JP2008095845A - Power transmission spline - Google Patents

Power transmission spline Download PDF

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JP2008095845A
JP2008095845A JP2006278853A JP2006278853A JP2008095845A JP 2008095845 A JP2008095845 A JP 2008095845A JP 2006278853 A JP2006278853 A JP 2006278853A JP 2006278853 A JP2006278853 A JP 2006278853A JP 2008095845 A JP2008095845 A JP 2008095845A
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male
spline
female
power transmission
diameter
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Hiroo Morimoto
洋生 森本
Yukio Matsubara
幸生 松原
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NTN Corp
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NTN Corp
NTN Toyo Bearing 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/10—Quick-acting couplings in which the parts are connected by simply bringing them together axially
    • F16D1/108—Quick-acting couplings in which the parts are connected by simply bringing them together axially having retaining means rotating with the coupling and acting by interengaging parts, i.e. positive coupling
    • F16D1/116—Quick-acting couplings in which the parts are connected by simply bringing them together axially having retaining means rotating with the coupling and acting by interengaging parts, i.e. positive coupling the interengaging parts including a continuous or interrupted circumferential groove in the surface of one of the coupling parts
    • 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
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/10—Quick-acting couplings in which the parts are connected by simply bringing them together axially
    • F16D2001/103—Quick-acting couplings in which the parts are connected by simply bringing them together axially the torque is transmitted via splined connections
    • 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
    • F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
    • F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
    • F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
    • F16D2003/22313—Details of the inner part of the core or means for attachment of the core on the shaft

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provid a power transmission spline having improved fatigue strength by relaxing the stress concentration of shearing stress as well as tensile stress. <P>SOLUTION: A male spline part Sm is formed on the outer periphery of a power transmission shaft. At the end on one axial side of a valley portion 21 of the male spline part Sm, a male side diameter enlarged portion 21b is provided whose outer diameter is gradually enlarged toward one axial side. Sectionally circular R-portions 21b1 are provided on both circumferential sides of the diameter enlarged portion 21b, and the curvature radius of the round-portion 21b1 is gradually increased toward one axial side. A female spline part has a female side diameter enlarged portion whose inner diameter is gradually enlarged toward one axial side, and the beginning end of the female side diameter enlarged portion is put in contact with a tooth face 23 on one axial side beyond a beginning end 21b3 of the male side diameter enlarged portion 21b. The beginning end of the female side diameter enlarged portion has no contact with the male side diameter enlarged portion 21b. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

本発明は、雄側部材と雌側部材の間でトルク伝達を行う動力伝達スプライン（セレーションも含まれる。以下、同じ）に関する。   The present invention relates to a power transmission spline (including serrations, hereinafter the same) for transmitting torque between a male member and a female member.

近年、環境問題に対する関心の高まりから、例えば自動車では排ガス規制の強化や燃費向上等が強く求められており、それらの対策の一環として、ドライブシャフト、プロペラシャフト等の動力伝達部品にもさらなる軽量化・強度向上が強く求められている。これら動力伝達部品の多くは、外周面にスプライン部を有する雄側部材と、内周面にスプライン部を有する雌側部材とを構成要素として含む。雄側部材のスプライン部（雄スプライン部）と雌側部材のスプライン部（雌スプライン部）とを嵌合させることにより、雄側部材と雌側部材が連結され、回転動力が伝達される。   In recent years, with increasing interest in environmental issues, for example, automobiles are strongly required to tighten exhaust gas regulations and improve fuel efficiency. As part of these measures, power transmission parts such as drive shafts and propeller shafts are further reduced in weight.・ Strength improvement is strongly demanded. Many of these power transmission components include a male side member having a spline portion on the outer peripheral surface and a female side member having a spline portion on the inner peripheral surface as constituent elements. By fitting the spline part (male spline part) of the male side member and the spline part (female spline part) of the female side member, the male side member and the female side member are connected, and rotational power is transmitted.

雄スプライン部や雌スプライン部の構成は種々知られている。一例として図８ａに、谷部１００の反軸端側（図面左側）の端部を、雄側拡径部１０２を介して雄側部材の外周面（平滑部）１０１につなげた、いわゆる切上がりタイプの雄スプライン部の平面図を示す（図中のクロスハッチングは、雄スプライン部の歯面のうち雌スプライン部との接触領域を現す）。拡径部１０２では、その外径寸法を領域Ｃの範囲で徐々に拡径させている。この形態の雄スプライン部の疲労破壊は、通常、谷部１００と拡径部１０２のつなぎ目付近もしくは拡径部１０２で生じる。その際のき裂発生モードは２つあり、１つはＡ部に集中する引張応力によるもの、もう一つはＢ部に集中する軸方向のせん断応力によるものである。鋼の場合、目安としてビッカース硬さ７００を境に、それ以下ではき裂発生が主としてせん断応力支配となり、それ以上でかつ片振り捩り疲労の場合は引張応力支配となる。   Various configurations of the male spline part and the female spline part are known. As an example, in FIG. 8 a, a so-called up-rounding in which the end on the opposite axis end side (the left side in the drawing) of the valley portion 100 is connected to the outer peripheral surface (smooth portion) 101 of the male side member via the male side enlarged diameter portion 102. The top view of the male spline part of a type is shown (the cross hatching in a figure shows the contact area | region with a female spline part among the tooth surfaces of a male spline part). In the enlarged diameter portion 102, the outer diameter dimension is gradually increased in the range of the region C. The fatigue failure of the male spline portion of this form usually occurs near the joint between the valley portion 100 and the enlarged diameter portion 102 or at the enlarged diameter portion 102. There are two crack generation modes at that time, one is due to the tensile stress concentrated in the A portion, and the other is due to the axial shear stress concentrated in the B portion. In the case of steel, cracks are mainly governed by shear stress below Vickers hardness 700 as a guide, and if it is more than that, and if it is swung torsional fatigue, it is governed by tensile stress.

これまで、スプライン部の疲労強度を向上させるための手段として、いくつかの方法が提案されている。例えば特許文献１では、拡径部と歯面の境界を鈍化させて応力集中を緩和する技術が開示されている。また、特許文献２では、通常は一つの拡径部を軸方向に２つ以上並べて設けた高強度化技術が開示されている。
特開２００５−１４７３６７号公報 特表平１１−５１４０７９号公報 Heretofore, several methods have been proposed as means for improving the fatigue strength of the spline portion. For example, Patent Literature 1 discloses a technique for reducing stress concentration by blunting the boundary between the enlarged diameter portion and the tooth surface. Further, Patent Document 2 discloses a high strength technology in which two or more diameter-expanded portions are usually arranged side by side in the axial direction.
JP 2005-147367 A Japanese National Patent Publication No. 11-514079

しかしながら、特許文献１に記載された技術では、引張応力集中の緩和には効果が認められるが、せん断応力集中の緩和効果は不充分である。また、特許文献２の技術では、せん断応力集中の緩和はできるが、引張応力集中の緩和効果は不充分である。このように、き裂発生を支配する２つの応力のどちらか一方を緩和できる技術は存在するが、双方を同時に緩和する技術は存在せず、さらなる疲労強度向上を実現するためには改良の余地があった。   However, in the technique described in Patent Document 1, an effect is recognized in reducing the tensile stress concentration, but the effect of reducing the shear stress concentration is insufficient. Further, in the technique of Patent Document 2, the shear stress concentration can be reduced, but the effect of reducing the tensile stress concentration is insufficient. As described above, there is a technology that can relieve one of the two stresses that govern crack initiation, but there is no technology that relieves both simultaneously, and there is room for improvement in order to achieve further improvement in fatigue strength. was there.

そこで、本発明では、せん断応力、さらには引張応力の応力集中を緩和させて、動力伝達スプラインの疲労強度の向上を図ることを目的とする。   Therefore, an object of the present invention is to improve the fatigue strength of the power transmission spline by relaxing the stress concentration of shear stress and further tensile stress.

本発明者らは、平行部に切欠きを有する試験片を製作し、これを回転曲げ疲労試験と捩り疲労試験にそれぞれ供して、応力集中係数と疲労強度との関係を求めた。   The inventors of the present invention manufactured a test piece having a notch in a parallel portion, and used it for a rotational bending fatigue test and a torsional fatigue test, respectively, to determine the relationship between the stress concentration factor and the fatigue strength.

試験片としては、図９に示す化学成分の同一ロットの中炭素鋼を用い、図１０ａおよび図１１ａに示す形状および寸法（単位ｍｍ）の試験片を製作した。図１０ａは回転曲げ疲労試験の試験片であり、図１１ａは捩り疲労試験の試験片である。回転曲げ疲労試験の試験片では、切欠き先端の曲率半径を０．１０、０．１５、０．２５、０．５０、１．４０の５水準とし、それぞれの応力集中係数αを３．５、３．０、２．５、２．０、１．５に設定した（図１０ｃ参照）。捩り疲労試験の試験片では、切欠き先端の曲率半径を０．１５、０．２５、０．５０、１．４０の４水準とし、それぞれの応力集中係数αを３．０、２．５、２．０、１．５に設定した（図１１ｃ参照）。これら全ての試験片に対し、切欠きを含む平行部に高周波焼入れを施した後に低温焼戻しを施した。何れの試験片も熱処理後の表面硬度は約ＨＶ６５０であった。   As a test piece, a medium carbon steel having the same chemical composition shown in FIG. 9 was used, and a test piece having the shape and dimensions (unit: mm) shown in FIGS. 10a and 11a was produced. FIG. 10 a is a test piece for a rotating bending fatigue test, and FIG. 11 a is a test piece for a torsional fatigue test. In the specimen of the rotating bending fatigue test, the radius of curvature of the notch tip is set to five levels of 0.10, 0.15, 0.25, 0.50, and 1.40, and the stress concentration coefficient α is 3.5. , 3.0, 2.5, 2.0, 1.5 (see FIG. 10c). In the torsional fatigue test specimen, the radius of curvature of the notch tip is set to four levels of 0.15, 0.25, 0.50, 1.40, and the stress concentration coefficient α is 3.0, 2.5, 2.0 and 1.5 were set (see FIG. 11c). All of these test pieces were subjected to induction quenching in parallel portions including the notches and then subjected to low temperature tempering. All the test pieces had a surface hardness of about HV650 after the heat treatment.

先ず、回転曲げ疲労試験は、小野式回転曲げ疲労試験機により、常温大気中で負荷周波数５０Ｈｚにて行った。   First, the rotating bending fatigue test was performed with an Ono type rotating bending fatigue tester in a room temperature atmosphere at a load frequency of 50 Hz.

回転曲げ疲労試験の結果、切欠きの水準によらず、切欠き底に沿ってき裂が発生して破断に至った。この場合のき裂発生モードは引張応力支配となる。破断に至るまでの負荷回数が１０５を越える辺りまでは、応力振幅の減少に伴って疲労曲線が降下し、応力振幅が一定値を下回ると破断しなくなる明瞭な疲労限現象を示した。なお、ここでの応力振幅は、切欠きの水準によらない公称応力振幅のことで、切欠き底直径（φ６．５ｍｍ）を有する平滑丸棒に疲労試験と同じ大きさの曲げモーメントを与えた時に表面に作用する最大引張応力振幅を意味する。 As a result of the rotating bending fatigue test, cracks occurred along the bottom of the notch regardless of the level of the notch, leading to fracture. The crack initiation mode in this case is governed by tensile stress. Until around exceeding the load count is 10 5 up to the break, fatigue curve drops with decreasing stress amplitude, stress amplitude showed clear fatigue limit phenomena no longer fracture and below a certain value. The stress amplitude here is a nominal stress amplitude that does not depend on the level of the notch, and a smooth round bar having a notch bottom diameter (φ6.5 mm) was given a bending moment of the same size as the fatigue test. It means the maximum tensile stress amplitude that sometimes acts on the surface.

図１２に、上記回転曲げ疲労試験で得られた応力集中係数ασと疲労限強度との関係を示す。図示のように、ασの減少に伴って疲労強度は向上したが、図中に破線で示すように、ασ≦２．７では疲労曲線の勾配が大きく、ασを減少させた時の疲労強度の向上がより顕著に現れることが判明した。 FIG. 12 shows the relationship between the stress concentration factor α σ obtained in the rotating bending fatigue test and the fatigue limit strength. As shown in the figure, the fatigue strength improved as α σ decreased. However, as shown by the broken line in the figure, when α σ ≦ 2.7, the fatigue curve has a large gradient, and when α σ is decreased. It has been found that the improvement in fatigue strength appears more prominently.

次に、捩り疲労試験は、電気式油圧サーボ疲労試験機により、トルク制御にて、常温大気中で負荷周波数２Ｈｚ、完全両振り（応力比Ｒ＝−１）の条件で行った。   Next, the torsional fatigue test was carried out under the conditions of a load frequency of 2 Hz and a full swing (stress ratio R = -1) in a normal temperature atmosphere by torque control using an electric hydraulic servo fatigue tester.

捩り疲労試験の結果、切欠きの水準によらず、切欠き底に沿ってき裂が発生して破断に至った。この場合のき裂発生モードはせん断応力支配となる。両振り捩り疲労試験は負荷回数が最大で１０６回近くになるまで行ったが、その範囲では応力振幅の減少に伴って、疲労曲線が降下した。なお、ここでの応力振幅は、切欠きの水準によらない公称応力振幅のことで、切欠き底直径（φ１７ｍｍ）を有する平滑丸棒に疲労試験と同じ大きさの捩りトルクを与えた時に表面に作用する最大せん断応力振幅を意味する。 As a result of the torsional fatigue test, cracks occurred along the bottom of the notch regardless of the level of the notch, leading to fracture. The crack initiation mode in this case is governed by shear stress. Both reversed torsional fatigue test is load count went until near 10 6 times at most in the range with decreasing stress amplitude fatigue curve drops. The stress amplitude here is a nominal stress amplitude that does not depend on the level of the notch, and is applied to a smooth round bar having a notch bottom diameter (φ17 mm) when a torsion torque of the same magnitude as that in the fatigue test is applied. Means the maximum shear stress amplitude acting on

図１３に、上記両振り捩り疲労試験で得られた応力集中係数ατと１０５回における疲労強度との関係を示す。図示のように、ατの減少に伴って疲労強度は向上したが、図中に破線で示すように、ατ≦２．１では疲労曲線の勾配が大きく、ατを減少させた時の疲労強度の向上がより顕著に現れることが判明した。 13 shows a relationship between fatigue strength of the both reversed torsional fatigue test with the resulting stress concentration factor alpha tau and 10 5 times. As shown in the figure, the fatigue strength improved as α τ decreased. However, as shown by the broken line in the figure, when α τ ≦ 2.1, the fatigue curve gradient was large, and when α τ was decreased, It has been found that the improvement in fatigue strength appears more prominently.

以上から、き裂発生が引張応力、せん断応力のどちらに支配される場合であっても応力集中緩和によって疲労強度が向上し、特に引張応力に対してはασ≦２．７で、また、せん断応力に対してはατ≦２．１でより応力集中の緩和効果が高まることが判明した。従って、双方の破損モードで疲労破壊する雄スプライン部の拡径部においては、そこに集中する第１主応力の最大値σ１ｍａｘを基準応力τ０の２．７倍以下（σ１ｍａｘ≦２．７τｏ）、軸方向のせん断応力の最大値τθｚｍａｘを基準応力τ０の２．１倍以下（τθｚｍａｘ≦２．１τ０）となるよう形状をチューニングすることが望ましい。ここで、基準応力τ０は、トルクＴと、図６に示す雄スプライン部Ｓｍの谷部底の直径ｄｏと、雄スプライン部の内径ｄｉとに対し、以下で与えられる値である。 From the above, whether the crack initiation is governed by either tensile stress or shear stress, the fatigue strength is improved by stress concentration relaxation, particularly α σ ≦ 2.7 for tensile stress, It has been found that the stress concentration relaxation effect is further enhanced when α τ ≦ 2.1 against shear stress. Accordingly, in the expanded portion of the male spline portion that undergoes fatigue failure in both failure modes, the maximum value σ 1max of the first principal stress concentrated there is not more than 2.7 times the reference stress τ 0 (σ 1max ≦ 2. 7τ o ), and it is desirable to tune the shape so that the maximum value τ θzmax of the shear stress in the axial direction is 2.1 times or less (τ θzmax ≦ 2.1τ 0 ) of the reference stress τ 0 . The reference stress tau 0 is the torque T, the diameter d o of the valley bottom of the male spline section Sm shown in FIG. 6, with respect to the inner diameter d i of the male spline portion, which is a value given below.

τ０＝１６Ｔｄｏ／［π（ｄｏ ４−ｄｉ ４）］ τ 0 = 16 Td o / [π (d o 4 −d i 4 )]

本発明者らが拡径部の形状を種々チューニングした結果、雄スプライン部の拡径部の円周方向両側にアール部を設け、アール部の曲率半径を反軸端側に向けて徐々に大きくすれば、σ１ｍａｘ≦２．７τｏ、およびτθｚｍａｘ≦２．１τ０を満足できることが判明した。 As a result of various tunings of the shape of the enlarged diameter portion by the present inventors, rounded portions are provided on both sides in the circumferential direction of the enlarged diameter portion of the male spline portion, and the curvature radius of the rounded portion is gradually increased toward the opposite shaft end side. Then, it was found that σ 1max ≦ 2.7τ o and τ θzmax ≦ 2.1τ 0 can be satisfied.

次に、図１０（ａ）および図１１（ａ）の切欠き疲労試験片と同じ成分（図９参照）の素材を用いて、両軸端に雄スプライン部を有するシャフト形状試験片を製作し（図１７ａ参照）、この試験片を用いて両振り捩り疲労試験および片振り捩り疲労試験を行った。試験片には、図１７ｂに示すインボリュートスプライン諸元に準じ、本発明品相当の雄スプライン部と従来品相当の雄スプライン部を形成した。これら試験片には、その全体に大気中の同一条件で高周波焼入れおよび焼戻しが施されている。両振り捩り疲労試験は８５０〜１３００Ｎｍの範囲の４水準で行い、片振り捩り疲労試験は１２５０〜２０００Ｎｍの範囲の４水準の最大捩りトルクを付与している。図１８に両振り捩り疲労試験で得られたＴ／Ｎ線図、図１９に片振り疲労試験で得られたＴ／Ｎ線図を示す。両図からも明らかなように、本発明品では、従来品に対して両振り捩り疲労および片振り捩り疲労の双方で大幅な疲労強度の向上を達成することができる。   Next, a shaft-shaped test piece having male spline portions at both shaft ends is manufactured using a material having the same component (see FIG. 9) as the notched fatigue test piece of FIGS. 10 (a) and 11 (a). (See FIG. 17a) Using this test piece, a double torsional fatigue test and a single torsional fatigue test were performed. According to the specifications of the involute spline shown in FIG. 17b, a male spline portion equivalent to the product of the present invention and a male spline portion equivalent to the conventional product were formed on the test piece. These test pieces are subjected to induction hardening and tempering under the same conditions in the atmosphere as a whole. The double torsional fatigue test is conducted at four levels in the range of 850 to 1300 Nm, and the single torsional fatigue test gives a maximum torsional torque of four levels in the range of 1250 to 2000 Nm. FIG. 18 shows a T / N diagram obtained in the double swing torsional fatigue test, and FIG. 19 shows a T / N diagram obtained in the single swing fatigue test. As is clear from both figures, the product of the present invention can achieve a significant improvement in fatigue strength in both the double torsional fatigue and the single swing torsional fatigue compared to the conventional product.

また、発明者らが鋭意検討した結果、せん断応力が集中する位置は、雄スプライン部の歯の形態のみならず、雌スプライン部の歯の形態にも左右されることが明らかになった。具体的には、雌スプライン部の山部に、図８ａに示すように、軸方向一方側（シャフトの反軸端側となる方向）に向けて内径寸法が拡径する雌側拡径部１０４を形成した場合、雌側拡径部の開始端１０３よりも軸方向一方側にせん断応力の集中部Ｂを生じることが判明した。   Further, as a result of intensive studies by the inventors, it has been clarified that the position where the shear stress is concentrated depends not only on the tooth shape of the male spline part but also on the tooth form of the female spline part. Specifically, as shown in FIG. 8a, the female-side enlarged portion 104 whose inner diameter increases toward the one side in the axial direction (the direction opposite to the shaft end) as shown in FIG. 8a. It was found that a concentrated portion B of shear stress occurs on one side in the axial direction from the start end 103 of the female-side enlarged portion.

一般に、捩りトルクにより発生するせん断応力は、その作用部位の径寸法に依存し、径寸法が大きくなるほど発生するせん断応力は小さくなる。従って、従来のように、雌スプライン部の雌側拡径部１０４の開始端１０３が、雄スプライン部の雄側拡径部１０２の開始端１０５よりも軸端側にあると、せん断応力の集中部Ｂが径寸法の小さい雄側拡径部１０２の開始端１０５付近で発生し、これが疲労寿命に悪影響を与えていると考えられる。   In general, the shear stress generated by the torsional torque depends on the diameter size of the acting site, and the generated shear stress decreases as the diameter size increases. Therefore, if the starting end 103 of the female-side enlarged portion 104 of the female spline portion is located on the axial end side of the starting end 105 of the male-side enlarged portion 102 of the male spline portion as in the prior art, the concentration of shear stress is increased. It is considered that the portion B occurs in the vicinity of the start end 105 of the male-side enlarged portion 102 having a small diameter size, which has an adverse effect on the fatigue life.

これに対し、図８ｂに示すように、雌スプライン部の雌側拡径部３２ｃの開始端３２ｃ１を、雄側拡径部２１ｂの開始端２１ｂ３よりも軸方向一方側に配置すれば、せん断応力の集中部Ｂが径寸法の大きい雄側拡径部２１ｂの領域中で発生する。そのため、せん断応力の集中度合いを低減することができ、疲労強度を向上させることが可能となる。この場合、図８ｃに示すように、雌側拡径部３２ｃの開始端３２ｃ１を、雄側拡径部２１ｂに接触させると、疲労強度が大幅に低下することが判明した。従って、雌側拡径部３２ｃの開始端３２ｃ１は、図８ｂに示すように、雄側拡径部２１ｂと非接触にしておくのが望ましい。   On the other hand, as shown in FIG. 8b, if the start end 32c1 of the female side enlarged portion 32c of the female spline portion is arranged on one side in the axial direction from the start end 21b3 of the male side enlarged portion 21b, the shear stress The concentrated portion B is generated in the region of the male-side enlarged portion 21b having a large diameter. Therefore, the degree of concentration of shear stress can be reduced, and the fatigue strength can be improved. In this case, as shown in FIG. 8c, it was found that the fatigue strength is greatly reduced when the start end 32c1 of the female side enlarged portion 32c is brought into contact with the male side enlarged portion 21b. Accordingly, it is desirable that the start end 32c1 of the female side enlarged portion 32c is not in contact with the male side enlarged portion 21b as shown in FIG. 8b.

以上から、本発明は、以下の事項によって特徴付けられるものである。   As described above, the present invention is characterized by the following matters.

（Ｉ）雄側部材の外周に設けられ、谷部の軸方向一方側にその外径寸法を徐々に拡径させた雄側拡径部を有する雄スプライン部と、雌側部材の内周に設けられ、山部に軸方向一方側に向けてその内径寸法を徐々に拡径させた雌側拡径部を有する雌スプライン部とを有する動力伝達スプラインにおいて、雄スプライン部の雄側拡径部の円周方向両側にアール部を設け、アール部の曲率半径を軸方向一方側に向けて徐々に大きくし、雌スプライン部の雌側拡径部の開始端を、雄側拡径部の開始端よりも軸方向一方側に配置する。雌側拡径部の開始端は、雄側拡径部と非接触にしておくのが望ましい。   (I) A male spline portion provided on the outer periphery of the male side member and having a male side enlarged portion whose outer diameter is gradually increased on one side in the axial direction of the valley, and an inner periphery of the female side member A power transmission spline provided with a female spline portion having a female-side enlarged portion whose inner diameter is gradually enlarged toward one side in the axial direction at the peak portion, and a male-side enlarged portion of the male spline portion Are provided on both sides in the circumferential direction, and the radius of curvature of the rounded portion is gradually increased toward one side in the axial direction, and the starting end of the female-side enlarged portion of the female spline portion is the start of the male-side enlarged portion. It arrange | positions in the axial direction one side rather than an end. It is desirable that the starting end of the female side enlarged portion is not in contact with the male side enlarged portion.

（ＩＩ）トルクＴが負荷されたときに、雄スプライン部の雄側拡径部に作用する第１主応力、および軸方向のせん断応力の最大値をそれぞれσ１ｍａｘ、τθｚｍａｘとし、トルクＴ、雄スプライン部の谷部の直径ｄｏ、雄スプライン部の内径ｄｉに対し、１）式で与えられる基準応力τ０とするとき、下記２）式と３）式を同時に満たすようにする（なお、雄スプライン部が中実部分に形成されている場合には、ｄｉ＝０である）。 (II) When the torque T is loaded, the first principal stress acting on the male-side diameter-enlarged portion of the male spline portion and the maximum value of the axial shear stress are σ 1max and τ θzmax , respectively. When the reference stress τ 0 given by the equation (1) is set to the diameter d o of the valley portion of the male spline portion and the inner diameter d i of the male spline portion, the following equations 2) and 3) are simultaneously satisfied ( Note that d i = 0 when the male spline portion is formed in a solid portion).

τ０＝１６Ｔｄｏ／［π（ｄｏ ４−ｄｉ ４）］ …１） τ 0 = 16 Td o / [π (d o 4 −d i 4 )]... 1)

σ１ｍａｘ≦２．７τｏ …２） σ 1max ≦ 2.7τ o ... 2)

τθｚｍａｘ≦２．１τ０ …３） τ θzmax ≦ 2.1τ 0 ... 3)

本発明者が検証したところ、以上の構成においては、アール部の曲率半径の増加率をｄＲ／ｄＬ、雄側拡径部の軸方向断面の内径端と外径端を結ぶ直線の角度をθとするとき、それぞれの値を０．０５≦ｄＲ／ｄＬ≦０．６０、および５°≦θ≦２０°の範囲に設定するのが望ましいことが判明した。   As a result of verification by the present inventor, in the above-described configuration, the rate of increase in the radius of curvature of the rounded portion is dR / dL, and the angle of the straight line connecting the inner diameter end and the outer diameter end of the axial cross section of the male enlarged portion It is found that it is desirable to set the respective values in the ranges of 0.05 ≦ dR / dL ≦ 0.60 and 5 ° ≦ θ ≦ 20 °.

雄スプライン部または雌スプライン部の一方もしくは双方に高周波焼入れもしくは浸炭焼入れ等の手段で、焼入れ硬化処理を施すのが好ましい。さらに動力伝達シャフトの雄スプライン部にショットピーニングを施すことにより、雄スプライン部の疲労強度をより一層高めることができる。   It is preferable that one or both of the male spline part and the female spline part is subjected to quench hardening by means of induction hardening or carburizing hardening. Furthermore, the fatigue strength of the male spline portion can be further increased by performing shot peening on the male spline portion of the power transmission shaft.

以上のように、本発明によれば、雄スプライン部における引張応力集中とせん断応力集中の双方を緩和させることができる。従って、より高い疲労強度を有する動力伝達スプラインの提供が可能となる。   As described above, according to the present invention, both the tensile stress concentration and the shear stress concentration in the male spline part can be relaxed. Therefore, it is possible to provide a power transmission spline having higher fatigue strength.

以下、本発明の実施の形態を、添付図面を参照して説明する。   Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.

図１は、動力伝達スプラインを有する等速自在継手１を示す。この等速自在継手１は、一方の動力伝達シャフト２に固定される内側継手部材３、内側継手部材３の外径側に配置され、他方の動力伝達シャフト９を有する外側継手部材４、内側継手部材３と外側継手部材４との間でトルクを伝達するトルク伝達部材としてのボール５を主要構成要素とする。図示例の等速自在継手１は、ツエッパ型と称される固定型のもので、内側継手部材３の外周に形成されたトラック溝３ａと外側継手部材４の内周に形成されたトラック溝４ａとで形成されるボールトラックにボール５を配置し、円周方向等配位置に配置した複数のボール５をケージ７で保持したものである。等速自在継手１としては、図示例のものに限定されず、他の固定型等速自在継手（アンダーカットフリー型等速自在継手等）、さらにはトリポード型等速自在継手をはじめとする摺動型等速自在継手も使用可能である。   FIG. 1 shows a constant velocity universal joint 1 having a power transmission spline. The constant velocity universal joint 1 includes an inner joint member 3 fixed to one power transmission shaft 2, an outer joint member 4 disposed on the outer diameter side of the inner joint member 3, and the other power transmission shaft 9. A ball 5 as a torque transmitting member that transmits torque between the member 3 and the outer joint member 4 is a main component. The illustrated constant velocity universal joint 1 is a fixed type called a zepper type, and a track groove 3 a formed on the outer periphery of the inner joint member 3 and a track groove 4 a formed on the inner periphery of the outer joint member 4. The balls 5 are arranged on a ball track formed by the following, and a plurality of balls 5 arranged at equal circumferential positions are held by a cage 7. The constant velocity universal joint 1 is not limited to the illustrated example, and other fixed type constant velocity universal joints (such as undercut-free type constant velocity universal joints), and a slide including a tripod type constant velocity universal joint. A dynamic constant velocity universal joint can also be used.

雄側部材となる動力伝達シャフト２は、炭素量０．３０〜０．６０mass程度の中炭素鋼（例えばＪＩＳ Ｇ４０５１に規定の機械構造用炭素鋼Ｓ４０Ｃ）で形成される。Ｃ量が０．３０mass％を下回ると、高周波焼入れしても安定した高硬度を得ることができず、０．６０mass％を越えると、素材硬度が上昇して後述の雄スプライン部Ｓｍを転造等で成形する際の加工性が低下する。   The power transmission shaft 2 serving as a male member is made of medium carbon steel (for example, carbon steel S40C for machine structure defined in JIS G4051) having a carbon content of about 0.30 to 0.60 mass. If the amount of C is less than 0.30 mass%, stable high hardness cannot be obtained even by induction hardening, and if it exceeds 0.60 mass%, the material hardness increases and the male spline portion Sm described later is rolled. The workability at the time of molding by, for example, decreases.

動力伝達シャフト２の軸端外周には、雄スプライン部Ｓｍが形成される。この雄スプライン部Ｓｍの歯を、図３に示すように雌側部材、たとえば内側継手部材３の内周に形成された雌スプライン部Ｓｆと嵌合させることによって、動力伝達シャフト２と内側継手部材３とがトルク伝達可能に結合されている。内側継手部材３は、例えば内側継手部材３の反軸端側（図３の左側）の内径端部を動力伝達シャフト２外周の肩部２４に当接させ、かつ軸端側（図３の右側）の内径端部を、例えば止め輪８（図１参照）で係止することによって、動力伝達シャフト２に対して軸方向で位置決め固定される。図１では、雄スプライン部Ｓｍを中実の動力伝達シャフト２の外周に形成した場合を例示しているが、図６に示すように内径ｄｉの中空軸の外周に形成することもできる。 A male spline portion Sm is formed on the outer periphery of the shaft end of the power transmission shaft 2. By fitting the teeth of the male spline part Sm with a female side member, for example, a female spline part Sf formed on the inner periphery of the inner joint member 3 as shown in FIG. 3, the power transmission shaft 2 and the inner joint member 3 is coupled to transmit torque. The inner joint member 3 has, for example, an inner diameter end portion on the opposite shaft end side (left side in FIG. 3) of the inner joint member 3 abutted against a shoulder portion 24 on the outer periphery of the power transmission shaft 2 and a shaft end side (right side in FIG. 3). ) Is fixed with respect to the power transmission shaft 2 in the axial direction by, for example, locking with the retaining ring 8 (see FIG. 1). In Figure 1, but illustrates a case of forming the male spline section Sm in solid outer periphery of the power transmission shaft 2, it can be formed on the outer periphery of the hollow shaft inside diameter d i, as shown in FIG.

図２、図３、および図６に示すように、動力伝達シャフト２の雄スプライン部Ｓｍは、軸方向に延びる谷部２１と山部２２とを円周方向に交互に有する。この実施形態の雄スプライン部Ｓｍは、転造加工で形成されたいわゆる切上りタイプで、各谷部２１は、軸方向で同径寸法のストレート部２１ａと、その反軸端側に形成された雄側拡径部２１ｂとで構成される。各山部２２も同様に、軸方向で同径寸法のストレート部２２ａと、その反軸端側に形成された雄側縮径部２２ｂとで構成される。図４に示すように、雄側拡径部２１ｂの開始端２１ｂ３と雄側縮径部２２ｂの開始端は軸方向で同じ位置にあり、かつその終端も軸方向で同じ位置にある。この雄スプライン部Ｓｍは冷間鍛造で成形することもでき、この場合は、通常、山部２２の雄側縮径部２２ｂは形成されず、山部２２の反軸端側は全体が同一外径寸法となる。   As shown in FIGS. 2, 3, and 6, the male spline portion Sm of the power transmission shaft 2 has trough portions 21 and crest portions 22 extending in the axial direction alternately in the circumferential direction. The male spline portion Sm of this embodiment is a so-called up-round type formed by rolling, and each valley portion 21 is formed on the straight portion 21a having the same diameter in the axial direction and on the opposite end side. It is comprised with the male side enlarged diameter part 21b. Similarly, each peak portion 22 includes a straight portion 22a having the same diameter in the axial direction and a male-side reduced diameter portion 22b formed on the opposite end side. As shown in FIG. 4, the start end 21b3 of the male-side enlarged diameter portion 21b and the start end of the male-side reduced diameter portion 22b are at the same position in the axial direction, and the end thereof is also at the same position in the axial direction. This male spline part Sm can also be formed by cold forging. In this case, normally, the male side reduced diameter part 22b of the peak part 22 is not formed, and the entire opposite end side of the peak part 22 is the same outside. It becomes a diameter dimension.

図３に示すように、雌スプライン部Ｓｆの谷部３１は、同径寸法で軸方向一方側（シャフト２の反軸端側と同方向）の端部まで形成されている。一方、山部３２は、小径部３２ａ、大径部３２ｂ、小径部３２ａと大径部３２ｂの間の雌側拡径部３２ｃを有する。大径部３２ｂの内径寸法は、雄スプライン部Ｓｍの山部２２の最大外径寸法（ストレート部２２ａの外径寸法）よりも小さく、雄スプライン部Ｓｍの反軸端側で動力伝達シャフト２の外周に形成された平滑部２５の外径寸法よりも大きい。雌側拡径部３２ｃの開始端３２ｃ１は、雄側拡径部２１ｂの開始端２１ｂ３よりも反軸端側にあり、かつ雄側拡径部２１ｂとは非接触の位置にある。   As shown in FIG. 3, the valley portion 31 of the female spline portion Sf has the same diameter and is formed up to the end portion on the one axial side (the same direction as the non-axial end side of the shaft 2). On the other hand, the mountain portion 32 includes a small diameter portion 32a, a large diameter portion 32b, and a female-side large diameter portion 32c between the small diameter portion 32a and the large diameter portion 32b. The inner diameter dimension of the large diameter part 32b is smaller than the maximum outer diameter dimension (outer diameter dimension of the straight part 22a) of the peak part 22 of the male spline part Sm, and the power transmission shaft 2 on the opposite end side of the male spline part Sm. It is larger than the outer diameter of the smooth portion 25 formed on the outer periphery. The start end 32c1 of the female side enlarged portion 32c is located on the side opposite the axial end from the start end 21b3 of the male side enlarged portion 21b, and is in a non-contact position with the male side enlarged portion 21b.

雄スプライン部Ｓｍと雌スプライン部Ｓｆとを互いに嵌合させると、雄スプライン部Ｓｍの歯面２３と、雌スプライン部Ｓｆの歯面（図示省略）とが強く圧接する。この時の両歯面の嵌合部（散点模様で表す）は、図４に示すように、雄側拡径部２１ｂの外径側領域にも及んでいる。雌側拡径部３２ｃの開始端３２ｃ１は、雄側拡径部２１ｂの開始端２１ｂ３よりも軸方向一方側（反軸端側）で、雄スプライン部Ｓｆの歯面２３と接触している。   When the male spline portion Sm and the female spline portion Sf are fitted to each other, the tooth surface 23 of the male spline portion Sm and the tooth surface (not shown) of the female spline portion Sf are in strong pressure contact. At this time, the fitting portions (represented by a dotted pattern) of both tooth surfaces extend to the outer diameter side region of the male-side enlarged diameter portion 21b as shown in FIG. The start end 32c1 of the female side enlarged portion 32c is in contact with the tooth surface 23 of the male spline portion Sf on one side in the axial direction (the opposite end side) from the start end 21b3 of the male side enlarged portion 21b.

なお、図３では、雄側拡径部２１ｂ、雄側縮径部２２ｂ、雌側拡径部３２ｃの軸方向断面を何れも直線的なテーパ状に形成した場合を例示しているが、両者の軸方向断面を曲線状に形成することもできる。また、直線状と曲線状の複合形状とすることもできる。   FIG. 3 illustrates the case where the axial cross sections of the male side enlarged portion 21b, the male side reduced portion 22b, and the female side enlarged portion 32c are all formed in a linear taper shape. The cross section in the axial direction can be formed in a curved shape. Moreover, it can also be set as the composite shape of a linear form and a curvilinear form.

図２に示すように、本発明において雄スプライン部Ｓｍの雄側拡径部２１ｂは、その円周方向両側に形成されたアール部２１ｂ１（散点模様で示す）と、アール部２１ｂ１の間に形成された平面状の平坦部２１ｂ２とで構成される。アール部２１ｂ１は半径方向断面が円弧状をなし、その円周方向両側は歯面２３および平坦部２１ｂ２に滑らかにつながっている。   As shown in FIG. 2, in the present invention, the male side enlarged portion 21b of the male spline portion Sm is between a rounded portion 21b1 (shown as a dotted pattern) formed on both sides in the circumferential direction and the rounded portion 21b1. It is comprised by the formed planar flat part 21b2. The radius portion 21b1 has a circular cross section in the radial direction, and both circumferential sides thereof are smoothly connected to the tooth surface 23 and the flat portion 21b2.

図４は、雄スプライン部Ｓｍのうち、雄側拡径部２１ｂ付近を示す平面図、図５ａ〜図５ｄは、図４におけるＡ−Ａ線、Ｂ−Ｂ線、Ｃ−Ｃ線、Ｄ−Ｄ線の各断面図である。図５ａに示すように、谷部２１のストレート部２１ａと歯面２３とをつなぐアール部の曲率半径ＲＡは、雄側拡径部２１ｂの開始端２１ｂ３に至るまで一定である。図５ｂ〜図５ｄに示すように、雄側拡径部２１ｂでは、アール部２１ｂ１の曲率半径が、開始端２１ｂ３の曲率半径ＲＡよりも大きく、かつ反軸端側ほど徐々に大きくなっている（ＲＡ＜ＲＢ＜ＲＣ＜ＲＤ）。また、図４に示すように、アール部２１ｂ１の境界線が山部の稜線と交わって歯面２３が無くなる位置までは、アール部２１ｂ１の円周方向の幅寸法は反軸端側（図面上方）に向けて徐々に拡大し、これを超えると幅寸法は徐々に縮小している。平坦部２１ｂ２の円周方向の幅寸法も反軸端側に向けて徐々に拡大している。 4 is a plan view showing the vicinity of the male-side enlarged diameter portion 21b in the male spline portion Sm, and FIGS. 5a to 5d are AA, BB, CC, and D- in FIG. It is each sectional drawing of a D line. As shown in FIG. 5a, the radius of curvature R A of the round portion connecting the straight portion 21a and the tooth surface 23 of the trough portion 21 is constant up to the starting end 21b3 of the male-side diameter-enlarged portion 21b. As shown in FIG 5b~ Figure 5d, the male-side diameter-enlarged portion 21b, the curvature radius of the rounded portion 21b1 is gradually increases significantly, and as Hanjiku end than the radius of curvature R A of the start end 21b3 (R A <R B <R C <R D). Further, as shown in FIG. 4, the width of the round portion 21b1 in the circumferential direction is on the side opposite the axis (upward in the drawing) until the position where the boundary line of the round portion 21b1 intersects the ridge line of the mountain portion and the tooth surface 23 disappears. ) Gradually expands toward (), and beyond this, the width dimension gradually decreases. The width dimension in the circumferential direction of the flat portion 21b2 is also gradually increased toward the opposite shaft end side.

図４中のＬは、雄側拡径部２１ｂのアール部２１ｂ１において、その曲率半径の中心を通る線の方向にとった座標を示す。アール部２１ｂ１の曲率半径の増加率は、ｄＲ／ｄＬで表され、本実施形態ではｄＲ／ｄＬ＝０．１８に設定している。また、図４中のθは、拡径部２１ｂの軸方向断面の内径端と外径端を結ぶ直線の傾斜角を表し、本実施形態ではθ＝８．３°に設定している。   L in FIG. 4 indicates coordinates taken in the direction of a line passing through the center of the radius of curvature in the rounded portion 21b1 of the male-side enlarged portion 21b. The increasing rate of the radius of curvature of the rounded portion 21b1 is represented by dR / dL, and is set to dR / dL = 0.18 in this embodiment. Further, θ in FIG. 4 represents the inclination angle of a straight line connecting the inner diameter end and the outer diameter end of the axial section of the enlarged diameter portion 21b, and is set to θ = 8.3 ° in the present embodiment.

図１４〜図１６に、上記特許文献１（特開２００５−１４７３６７号公報）に記載された雄スプライン部Ｓｍ’、すなわち、雄側拡径部２１ｂ’と歯面２３’の境界にアール部２１ｂ１’を形成し、かつアール部２１ｂ１’の曲率半径を軸方向全長にわたって一定とした雄スプライン部Ｓｍ’を示す。雌スプライン部Ｓｆ’のうち、山部３２’に形成された拡径部３２ｃ’の開始端３２ｃ１’は、雄側拡径部２１ｂ’の開始端２１ｂ３’よりも軸端側にある（なお、図１４〜図１６では、図２〜図４に表された部位と対応する部位に（’）を加えた同一符号を付している）。   14 to 16, the male spline portion Sm ′ described in Patent Document 1 (Japanese Patent Laid-Open No. 2005-147367), that is, the rounded portion 21b1 at the boundary between the male-side enlarged portion 21b ′ and the tooth surface 23 ′. A male spline portion Sm ′ is formed, in which the radius of curvature of the rounded portion 21b1 ′ is constant over the entire length in the axial direction. Of the female spline portion Sf ′, the start end 32c1 ′ of the enlarged diameter portion 32c ′ formed in the peak portion 32 ′ is closer to the shaft end side than the start end 21b3 ′ of the male enlarged diameter portion 21b ′ (note that In FIGS. 14-16, the same code | symbol which added (') to the site | part corresponding to the site | part represented by FIGS. 2-4 is attached | subjected.

図２に示す雄スプライン部Ｓｍ（本発明品）と図１４に示す雄スプライン部Ｓｍ’（従来品）のそれぞれについてＦＥＭ解析を行い、それぞれについて第１主応力の最大値σ１ｍａｘとせん断応力の最大値τθｚｍａｘを求め、これらを上記基準応力τ０で除した値を算出した。 FEM analysis is performed for each of the male spline portion Sm (product of the present invention) shown in FIG. 2 and the male spline portion Sm ′ (conventional product) shown in FIG. 14, and the maximum value σ 1max of the first principal stress and the shear stress of each are analyzed. A maximum value τ θzmax was obtained, and a value obtained by dividing the maximum value τ θzmax by the reference stress τ 0 was calculated.

このＦＥＭ解析は、３次元線形弾性解析であり、解析ソフトとして “I-deas Ver.10”を使用した。解析モデルは、図２０に示すように、雄スプライン部Ｓｍ、Ｓｍ’の１つの谷部２１、２１’を含む線形弾性体で、モデル長は１００ｍｍである。図２１に、この解析モデルに付したメッシュを示す。各要素は４面体二次要素で、総要素数は約２０万個、総接点数は約３０万個である。要素長は、主要部分Ｐ（雄スプライン部Ｓｍ、Ｓｍ’を含む部分で）で０．２ｍｍ以下とし（最小要素長は０．０５ｍｍ）、主要部分Ｐ以外で０．５ｍｍとした。図２２は、主要部分Ｐのメッシュを拡大して示す図であり、同図（ａ）が図２に対応した本発明品を表し、同図（ｂ）が図１４に対応した従来品を表す。図２３に示すように、解析モデルの反軸端側端面ＭにRigid要素を作成し、この端面Ｍの中心軸Ｏ上にトルクＴを負荷した。但し、モデルとして、１／歯数モデルを使用しているので、負荷トルクは、実際のトルクの１／歯数である。図２４に示すように、解析モデルは、谷部２１の中心を通る半径方向軸を対称軸とした形状で、円周方向の両側面Ｗの全接点を周期対称としている。なお、図２５に示すように、解析モデルの相手部材との接触面（散点模様で示す）では、その法線方向の変位が拘束されている。   This FEM analysis is a three-dimensional linear elastic analysis, and “I-deas Ver. 10” was used as analysis software. As shown in FIG. 20, the analysis model is a linear elastic body including one valley portion 21, 21 ′ of the male spline portions Sm, Sm ′, and the model length is 100 mm. FIG. 21 shows a mesh attached to this analysis model. Each element is a tetrahedral secondary element, the total number of elements is about 200,000, and the total number of contacts is about 300,000. The element length was 0.2 mm or less (the minimum element length was 0.05 mm) at the main portion P (including the male spline portions Sm and Sm ′), and 0.5 mm at the portions other than the main portion P. FIG. 22 is an enlarged view showing the mesh of the main part P. FIG. 22A shows the product of the present invention corresponding to FIG. 2, and FIG. 22B shows the conventional product corresponding to FIG. . As shown in FIG. 23, a Rigid element was created on the end face M on the opposite end side of the analysis model, and a torque T was loaded on the central axis O of the end face M. However, since a 1 / tooth number model is used as a model, the load torque is 1 / tooth number of actual torque. As shown in FIG. 24, the analysis model has a shape in which the radial axis passing through the center of the valley portion 21 is an axis of symmetry, and all the contacts on both side surfaces W in the circumferential direction are cyclically symmetric. In addition, as shown in FIG. 25, the displacement of the normal direction is restrained in the contact surface (it shows with a dotted pattern) with the other party member of an analysis model.

第１主応力σ１の解析結果を図２６に示し、軸方向せん断応力τθｚの解析結果を図２７に示す。なお、図２６および図２７の何れでも、（ａ）図が本発明品モデルを表し、（ｂ）図が従来品モデルを示す。なお、両図中の基準応力τ０は、トルクＴ、雄スプライン部Ｓｍの谷部の直径ｄｏ、雄スプライン部の内径ｄｉに対し、τ０＝１６Ｔｄｏ／［π（ｄｏ ４−ｄｉ ４）］なる式で与えられる。 The analysis result of the first principal stress σ 1 is shown in FIG. 26, and the analysis result of the axial shear stress τ θz is shown in FIG. 26A and 27B, FIG. 26A shows the product model of the present invention, and FIG. 26B shows the conventional product model. The reference stress τ 0 in both figures is τ 0 = 16 Td o / [π (d o 4 − −) with respect to the torque T, the diameter d o of the valley of the male spline part Sm, and the inner diameter d i of the male spline part. d i 4 )].

以上の解析結果から、従来品では、σ１ｍａｘ／τ０＝３．０３であるのに対し、本発明品では、σ１ｍａｘ／τ０＝２．４８となり、従来品より引張応力に対する応力集中の緩和効果が高まることが判明した。これは、本発明品では、歯面２３の終端近傍におけるアール部２１ｂ１の曲率半径が、従来品の対応部位での曲率半径よりも大きくなるためと考えられる。先に説明したように、引張応力に対する応力集中係数ασが２．７以下であれば、応力集中の緩和効果が顕著となるので、σ１ｍａｘ／τ０≦２．７の本発明品であれば、従来品に比べ、引張り応力に対する疲労強度を大幅に増大させることが可能である。 From the above analysis results, σ 1max / τ 0 = 3.03 in the conventional product, whereas σ 1max / τ 0 = 2.48 in the product of the present invention. It has been found that the relaxation effect is enhanced. This is presumably because the radius of curvature of the rounded portion 21b1 in the vicinity of the end of the tooth surface 23 is larger than the radius of curvature at the corresponding portion of the conventional product in the product of the present invention. As described above, if the stress concentration coefficient α σ with respect to the tensile stress is 2.7 or less, the stress concentration mitigating effect becomes significant, so that the present invention product of σ 1max / τ 0 ≦ 2.7 can be used. For example, it is possible to greatly increase the fatigue strength against tensile stress compared to conventional products.

また、従来品では、τθｚｍａｘ／τ０＝２．２８であるのに対し、本発明品ではτθｚｍａｘ／τ０＝１．７４となり、従来品より軸方向のせん断応力に対する応力集中の緩和効果も高まることが判明した。上記のとおり、せん断応力に対する応力集中係数ατが２．１以下であれば、応力集中の緩和効果が顕著となるので、τθｚｍａｘ／τ０≦２．１である本発明品は、従来品に比べ、せん断応力に対する疲労強度を大幅に向上させることができる。このように本発明によれば、雄スプライン部Ｓｍで引張応力およびせん断応力の双方に対して高い応力集中緩和効果を得ることができる。従って、動力伝達シャフト２の疲労強度を高めることができる。 Further, in the conventional product, τ θzmax / τ 0 = 2.28, whereas in the product of the present invention, τ θzmax / τ 0 = 1.74, which is a stress relaxation effect on the shear stress in the axial direction as compared with the conventional product. It was also found to increase. As described above, if the stress concentration coefficient α τ with respect to the shear stress is 2.1 or less, the stress concentration relaxation effect becomes significant. Therefore, the product of the present invention in which τ θzmax / τ 0 ≦ 2.1 is a conventional product. Compared to the above, the fatigue strength against shear stress can be greatly improved. Thus, according to the present invention, it is possible to obtain a high stress concentration relaxation effect with respect to both tensile stress and shear stress in the male spline portion Sm. Therefore, the fatigue strength of the power transmission shaft 2 can be increased.

本発明者がさらに解析したところ、図４に示すアール部２１ｂ１の曲率半径の増加率ｄＲ／ｄＬが０．０５≦ｄＲ／ｄＬ≦０．６０であり、かつ拡径部２１ｂの傾斜角θが５°≦θ≦２０°の範囲であれば、σ１ｍａｘ／τ０≦２．７、τθｚｍａｘ／τ０≦２．１を満足できることが判明した。 As a result of further analysis by the present inventor, the rate of increase dR / dL of the radius of curvature of the rounded portion 21b1 shown in FIG. 4 is 0.05 ≦ dR / dL ≦ 0.60, and the inclination angle θ of the enlarged diameter portion 21b is In the range of 5 ° ≦ θ ≦ 20 °, it was found that σ 1max / τ 0 ≦ 2.7 and τ θzmax / τ 0 ≦ 2.1 can be satisfied.

図１４に示すように、従来品では、最大せん断応力τθｚｍａｘが雄側拡径部２１ｂ’の開始端２１ｂ３’の中心線付近で生じる。このように、中心線上で最大せん断応力が発生すると、動力伝達シャフト２が正逆両方向のトルクを伝達する際、正逆何れの回転時にも同じ部位に最大せん断応力が生じるため、それだけ疲労破壊が進展し易くなる。これに対し、本発明品では、最大せん断応力τθｚｍａｘは、図２に示すように、雄側拡径部２１ｂの開始端２１ｂ３よりも反軸端側の双方のアール部２１ｂ１で生じる。そのため、正回転時と逆回転時で最大せん断応力の発生部位が異なり、従って、疲労破壊の進展速度も抑制することが可能となる。以上から、本発明品は、トルクの伝達方向が頻繁に切り替わる用途、例えば車両の前進・後退に応じてトルク伝達方向が反転するような用途に特に好適なものとなる。 As shown in FIG. 14, in the conventional product, the maximum shear stress τ θzmax is generated in the vicinity of the center line of the start end 21b3 ′ of the male-side enlarged portion 21b ′. In this way, when the maximum shear stress is generated on the center line, when the power transmission shaft 2 transmits torque in both forward and reverse directions, the maximum shear stress is generated in the same part during both forward and reverse rotations, so that fatigue failure is caused accordingly. Easy to progress. On the other hand, in the product of the present invention, as shown in FIG. 2, the maximum shear stress τ θzmax is generated in the rounded portions 21b1 on both sides opposite to the start end 21b3 of the male enlarged diameter portion 21b. For this reason, the generation site of the maximum shear stress differs between the forward rotation and the reverse rotation, and therefore the progress rate of fatigue fracture can be suppressed. From the above, the product of the present invention is particularly suitable for an application in which the torque transmission direction is frequently switched, for example, an application in which the torque transmission direction is reversed in accordance with forward / backward movement of the vehicle.

以上に述べたアール部２１ｂ１を有する雄側拡径部２１ｂは、転造加工時に使用する転造ラックに、当該雄側拡径部２１ｂに対応した形状の成形部を形成することにより、雄スプライン部Ｓｍの歯と同時に形成することができる。雄スプライン部をプレス加工で冷間鍛造する場合も同様に、プレス加工用のダイスに雄側拡径部２１ｂの形状に対応した成形部を予め形成することにより、雄スプライン部Ｓｍの歯と同時にアール部２１ｂ１を成形することができる。雌スプライン部Ｓｆは、例えばブローチ加工によって形成される。成形後の雄スプライン部Ｓｍおよび雌スプライン部Ｓｆには、高周波焼入れや浸炭焼入れ等の熱処理が施され、さらに必要に応じてショットピーニングが施される。   The male side enlarged portion 21b having the rounded portion 21b1 described above is formed by forming a molding portion having a shape corresponding to the male side enlarged portion 21b on a rolling rack used during rolling. It can be formed simultaneously with the teeth of the part Sm. Similarly, in the case of cold forging the male spline part by press working, a molding part corresponding to the shape of the male-side enlarged diameter part 21b is formed in advance on the die for press work, thereby simultaneously with the teeth of the male spline part Sm. The rounded portion 21b1 can be formed. The female spline portion Sf is formed by broaching, for example. The male spline portion Sm and the female spline portion Sf after molding are subjected to heat treatment such as induction hardening and carburizing quenching, and further subjected to shot peening as necessary.

以上の対策により、雄スプライン部Ｓｍで引張応力およびせん断応力の双方に対して高い疲労強度が得られる。これと併せて、上記のように、雌スプライン部Ｓｆの雌側拡径部３２ｃの開始端３２ｃ１を、雄側拡径部２１ｂの開始端２１ｂ３よりも反軸端側で歯面２３に接触させているので、せん断応力の集中部を径寸法の大きい雄側拡径部２１ｂの領域中で発生させることができる。そのため、せん断応力の集中度合いを低減することができ、疲労強度を向上させることが可能となる。さらに、雌側拡径部３２ｃの開始端３２ｃ１を、雄側拡径部２１ｂの面と非接触にしていることから、雄スプライン部Ｓｍの疲労強度が不測に低下することはない。   By the above measures, high fatigue strength can be obtained for both tensile stress and shear stress in the male spline portion Sm. At the same time, as described above, the start end 32c1 of the female-side enlarged portion 32c of the female spline portion Sf is brought into contact with the tooth surface 23 on the side opposite to the start end 21b3 of the male-side enlarged portion 21b. Therefore, the concentrated portion of the shear stress can be generated in the region of the male side enlarged portion 21b having a large diameter. Therefore, the degree of concentration of shear stress can be reduced, and the fatigue strength can be improved. Furthermore, since the start end 32c1 of the female-side enlarged portion 32c is not in contact with the surface of the male-side enlarged portion 21b, the fatigue strength of the male spline portion Sm does not drop unexpectedly.

図７に本発明の他の実施形態を示す。この実施形態は、雄スプライン部Ｓｍもしくは雌スプライン部Ｓｆ（図面では雄スプライン部Ｓｍ）のうち、何れか一方の歯に軸心方向に対して捩れ角βを持たせた実施形態であり、嵌合後の両スプライン部Ｓｍ、Ｓｆ間のガタ詰めに有効な手法である。捩れ角βを設けた場合、トルク伝達側の歯面同士の接触圧力が高まり、これに伴って拡径部に集中する引張応力、せん断応力も高くなるため、疲労強度の低下を招く。この観点から、従来品では、捩れ角βは実質１５’が限度とされてきた。これに対し、本発明品では、上記のとおり動力伝達スプラインの疲労強度を大幅に高めることができるので、１５’以上の捩れ角βをとることができ、高いガタ詰め効果を得ることが可能である。   FIG. 7 shows another embodiment of the present invention. This embodiment is an embodiment in which either one of the male spline part Sm or the female spline part Sf (male spline part Sm in the drawing) has a twist angle β with respect to the axial direction. This is an effective method for loosening between the spline portions Sm and Sf after the combination. When the torsion angle β is provided, the contact pressure between the tooth surfaces on the torque transmission side increases, and as a result, the tensile stress and the shear stress concentrated on the enlarged diameter portion also increase, resulting in a decrease in fatigue strength. From this point of view, the conventional product has been limited to a torsion angle β of substantially 15 '. On the other hand, in the present invention product, the fatigue strength of the power transmission spline can be greatly increased as described above, so that a twist angle β of 15 ′ or more can be obtained and a high backlash filling effect can be obtained. is there.

上述の実施形態では、雄スプライン部Ｓｍとして、雄側拡径部２１ｂの円周方向幅を反軸端側で徐々に拡大させたいわゆる「槍形タイプ」を例示しているが、これに限らず、雄側拡径部２１ｂの円周方向幅を一定にしたいわゆる「舟形タイプ」の雄スプライン部Ｓｍに本発明を適用することもできる。この場合も、雄側拡径部２１ｂの円周方向両側にアール部を設け、かつアール部の曲率半径を反軸端側ほど徐々に大きくすることにより、本発明と同様の効果が得られる。   In the above-described embodiment, as the male spline portion Sm, a so-called “saddle type” in which the circumferential width of the male-side diameter-expanded portion 21b is gradually enlarged on the opposite shaft end side is illustrated, but the present invention is not limited thereto. Alternatively, the present invention can also be applied to a so-called “boat type” male spline portion Sm in which the circumferential width of the male-side enlarged diameter portion 21b is constant. Also in this case, the same effects as those of the present invention can be obtained by providing rounded portions on both sides in the circumferential direction of the male side enlarged portion 21b and gradually increasing the radius of curvature of the rounded portion toward the opposite end.

以上の実施形態で示した雄スプライン部Ｓｍは、等速自在継手１の内側継手部材３に結合した動力伝達シャフト２に設けられたものであったが、同様の雄スプライン部Ｓｍは、例えば外側継手部材４と一体又は別体の動力伝達シャフト９（図１参照）に形成することもできる。   Although the male spline part Sm shown in the above embodiment was provided in the power transmission shaft 2 couple | bonded with the inner joint member 3 of the constant velocity universal joint 1, the same male spline part Sm is an outer side, for example It can also be formed in a power transmission shaft 9 (see FIG. 1) that is integral with or separate from the joint member 4.

以上、本発明の実施形態につき説明したが、本発明の特徴は、形状の改良による応力集中の緩和であるから、動力伝達スプラインが上記以外の様々な材質で形成されている場合にも適用が可能である。例えば、焼入れ硬化しない鋼で形成される動力伝達スプラインであってもよい。さらには、非鉄金属、セラミック材料、樹脂材料などで形成される動力伝達スプラインであってもよい。   As described above, the embodiment of the present invention has been described. However, since the feature of the present invention is the relaxation of stress concentration by improving the shape, the present invention can be applied even when the power transmission spline is formed of various materials other than the above. Is possible. For example, a power transmission spline formed of steel that is not hardened by hardening may be used. Furthermore, a power transmission spline formed of a non-ferrous metal, a ceramic material, a resin material, or the like may be used.

動力伝達スプラインを有する等速自在継手の断面図である。It is sectional drawing of the constant velocity universal joint which has a power transmission spline. 雄スプライン部の反軸端側部分（図１の符号Ｘ部）を示す斜視図である。It is a perspective view which shows the other end side part (code | symbol X part of FIG. 1) of a male spline part. 図１の符号Ｘ部を拡大して示す断面図である。It is sectional drawing which expands and shows the code | symbol X part of FIG. （ａ）図は雄スプライン部の反軸端側部分を示す平面図、（ｂ）図は（ａ）図のＹ−Ｙ線断面図である。(A) The figure is a top view which shows the opposite-axis end side part of a male spline part, (b) A figure is the YY sectional view taken on the line (a). （ａ）図は、図４中のＡ−Ａ線断面図、（ｂ）図は同Ｂ−Ｂ線断面図、（ｃ）図は同Ｃ−Ｃ線断面図、（ｄ）図は同Ｄ−Ｄ線断面図である。4A is a sectional view taken along line AA in FIG. 4, FIG. 4B is a sectional view taken along line BB, FIG. 4C is a sectional view taken along line CC, and FIG. FIG. 雄スプライン部の周方向断面図である。It is a circumferential direction sectional view of a male spline part. 捩れ角を有する雄スプライン部の概略構成を示す平面図である。It is a top view which shows schematic structure of the male spline part which has a twist angle. 雄スプライン部の平面図である。It is a top view of a male spline part. 雄スプライン部の平面図である。It is a top view of a male spline part. 雄スプライン部の平面図である。It is a top view of a male spline part. 疲労試験で使用する試験片の化学組成を示す表である。It is a table | surface which shows the chemical composition of the test piece used by a fatigue test. 回転曲げ疲労試験の試験片を示す側面図である。It is a side view which shows the test piece of a rotation bending fatigue test. 上記試験片の切欠き部Ａを拡大した側面図である。It is the side view to which the notch part A of the said test piece was expanded. 切欠き部の寸法と応力集中係数の関係を示す表である。It is a table | surface which shows the relationship between the dimension of a notch part, and a stress concentration factor. 捩り疲労試験の試験片を示す側面図である。It is a side view which shows the test piece of a torsional fatigue test. 上記試験片の切欠き部Ａを拡大した側面図である。It is the side view to which the notch part A of the said test piece was expanded. 切欠き部の寸法と応力集中係数の関係を示す表である。It is a table | surface which shows the relationship between the dimension of a notch part, and a stress concentration factor. 回転曲げ疲労試験で求めた疲労限強度の測定結果を示す図である。It is a figure which shows the measurement result of the fatigue limit strength calculated | required by the rotation bending fatigue test. 捩り疲労試験で求めた１０５回における捩り疲労強度の測定結果を示す図である。Is a graph showing measurement results of the torsional fatigue strength at 10 5 times determined in torsional fatigue test. 従来の雄スプライン部の反軸端側部分を示す斜視図であるIt is a perspective view which shows the anti-shaft end side part of the conventional male spline part. 従来の動力伝達スプラインの断面図である。It is sectional drawing of the conventional power transmission spline. 従来の雄スプライン部の反軸端側部分を示す平面図である。It is a top view which shows the non-axis end side part of the conventional male spline part. 試験片を示す側面図である。It is a side view which shows a test piece. 試験片のインボリュートスプライン緒元を示す表である。It is a table | surface which shows the involute spline specification of a test piece. 両振り捩り疲労試験で得られたＴ／Ｎ線図である。It is a T / N diagram obtained by the double torsional fatigue test. 片振り捩り疲労試験で得られたＴ／Ｎ線図である。FIG. 3 is a T / N diagram obtained in a single swing torsional fatigue test. ＦＥＭ解析モデルを示す斜視図である。It is a perspective view which shows a FEM analysis model. メッシュを付した解析モデルを示す斜視図である。It is a perspective view which shows the analysis model which attached | subjected the mesh. （ａ）図は、メッシュを付した本発明品の主要部分Ｐの斜視図であり、同図（ｂ）が同じく従来品の主要部分Ｐの斜視図である。(A) The figure is a perspective view of the principal part P of this invention goods which attached | subjected the mesh, The figure (b) is a perspective view of the principal part P of a conventional product similarly. 解析モデルの反軸端側の端部の斜視図である。It is a perspective view of the edge part by the side of the non-axis end of an analysis model. 図２０の矢印方向から見た解析モデルの正面図である。It is a front view of the analysis model seen from the arrow direction of FIG. 解析モデルの斜視図である。It is a perspective view of an analysis model. 第１主応力の解析結果を示す図である。It is a figure which shows the analysis result of a 1st principal stress. 軸方向せん断応力の解析結果を示す図である。It is a figure which shows the analysis result of an axial direction shear stress.

符号の説明Explanation of symbols

１ 等速自在継手
２ 動力伝達シャフト（雄側部材）
３ 内側継手部材（雌側部材）
４ 外側継手部材
５ トルク伝達ボール
７ 保持器
２１ 谷部
２１ａ ストレート部
２１ｂ 雄側拡径部
２１ｂ１ アール部
２１ｂ２ 平坦部
２１ｂ３ 開始端
２２ 山部
２３ 歯面
２４ 肩部
２５ 平滑部
３２ 山部
３２ｃ 雌側拡径部
３２ｃ１ 開始端
Ｓｍ 雄スプライン部
Ｓｆ 雌スプライン部 1 Constant velocity universal joint 2 Power transmission shaft (male side member)
3 Inner joint member (female side member)
4 Outer joint member 5 Torque transmission ball 7 Cage 21 Valley portion 21a Straight portion 21b Male side enlarged portion 21b1 Round portion 21b2 Flat portion 21b3 Start end 22 Mountain portion 23 Tooth surface 24 Shoulder portion 25 Smooth portion 32 Mountain portion 32c Female side Expanded diameter portion 32c1 Start end Sm Male spline portion Sf Female spline portion

Claims (7)

雄側部材の外周に設けられ、谷部の軸方向一方側にその外径寸法を徐々に拡径させた雄側拡径部を有する雄スプライン部と、雌側部材の内周に設けられ、山部にその内径寸法を軸方向一方側に向けて徐々に拡径させた雌側拡径部を有する雌スプライン部とを備えた動力伝達スプラインにおいて、
雄スプライン部の雄側拡径部の円周方向両側にアール部を設け、アール部の曲率半径を軸方向一方側に向けて徐々に大きくし、雌スプライン部の雌側拡径部の開始端を、雄側拡径部の開始端よりも軸方向一方側に配置したことを特徴とする動力伝達スプライン。 Provided on the outer periphery of the male side member, provided on the inner periphery of the female side member, a male spline part having a male side enlarged diameter part whose diameter is gradually increased on one side in the axial direction of the valley part, In the power transmission spline provided with a female spline portion having a female-side enlarged diameter portion whose inner diameter dimension is gradually enlarged toward the one side in the axial direction at the mountain portion,
A rounded portion is provided on both sides in the circumferential direction of the male-side enlarged portion of the male spline portion, and the radius of curvature of the rounded portion is gradually increased toward one side in the axial direction to start the female-side enlarged portion of the female spline portion. Is disposed on one side in the axial direction from the start end of the male-side enlarged portion. トルクＴが負荷されたときに、雄スプライン部の雄側拡径部に作用する第１主応力、および軸方向のせん断応力の最大値をそれぞれσ１ｍａｘ、τθｚｍａｘとし、トルクＴ、雄スプライン部の谷部の直径ｄｏ、雄スプライン部の内径ｄｉに対し、１）式で与えられる基準応力τ０とするとき、下記２）式と３）式を同時に満たす請求項１記載の動力伝達スプライン。
τ０＝１６Ｔｄｏ／［π（ｄｏ ４−ｄｉ ４）］ …１）
σ１ｍａｘ≦２．７τｏ …２）
τθｚｍａｘ≦２．１τ０ …３） When the torque T is applied, the first principal stress acting on the male-side expanded portion of the male spline portion and the maximum values of the shear stress in the axial direction are σ 1max and τ θzmax , respectively, and the torque T and the male spline portion 2. The power transmission according to claim 1, wherein the following formula 2) and formula 3) are simultaneously satisfied when the reference stress τ 0 given by formula (1) is used for the diameter d o of the trough portion and the inner diameter d i of the male spline portion: spline.
τ 0 = 16 Td o / [π (d o 4 −d i 4 )]... 1)
σ 1max ≦ 2.7τ o ... 2)
τ θzmax ≦ 2.1τ 0 ... 3) アール部の曲率半径の増加率をｄＲ／ｄＬ、雄側拡径部の軸方向断面の内径端と外径端を結ぶ直線の角度をθとするとき、それぞれの値が
０．０５≦ｄＲ／ｄＬ≦０．６０、
５°≦θ≦２０°
の範囲にある請求項２記載の動力伝達スプライン。 When the rate of increase in the radius of curvature of the rounded portion is dR / dL and the angle of the straight line connecting the inner diameter end and the outer diameter end of the axial cross section of the male-side enlarged diameter portion is θ, each value is 0.05 ≦ dR / dL ≦ 0.60,
5 ° ≦ θ ≦ 20 °
The power transmission spline according to claim 2 in the range of 雌側拡径部の開始端を、雄側拡径部と非接触にした請求項１〜３何れか記載の動力伝達スプライン。   The power transmission spline according to any one of claims 1 to 3, wherein a starting end of the female side enlarged portion is not in contact with the male side enlarged portion. 雄スプライン部または雌スプライン部の一方もしくは双方に焼入れ硬化処理を施した請求項１〜４何れか記載の動力伝達スプライン。   The power transmission spline according to claim 1, wherein one or both of the male spline part and the female spline part is subjected to quench hardening. 焼入れ硬化処理を高周波焼入れで行った請求項５記載の動力伝達スプライン。   The power transmission spline according to claim 5, wherein the quench hardening treatment is performed by induction hardening. 焼入れ硬化処理を浸炭焼入れで行った請求項５記載の動力伝達スプライン。   The power transmission spline according to claim 5, wherein the quench hardening process is performed by carburizing and quenching.
JP2006278853A 2006-10-12 2006-10-12 Power transmission spline Withdrawn JP2008095845A (en)

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102395805A (en) * 2009-04-16 2012-03-28 本田技研工业株式会社 Tripod constant velocity joint, and method and device for assembling same
WO2014156640A1 (en) * 2013-03-25 2014-10-02 Ntn株式会社 Motive-power-transmitting shaft and spline-processing method
CN105903867A (en) * 2015-02-19 2016-08-31 加特可株式会社 Spline shaft and manufacturing method thereof

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102395805A (en) * 2009-04-16 2012-03-28 本田技研工业株式会社 Tripod constant velocity joint, and method and device for assembling same
WO2014156640A1 (en) * 2013-03-25 2014-10-02 Ntn株式会社 Motive-power-transmitting shaft and spline-processing method
JPWO2014156640A1 (en) * 2013-03-25 2017-02-16 Ntn株式会社 Power transmission shaft and spline processing method
US10352365B2 (en) 2013-03-25 2019-07-16 Ntn Corporation Power transmission shaft and spline-processing method
CN105903867A (en) * 2015-02-19 2016-08-31 加特可株式会社 Spline shaft and manufacturing method thereof
CN105903867B (en) * 2015-02-19 2018-04-03 加特可株式会社 Splined shaft and its manufacture method

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