 32 having a radius of curvature Rb larger than the radius of curvature Ra of the convex curved surface, and a relief portion 33 provided at the bottom of the concave curved surface 32. . The contact portion 31 a includes the periphery of the escape portion 32. In this case, the annular contact portion 31a can be realized with a simple structure.

また、本実施形態では、凸湾曲面としてのボール３０および凹湾曲面３２は、それぞれ球面を含むようにしている。この場合、上述の凸湾曲面および凹湾曲面を安価に形成できる。
図５は、接触角Ｄと自在継手４の回転抵抗トルクＴとの関係を示すグラフであり、横軸に接触角Ｄ［度］を、縦軸に回転抵抗トルクＴ［Ｎ・ｍ］を示す。図５のグラフは、後述する式１，式２，式３を用いて、接触角Ｄ［度］の任意の値に対する回転抵抗トルクＴの値を求め、接触角Ｄ［度］の値を変化させたときの回転抵抗トルクＴの値の変化をプロットしたものである。また、図５には、回転抵抗トルクＴの許容最大値Ｔｍａｘを仮に０．１１７［Ｎ・ｍ］とし破線で示した。回転抵抗トルクＴが、許容最大値Ｔｍａｘを越えて大きくなると、スムーズな操舵感を得ることができないおそれがある。 In the present embodiment, the ball 30 and the concave curved surface 32 as convex curved surfaces each include a spherical surface. In this case, the above-mentioned convex curved surface and concave curved surface can be formed at low cost.
FIG. 5 is a graph showing the relationship between the contact angle D and the rotational resistance torque T of the universal joint 4, wherein the horizontal axis represents the contact angle D [degree], and the vertical axis represents the rotational resistance torque T [N · m]. . The graph of FIG. 5 obtains the value of the rotational resistance torque T with respect to an arbitrary value of the contact angle D [degree] using the formula 1, formula 2, and formula 3 described later, and changes the value of the contact angle D [degree]. The change of the value of the rotational resistance torque T when it is made to plot is plotted. Further, in FIG. 5, the allowable maximum value Tmax of the rotational resistance torque T is assumed to be 0.117 [N · m] and indicated by a broken line. If the rotational resistance torque T exceeds the allowable maximum value Tmax, there is a possibility that a smooth steering feeling cannot be obtained.

以下の式１，式２，式３を用いて、接触角Ｄが４０度であるときの回転抵抗トルクＴを求める場合について、具体的に説明する。
式１：Ｆ＝μ・Ｆａ・ｃｏｓ（Ｄ）；
式２：Ｒ＝Ｒｂ・ｓｉｎ（Ｄ）；
式３：Ｔ＝２・Ｆ・Ｒ／１０００；
ここで、式１において、符号Ｆは、接触部３０ａ，３１ａに作用する摩擦荷重［Ｎ］である。符号μは、接触部３０ａ，３１ａ間の摩擦係数である。符号Ｆａは、外輪カップ２８がボール３０をトラニオン２４の軸方向に付勢する付勢力Ｆａ［Ｎ］である。符号Ｄは、接触角［度］である。具体的には、摩擦係数μは、外輪カップ２８とボール３０との金属接触であるので、０．１５である。付勢力Ｆａは、自在継手４の製造時に所定範囲内に設定され、ここでは、その最大値は５００［Ｎ］とした。 The case where the rotational resistance torque T when the contact angle D is 40 degrees is obtained using the following Equation 1, Equation 2, and Equation 3 will be specifically described.
Formula 1: F = μ · Fa · cos (D);
Formula 2: R = Rb · sin (D);
Formula 3: T = 2 · F · R / 1000;
Here, in Formula 1, the code | symbol F is the friction load [N] which acts on the contact parts 30a and 31a. The symbol μ is a friction coefficient between the contact portions 30a and 31a. Reference numeral Fa is an urging force Fa [N] that the outer ring cup 28 urges the ball 30 in the axial direction of the trunnion 24. Reference sign D is a contact angle [degree]. Specifically, the friction coefficient μ is 0.15 because it is a metal contact between the outer ring cup 28 and the ball 30. The urging force Fa is set within a predetermined range when the universal joint 4 is manufactured, and the maximum value is 500 [N] here.

また、式２において、符号Ｒは、接触部３０ａの半径［ｍｍ］である。符号Ｒｂは、ボール３０の半径［ｍｍ］であり、具体的な値は、１．５８７５［ｍｍ］である。この値は、車両用操舵装置の中間軸用の自在継手４に実用的に利用可能なボール３０の最小の半径である。
また、式３において、符号Ｔは、回転抵抗トルク［Ｎ・ｍ］である。符号Ｆは、上述の式１で求めた摩擦荷重［Ｎ］であり、符号Ｒは、式２で求めた接触部３０ａの半径Ｒ［ｍｍ］である。 Moreover, in Formula 2, the code | symbol R is the radius [mm] of the contact part 30a. The symbol Rb is the radius [mm] of the ball 30 and a specific value is 1.5875 [mm]. This value is the minimum radius of the ball 30 that can be practically used for the universal joint 4 for the intermediate shaft of the vehicle steering system.
Further, in Expression 3, the symbol T is the rotational resistance torque [N · m]. The symbol F is the friction load [N] obtained by the above equation 1, and the symbol R is the radius R [mm] of the contact portion 30a obtained by the equation 2.

式１に、上述のμ＝０．１５、Ｆａ＝５００［Ｎ］、Ｄ＝４０度の各値を代入すると、摩擦荷重Ｆ＝５７．５［Ｎ］が得られる。
式２に、上述のＲｂ＝１．５８７５［ｍｍ］、Ｄ＝４０度の各値を代入すると、半径Ｒ＝１．０２０［ｍｍ］が得られる。
式３に、式１で求めた摩擦荷重Ｆ＝５７．５［Ｎ］、式２で求めた半径Ｒ＝１．０２０［ｍｍ］の値を代入すると、回転抵抗トルクＴ＝０．１１７［Ｎ・ｍ］が得られる。 By substituting the above values of μ = 0.15, Fa = 500 [N], and D = 40 degrees into Equation 1, the friction load F = 57.5 [N] is obtained.
By substituting the above values of Rb = 1.5875 [mm] and D = 40 degrees into Equation 2, the radius R = 1.020 [mm] is obtained.
When the values of the friction load F = 57.5 [N] obtained in Equation 1 and the radius R = 1.020 [mm] obtained in Equation 2 are substituted into Equation 3, the rotational resistance torque T = 0.117 [N] M] is obtained.

同様に、接触角Ｄ＝３９［度］に対する回転抵抗トルクＴ［Ｎ・ｍ］を求めると、回転抵抗トルクＴ＝０．１１６［Ｎ・ｍ］が得られる。
このように、実用的な構成においてスムーズな操舵感を得ることができる回転抵抗トルクＴの仮許容最大値Ｔｍａｘ＝０．１１７［Ｎ・ｍ］を、加工時の寸法公差を考慮したときでも確実に越えないようにするには、接触角Ｄ［度］を４０度未満の範囲にする必要があることがわかる。換言すれば、接触角Ｄが４０度未満の範囲内である場合には、回転抵抗トルクＴがその仮許容最大値である０．１１７［Ｎ・ｍ］を越えることはなくて、スムーズな操舵感を得ることができることがわかる。 Similarly, when the rotational resistance torque T [N · m] with respect to the contact angle D = 39 [degrees] is obtained, the rotational resistance torque T = 0.116 [N · m] is obtained.
In this way, the provisional allowable maximum value Tmax = 0.117 [N · m] of the rotational resistance torque T that can obtain a smooth steering feeling in a practical configuration is ensured even when the dimensional tolerance at the time of machining is taken into consideration. It can be seen that the contact angle D [degree] needs to be in a range of less than 40 degrees in order not to exceed. In other words, when the contact angle D is within a range of less than 40 degrees, the rotational resistance torque T does not exceed the provisional allowable maximum value of 0.117 [N · m], and smooth steering is performed. It can be seen that a feeling can be obtained.

図６は、接触角Ｄ［度］と、接触部３０ａ，３１ａの半径Ｒ［ｍｍ］との関係を示すグラフであり、横軸に接触角Ｄ［度］を、縦軸に上述の半径Ｒ［ｍｍ］を示す。図６のグラフは、式２に接触角Ｄの任意の値を代入することにより、この値に対応する半径Ｒの値を求め、得られた半径Ｒの値と接触角Ｄの値とをプロットしたものである。図６のグラフから、接触角Ｄが大きくなると、半径Ｒも大きくなることがわかる。   FIG. 6 is a graph showing the relationship between the contact angle D [degrees] and the radius R [mm] of the contact portions 30a and 31a. The horizontal axis represents the contact angle D [degrees], and the vertical axis represents the radius R described above. [Mm] is shown. In the graph of FIG. 6, by substituting an arbitrary value of the contact angle D into Equation 2, the value of the radius R corresponding to this value is obtained, and the obtained value of the radius R and the value of the contact angle D are plotted. It is a thing. From the graph of FIG. 6, it can be seen that the radius R increases as the contact angle D increases.

具体的には、上述の式２に、Ｒｂ＝１．５８７５［ｍｍ］と、実用的に形成可能な逃げ部３３の最小半径であるＲ＝０．２５［ｍｍ］とを代入し、接触角Ｄの値を逆算すると、接触角Ｄ＝９．１［度］が得られる。このＤ＝９．１［度］の値に寸法公差を考慮すると、接触角Ｄが１０度以上であれば、逃げ部３３を容易に製造することができる。
また、本実施形態について、以下のような変形例を考えることができる。以下の説明では、上述の実施形態と異なる点を中心に説明し、同様の構成については同じ符号を付して説明を省略する。 Specifically, Rb = 1.5875 [mm] and R = 0.25 [mm], which is the minimum radius of the relief portion 33 that can be formed practically, are substituted into the above-described formula 2, and the contact angle is calculated. When the value of D is calculated backward, the contact angle D = 9.1 [degrees] is obtained. In consideration of dimensional tolerance in the value of D = 9.1 [degrees], the relief portion 33 can be easily manufactured if the contact angle D is 10 degrees or more.
Moreover, the following modifications can be considered about this embodiment. In the following description, differences from the above-described embodiment will be mainly described, and the same components are denoted by the same reference numerals and description thereof is omitted.

例えば、図７は、本発明の変形例としての自在継手４の要部の模式図である。図７を参照して、外輪カップ２８の内底面２８ａに凸部３５を設け、トラニオン２４の端面２４ａに凹部３６を設けてもよい。凸部３５と凹部３６との接触角Ｄは、０度を越え４０度未満の範囲内の値である。この構成でも、図３および図４に示された実施形態で説明した効果を得ることができる。   For example, FIG. 7 is a schematic diagram of a main part of the universal joint 4 as a modification of the present invention. Referring to FIG. 7, convex portion 35 may be provided on inner bottom surface 28 a of outer ring cup 28, and concave portion 36 may be provided on end surface 24 a of trunnion 24. The contact angle D between the convex portion 35 and the concave portion 36 is a value in the range of more than 0 degrees and less than 40 degrees. Even with this configuration, the effects described in the embodiment shown in FIGS. 3 and 4 can be obtained.

要は、本実施形態の自在継手４は、上述のトラニオン２４と、上述の複数の針状ころ２７と、上述の外輪カップ２８と、上記トラニオン２４の端面２４ａおよび外輪カップ２８の内底面２８ａの何れか一方に設けられた凸部（例えば、図４ではボール３０、図７では凸部３５）、および他方に設けられ上記凸部を受ける凹部（例えば図４ではボール受け部３１、図７では凹部３６）とを備え、上記凸部および凹部は、トラニオン２４の中心軸線を中心とする環状の接触部３０ａ，３１ａで互いに押圧状態で接触しており、上記接触部３０ａ，３１ａで凸部および凹部間に働く押圧力の方向Ｆ１と、トラニオン２４の中心軸線とのなす角度である接触角Ｄは、０度を越え４０度未満の範囲にあればよい。   In short, the universal joint 4 of the present embodiment includes the trunnion 24, the plurality of needle rollers 27, the outer ring cup 28, the end surface 24a of the trunnion 24 and the inner bottom surface 28a of the outer ring cup 28. A convex portion (for example, the ball 30 in FIG. 4 and the convex portion 35 in FIG. 7) provided on either side, and a concave portion (for example, the ball receiving portion 31 in FIG. 4 and the convex portion 35 in FIG. 7) provided on the other side. A concave portion 36), and the convex portion and the concave portion are in contact with each other in a pressed state at annular contact portions 30a, 31a centering on the central axis of the trunnion 24, and the convex portions and the concave portions 36a, 31a The contact angle D, which is the angle formed between the direction F1 of the pressing force acting between the recesses and the central axis of the trunnion 24, may be in the range of more than 0 degrees and less than 40 degrees.

また、上述の実施形態では、凸部と凹部とは線接触するものとして説明したが、凸部と凹部との接触部が、径方向に所定幅を有する帯状の環状をなしていてもよい。この場合、環状の帯の幅の中心位置に作用する押圧力について、上述の接触角Ｄが、上述の範囲内にあればよい。その他、特許請求の範囲に記載された事項の範囲で種々の設計変更を施すことが可能である。   In the above-described embodiment, the convex portion and the concave portion are described as being in line contact, but the contact portion between the convex portion and the concave portion may form a belt-like ring having a predetermined width in the radial direction. In this case, the above-mentioned contact angle D should just be in the above-mentioned range about the pressing force which acts on the center position of the width | variety of a cyclic | annular belt | band | zone. In addition, various design changes can be made within the scope of matters described in the claims.

本発明の一実施形態の自在継手を含む車両用操舵装置の模式図である。It is a mimetic diagram of a steering device for vehicles containing a universal joint of one embodiment of the present invention. 図１に示す車両用操舵装置の要部の側面図である。It is a side view of the principal part of the steering apparatus for vehicles shown in FIG. 図２に示す自在継手の一部断面図である。It is a partial cross section figure of the universal joint shown in FIG. 図３に示す自在継手の要部の断面図である。It is sectional drawing of the principal part of the universal joint shown in FIG. 図４に示す自在継手における接触角Ｄと、回転抵抗トルクＴとの関係を示すグラフであり、横軸に接触角Ｄ［度］を、縦軸に回転抵抗トルクＴ［Ｎ・ｍ］を示す。5 is a graph showing the relationship between the contact angle D and the rotational resistance torque T in the universal joint shown in FIG. 4, where the horizontal axis represents the contact angle D [degrees] and the vertical axis represents the rotational resistance torque T [N · m]. . 図４に示す自在継手における接触角Ｄと、接触部の半径Ｒとの関係を示すグラフであり、横軸に接触角Ｄ［度］を、縦軸に半径Ｒ［ｍｍ］を示す。It is a graph which shows the relationship between the contact angle D in the universal joint shown in FIG. 4, and the radius R of a contact part, the contact angle D [degree] is shown on a horizontal axis, and the radius R [mm] is shown on a vertical axis | shaft. 本発明の変形例の自在継手の要部の模式図である。It is a schematic diagram of the principal part of the universal joint of the modification of this invention.

符号の説明Explanation of symbols

４，６…自在継手、２０，２１…ヨーク、２２…十字軸、２４…トラニオン、２４ａ…（トラニオンの）端面、２４ｂ…（トラニオンの）外周面、２４ｃ…（トラニオンの）中心軸線、２５…嵌合孔、２７…針状ころ、２８…外輪カップ、２８ａ…（外輪カップの）内底面、３０…ボール（凸部）、３０ａ…接触部、３０ｂ…（ボールの）表面（凸湾曲面、球面）、３０ｃ…先端、３１…ボール受け部（凹部）、３１ａ…接触部（逃げ部の周縁）、３２…凹湾曲面（球面）、３３…逃げ部（凹湾曲面の底部）、Ｄ…接触角、Ｆ１…押圧力の方向、Ｒａ…凸湾曲面の曲率半径   4, 6 ... Universal joints, 20, 21 ... Yoke, 22 ... Cross shaft, 24 ... Trunnion, 24a ... (Trunnion) end face, 24b ... (Trunnion) outer peripheral surface, 24c ... (Trunnion) central axis, 25 ... Fitting hole, 27 ... needle rollers, 28 ... outer ring cup, 28a ... inner bottom surface of (outer ring cup), 30 ... ball (convex part), 30a ... contact part, 30b ... (ball) surface (convex curved surface, Spherical surface), 30c ... tip, 31 ... ball receiving part (concave part), 31a ... contact part (periphery of relief part), 32 ... concave curved surface (spherical surface), 33 ... relief part (bottom part of concave curved surface), D ... Contact angle, F1 ... direction of pressing force, Ra ... radius of curvature of convex curved surface

Claims (2)

十字軸に設けられたトラニオンと、
このトラニオンの外周面の周囲を取り囲んで環状に配置された複数の針状ころと、
ヨークの嵌合孔に保持され、上記針状ころを介して上記トラニオンを回転自在に支持する有底円筒状の外輪カップと、
上記トラニオンの端面および外輪カップの内底面の何れか一方に設けられた凸部、および他方に設けられ上記凸部を受ける凹部とを備え、
上記凸部および凹部は、トラニオンの中心軸線を中心とする環状の接触部で互いに押圧状態で接触しており、
上記接触部で凸部および凹部間に働く押圧力の方向と、トラニオンの中心軸線とのなす角度である接触角は、０度を越え４０度未満の範囲にあり、
上記凸部は、凸湾曲面を含み、
上記凹部は、上記凸湾曲面の曲率半径よりも大きい曲率半径を有する凹湾曲面と、この凹湾曲面の底部に設けられ凸湾曲面の先端から逃げるように窪んだ逃げ部とを含み、上記接触部は、逃げ部の周縁を含むことを特徴とする自在継手。 A trunnion provided on the cross shaft,
A plurality of needle rollers arranged in an annular shape surrounding the periphery of the trunnion;
A cylindrical outer ring cup with a bottom that is held in a fitting hole of the yoke and rotatably supports the trunnion via the needle rollers;
A convex portion provided on any one of the end surface of the trunnion and the inner bottom surface of the outer ring cup, and a concave portion provided on the other side for receiving the convex portion,
The convex portion and the concave portion are in contact with each other in a pressed state at an annular contact portion centering on the central axis of the trunnion,
The direction of the pressing force acting between the convex portion and the concave portion at the contact portion, the contact angle is an angle between the center axis line of the trunnion, Ri range near less than 40 degrees greater than zero degrees,
The convex portion includes a convex curved surface,
The concave portion includes a concave curved surface having a radius of curvature larger than the radius of curvature of the convex curved surface, and a relief portion that is provided at the bottom of the concave curved surface and is recessed so as to escape from the tip of the convex curved surface, The contact portion includes a peripheral edge of the escape portion . 請求項１に記載の自在継手において、
上記凸湾曲面および凹湾曲面は、それぞれ球面を含むことを特徴とする自在継手。 The universal joint according to claim 1 ,
Each of the convex curved surface and the concave curved surface includes a spherical surface.
JP2006066370A 2006-03-10 2006-03-10 Universal joint Expired - Fee Related JP4773233B2 (en)

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