JP2006077963A - Power transmission structure - Google Patents

Power transmission structure Download PDF

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JP2006077963A
JP2006077963A JP2004265782A JP2004265782A JP2006077963A JP 2006077963 A JP2006077963 A JP 2006077963A JP 2004265782 A JP2004265782 A JP 2004265782A JP 2004265782 A JP2004265782 A JP 2004265782A JP 2006077963 A JP2006077963 A JP 2006077963A
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shaft
spline
inner member
power transmission
universal joint
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JP2004265782A
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Katsuhiro Sakurai
勝弘 櫻井
Akira Nakagawa
亮 中川
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NTN Corp
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NTN Corp
NTN Toyo Bearing Co Ltd
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Abstract

<P>PROBLEM TO BE SOLVED: To relax stress concentration to a root part of a spline. <P>SOLUTION: A spline 1b formed in the outer periphery of the end part of a shaft 1 is fitted to a spline 3d formed in the inner periphery of an inner member 3 of a fixed constant speed universal joint, and further the shaft 1 and the inner member 3 are welded to each other on the shaft end face 5 of the shaft 1 to be united into one body. The shaft 1 and the inner member 3 are constrained in the axial direction and in the rotating direction by the welded part 6. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

本発明は、自動車等の動力伝達系に用いられる動力伝達構造に関し、特に等速自在継手を使用した動力伝達構造に関する。   The present invention relates to a power transmission structure used in a power transmission system of an automobile or the like, and more particularly to a power transmission structure using a constant velocity universal joint.

例えば、自動車の動力伝達系において、減速装置（ディファレンシャル）から駆動輪に動力を伝達する動力伝達シャフトは、ドライブシャフト（駆動軸）と呼ばれることがある。特にＦＦ車に使用されるドライブシャフトでは、前輪操舵時に大きな作動角と等速性が要求され、また、懸架装置との関係で軸方向の変位を吸収する機能が要求されるので、その一端部をダブルオフセット型等速自在継手やトリポード型等速自在継手等の摺動型等速自在継手を介して減速装置側に連結し、その他端部をバーフィールド型等速自在継手（ゼッパジョイントと呼ばれることもある。）等の固定側等速自在継手を介して駆動輪側に連結する機構が多く採用されている。   For example, in a power transmission system of an automobile, a power transmission shaft that transmits power from a speed reducer (differential) to drive wheels may be called a drive shaft (drive shaft). In particular, drive shafts used in front-wheel drive vehicles require a large operating angle and constant velocity during front wheel steering, and also require a function to absorb axial displacement in relation to the suspension system. Are connected to the speed reducer via a sliding type constant velocity universal joint such as a double offset type constant velocity universal joint or a tripod type constant velocity universal joint, and the other end is connected to a barfield type constant velocity universal joint (Zepper joint). In many cases, a mechanism that is connected to the drive wheel side via a fixed-side constant velocity universal joint is used.

図８は、中空状の動力伝達シャフト１と、動力伝達シャフト１の一端部に連結された摺動型等速自在継手２と、動力伝達シャフト１の他端部に連結された固定型等速自在継手３とを備えた自動車の動力伝達機構を示している。   FIG. 8 shows a hollow power transmission shaft 1, a sliding type constant velocity universal joint 2 connected to one end of the power transmission shaft 1, and a fixed type constant speed connected to the other end of the power transmission shaft 1. The power transmission mechanism of the motor vehicle provided with the universal joint 3 is shown.

この動力伝達機構において、摺動型等速自在継手２は減速装置（ディファレンシャル）に連結され、固定型等速自在継手３は駆動輪側に連結される。動力伝達シャフト１の一端部は摺動型等速自在継手２の内方部材（トリポード部材）２ａに連結され、摺動型等速自在継手２の外方部材２ｂの端部外周と動力伝達シャフト１の外周にブーツ２ｃが固定される。   In this power transmission mechanism, the sliding type constant velocity universal joint 2 is connected to a reduction gear (differential), and the fixed type constant velocity universal joint 3 is connected to the drive wheel side. One end portion of the power transmission shaft 1 is connected to an inner member (tripod member) 2a of the sliding type constant velocity universal joint 2, and the outer periphery of the end portion of the outer member 2b of the sliding type constant velocity universal joint 2 and the power transmission shaft. A boot 2 c is fixed to the outer periphery of 1.

また、動力伝達シャフト１の他端部は固定型等速自在継手３の内方部材３ａに連結され、固定型等速自在継手３の外方部材３ｂの端部外周と動力伝達シャフト１の外周にブーツ３ｃが固定される。   The other end of the power transmission shaft 1 is connected to the inner member 3 a of the fixed type constant velocity universal joint 3, and the outer periphery of the outer member 3 b of the fixed type constant velocity universal joint 3 and the outer periphery of the power transmission shaft 1. The boot 3c is fixed to the front.

シャフト１の他端部と固定型等速自在継手３の内方部材３ａとの連結は、例えば、図９に拡大して示すように、シャフト１の他端部外周に形成されたスプライン１ｂと、内方部材３ａの内周に形成されたスプライン３ｄとを相互に嵌合すると共に、シャフト１の一端部の軸端側に形成された止め輪溝１ａに止め輪４を装着し、シャフト１と内方部材３ａとの相対移動を軸方向に規制することにより行われる。同様に、シャフト１の一端部と摺動型等速自在継手２の内方部材２ａとの連結は、シャフト１の一端部外周に形成されたスプライン１ｂと、内方部材２ａの内周に形成されたスプライン２ｄとを相互に嵌合すると共に、シャフト１の一端部の軸端側に形成した止め輪溝１ａに止め輪を装着し、シャフト１と内方部材２ａとの相対移動を軸方向に規制することにより行われる。   The connection between the other end of the shaft 1 and the inner member 3a of the fixed type constant velocity universal joint 3 is, for example, an enlarged view of the other end of the shaft 1 as shown in FIG. The spline 3d formed on the inner periphery of the inner member 3a is mutually fitted, and a retaining ring 4 is mounted in a retaining ring groove 1a formed on the shaft end side of one end of the shaft 1, so that the shaft 1 And the inner member 3a are controlled by restricting relative movement in the axial direction. Similarly, the connection between one end portion of the shaft 1 and the inner member 2a of the sliding type constant velocity universal joint 2 is formed on the outer periphery of the one end portion of the shaft 1 and the inner periphery of the inner member 2a. The splines 2d are fitted to each other, and a retaining ring is attached to a retaining ring groove 1a formed on the shaft end side of one end of the shaft 1, so that the relative movement between the shaft 1 and the inner member 2a is axially performed. It is done by restricting to.

また、下記の特許文献１では、スプライン嵌合に際し、シャフト側のスプラインに捩れ角を付与し、これを継手内方部材のスプラインに圧入することにより、スプライン嵌合部のガタを抑えると共に、シャフトのスプラインの反軸端側において、トルク負荷時の内方部材とシャフトのスプラインの歯面にかかる応力を圧入による応力により打ち消して最大応力を軽減している。
実公平６−３３２２０号公報 In addition, in the following Patent Document 1, when a spline is fitted, a twist angle is given to the spline on the shaft side, and this is press-fitted into the spline of the joint inner member. At the opposite end of the spline, the stress applied to the inner surface of the inner member and the shaft spline at the time of torque load is canceled out by the stress caused by the press-fitting to reduce the maximum stress.
Japanese Utility Model Publication No. 6-33220

従来のスプライン嵌合構造では、シャフトに捩りトルクが加わると、捩りの支点がシャフトのスプラインの根元部になるため、スプラインの根元部に応力が集中する傾向がある。特に、特許文献１のように、スプライン嵌合部のガタを抑えるために、シャフト側のスプラインに捩れ角を付与した構造では、スプラインの根元部への応力集中がさらに顕著になる。   In the conventional spline fitting structure, when torsional torque is applied to the shaft, the torsion fulcrum becomes the root part of the spline of the shaft, and therefore stress tends to concentrate on the root part of the spline. In particular, as in Patent Document 1, in a structure in which a twist angle is given to the spline on the shaft side in order to suppress the play of the spline fitting portion, the stress concentration on the root portion of the spline becomes more remarkable.

本発明の課題は、スプラインの根元部への応力集中を緩和し、シャフトと継手内部方部材の強度を高めた動力伝達構造を提供することである。   The subject of this invention is providing the power transmission structure which relieve | moderated the stress concentration to the root part of a spline, and raised the intensity | strength of the shaft and the joint internal member.

本発明の他の課題は、従来構造と同等以上の強度を確保しつつ、シャフトと継手内部方部材のサイズダウンを図り、動力伝達構造の軽量コンパクト化を図ることである。 Another object of the present invention is to reduce the size of the shaft and the joint inner member while ensuring a strength equal to or higher than that of the conventional structure, and to reduce the weight and size of the power transmission structure.

上記課題を解決するため、本発明は、等速自在継手の内方部材の内周に形成したスプラインと、シャフトの端部外周に形成したスプラインとを互いに嵌合させた動力伝達構造において、内方部材とシャフトとを軸方向及び回転方向に相互に拘束する拘束部を設け、シャフトに捩りトルクが負荷されたときの捩りの支点が、シャフトのスプラインの根元部と拘束部になるようにした。   In order to solve the above problems, the present invention provides a power transmission structure in which a spline formed on the inner periphery of an inner member of a constant velocity universal joint and a spline formed on an outer periphery of an end of a shaft are fitted to each other. A constraining part that constrains the side member and the shaft in the axial direction and the rotational direction is provided so that the torsion fulcrum when the torsional torque is applied to the shaft becomes the root part of the shaft spline and the constraining part. .

上記構成において、拘束部は、シャフトの軸端と内方部材とを相互に固着することにより構成することができる。ここでの固着には、溶着、圧着、接着等が含まれる。   In the above configuration, the restraining portion can be configured by fixing the shaft end of the shaft and the inner member to each other. The fixing here includes welding, pressure bonding, adhesion, and the like.

また、上記構成において、拘束部は、シャフトと内方部材とを摩擦力により拘束するものとすることができる。   Further, in the above configuration, the restraining portion can restrain the shaft and the inward member with a frictional force.

本発明によれば、シャフトに捩りトルクが負荷されたときの捩りの支点が、シャフトのスプラインの根元部と拘束部になるので、スプラインの根元部の応力集中が従来構造に比べて緩和される。これにより、シャフトと継手内方部材の強度が向上する。   According to the present invention, since the torsion fulcrum when the torsional torque is applied to the shaft becomes the root portion and the restraint portion of the shaft spline, the stress concentration at the root portion of the spline is alleviated compared to the conventional structure. . Thereby, the intensity | strength of a shaft and a joint inner member improves.

また、従来構造と同等以上の強度を確保しつつ、シャフトと継手内部方部材のサイズダウンを図り、動力伝達構造の軽量コンパクト化を図ることができる。 In addition, the shaft and the joint inner member can be reduced in size while ensuring a strength equal to or higher than that of the conventional structure, and the power transmission structure can be reduced in weight and size.

以下、本発明の実施の形態を図面に基づいて説明する。尚、以下で説明する実施の形態は、図８に示す自動車の動力伝達機構において、シャフト１の他端部と固定型等速自在継手３の内方部材３ａとの間に設けられる動力伝達構造に関するものであるが、シャフト１の一端部と摺動型等速自在継手２の内方部材２ａとの間に設けられる動力伝達構造にも同様に適用することができる。また、図８、９に示す従来構造の部材又は部分については同一符号を付与してその詳細な説明を省略する。   Hereinafter, embodiments of the present invention will be described with reference to the drawings. The embodiment described below is a power transmission structure provided between the other end of the shaft 1 and the inner member 3a of the fixed type constant velocity universal joint 3 in the power transmission mechanism of the automobile shown in FIG. However, the invention can be similarly applied to a power transmission structure provided between one end of the shaft 1 and the inner member 2a of the sliding type constant velocity universal joint 2. Further, members or portions of the conventional structure shown in FIGS. 8 and 9 are given the same reference numerals and detailed description thereof is omitted.

図１に示す実施の形態１では、固定型等速自在継手３の内方部材３ａの内周に形成されたスプライン３ｄに、シャフト１の端部外周に形成されたスプライン１ｂが嵌合され、さらに、シャフト１と内方部材３ａとが、シャフト１の軸端面５の側で相互に溶着（溶接）されて一体化されている。シャフト１と内方部材３ａとは、溶着部６により軸方向及び回転方向に相互に拘束される。したがって、実施の形態１では、溶着部６が拘束部になる。   In Embodiment 1 shown in FIG. 1, a spline 1b formed on the outer periphery of the end of the shaft 1 is fitted to a spline 3d formed on the inner periphery of the inner member 3a of the fixed type constant velocity universal joint 3, Further, the shaft 1 and the inner member 3a are welded (welded) to each other on the shaft end surface 5 side of the shaft 1 and integrated. The shaft 1 and the inner member 3a are mutually restrained in the axial direction and the rotational direction by the welded portion 6. Therefore, in Embodiment 1, the welding part 6 becomes a restraint part.

上記のように、シャフト１と内方部材３ａとが、溶着部６によりシャフト１の軸端面５の側で相互に拘束されるので、シャフト１に捩りトルクが負荷されたとき、捩りの支点は、シャフト１のスプライン１ｂの根元部Ａと溶着部６の２箇所になる。そのため、スプライン１ｂの根元部Ａへの応力集中が緩和される。 As described above, the shaft 1 and the inner member 3a are mutually restrained on the shaft end surface 5 side of the shaft 1 by the welded portion 6, and therefore when the torsional torque is applied to the shaft 1, the torsion fulcrum is The root portion A of the spline 1b of the shaft 1 and the welded portion 6 are provided. Therefore, the stress concentration on the root portion A of the spline 1b is alleviated.

シャフト１のスプライン１ｂにかかる応力状態を見てみると、図２に示すように、図９に示す従来構造（実線）では、スプライン１ｂの根元部Ａと軸端部Ｂとで応力差が大きく、根元部Ａへの応力集中が認められたが、実施の形態１（本発明：一点鎖線）では、根元部Ａでの応力が減少する一方、軸端部Ｂでの応力が増大し、従来構造に比べて、根元部Ａと軸端部Ｂとで応力が均一化され、根元部Ａへの応力集中が緩和されていた。これは、上記のように、捩りの支点が、シャフト１のスプライン１ｂの根元部Ａと溶着部６の２箇所に増えたことにより、シャフト１にかかる応力が分散されたためである。   When the stress state applied to the spline 1b of the shaft 1 is seen, as shown in FIG. 2, in the conventional structure (solid line) shown in FIG. 9, there is a large stress difference between the root portion A and the shaft end portion B of the spline 1b. In the first embodiment (the present invention: one-dot chain line), the stress at the root portion A decreases while the stress at the shaft end portion B increases. Compared with the structure, the stress was made uniform between the root portion A and the shaft end portion B, and the stress concentration on the root portion A was alleviated. This is because, as described above, the stress applied to the shaft 1 is dispersed because the fulcrum of torsion has increased to two locations, that is, the root portion A of the spline 1b of the shaft 1 and the welded portion 6.

上記のように、シャフト１のスプライン１ｂの根元部Ａへの応力集中が緩和される結果、シャフト１の強度は向上する。また、内方部材３ａのスプライン３ｄについても根元部Ａへの応力集中が緩和される結果、内方部材３ａの強度は向上する。また、シャフト１と内方部材３ａの強度を従来品と同等以上に確保した場合、シャフト１と内方部材３ａをサイズダウンして、軽量コンパクト化を図ることができる。   As described above, the stress concentration on the root portion A of the spline 1b of the shaft 1 is alleviated. As a result, the strength of the shaft 1 is improved. Further, the stress concentration on the root portion A of the spline 3d of the inner member 3a is alleviated, so that the strength of the inner member 3a is improved. Further, when the strength of the shaft 1 and the inner member 3a is ensured to be equal to or higher than that of the conventional product, the size of the shaft 1 and the inner member 3a can be reduced to achieve a lighter and more compact size.

次に、本発明の実施の形態２を図３、図４を用いて説明する。   Next, a second embodiment of the present invention will be described with reference to FIGS.

図３に示す実施の形態２では、固定型等速自在継手３の内方部材３ａの内周に形成されたスプライン３ｄに、シャフト１の端部外周に形成されたスプライン１ｂが嵌合され、さらに、シャフト１と内方部材３ａとが、シャフト１の軸端面７の側に配置された端面部材８によって相互に固定されている。すなわち、シャフト１の軸端面７と内方部材３の一方の端面に端面部材８をあてがい、端面部材８をシャフト１の軸端面７に螺子９で締め付けて、内方部材３ａの他方の端部をシャフト１の肩部１ｄに押し当てることにより、内方部材３ａを端面部材８とシャフト１の肩部１ｄとで軸方向に挟持固定している。これにより、シャフト１と内方部材３ａとは、端面部材８と内方部材３の端面との当接部Ｃ１、内方部材３ａの端部とシャフト１の肩部１ｄとの当接部Ｃ２、及び、螺子９と端面部材８との当接部Ｃ３に発生する摩擦力により軸方向及び回転方向に相互に拘束される。したがって、実施の形態２では、当接部Ｃ１、Ｃ２、Ｃ３が拘束部になる。   In Embodiment 2 shown in FIG. 3, a spline 1b formed on the outer periphery of the end of the shaft 1 is fitted to a spline 3d formed on the inner periphery of the inner member 3a of the fixed type constant velocity universal joint 3. Further, the shaft 1 and the inner member 3 a are fixed to each other by an end surface member 8 disposed on the shaft end surface 7 side of the shaft 1. That is, the end surface member 8 is applied to the shaft end surface 7 of the shaft 1 and one end surface of the inner member 3, and the end surface member 8 is fastened to the shaft end surface 7 of the shaft 1 with the screw 9, and the other end portion of the inner member 3 a. Is pressed against the shoulder 1d of the shaft 1 so that the inner member 3a is clamped and fixed in the axial direction by the end face member 8 and the shoulder 1d of the shaft 1. Thereby, the shaft 1 and the inner member 3a are in contact with the end face member 8 between the end face member 8 and the end face of the inner member 3, and the contact part C2 between the end portion of the inner member 3a and the shoulder 1d of the shaft 1. And, they are mutually restrained in the axial direction and the rotational direction by the frictional force generated at the contact portion C3 between the screw 9 and the end face member 8. Accordingly, in the second embodiment, the contact portions C1, C2, and C3 are the restraining portions.

上記のように、シャフト１と内方部材３ａとが、当接部Ｃ１、Ｃ２、Ｃ３によりシャフト１のスプライン１ｂを挟んで軸方向両側で相互に拘束されるので、シャフト１に捩りトルクが負荷されたとき、捩りの支点は、シャフト１のスプライン１ｂの根元部Ａと当接部Ｃ１、Ｃ２、Ｃ３の４箇所になる。そのため、スプライン１ｂの根元部Ａへの応力集中が緩和される。 As described above, the shaft 1 and the inner member 3a are mutually restrained on both sides in the axial direction with the splines 1b of the shaft 1 sandwiched between the contact portions C1, C2, and C3. When this is done, there are four fulcrum points for twisting: the root portion A of the spline 1b of the shaft 1 and the contact portions C1, C2, and C3. Therefore, the stress concentration on the root portion A of the spline 1b is alleviated.

実施の形態２について、シャフト１のスプライン１ｂにかかる応力状態を見てみると、図４に示すように、図９に示す従来構造（実線）に比べ、実施の形態２（本発明：一点鎖線）では、根元部Ａから軸端部Ｂにかけて応力が均一に減少していた。その結果、根元部Ａへの応力集中が従来構造に比べて緩和されていた。これは、上記のように、捩りの支点が、シャフト１のスプライン１ｂの根元部Ａと当接部Ｃ１、Ｃ２、Ｃ３の４箇所に増えたことにより、シャフト１にかかる応力が分散されたためである。 When the stress state applied to the spline 1b of the shaft 1 in the second embodiment is seen, as shown in FIG. 4, the second embodiment (the present invention: one-dot chain line) is compared with the conventional structure (solid line) shown in FIG. ), The stress was uniformly reduced from the root A to the shaft end B. As a result, the stress concentration on the root portion A was relaxed compared to the conventional structure. This is because the stress applied to the shaft 1 is dispersed because the fulcrum of torsion has increased to four locations of the root portion A of the spline 1b of the shaft 1 and the contact portions C1, C2, and C3 as described above. is there.

図５は、本発明の実施の形態３を示している。この実施の形態３が、上記の実施の形態２と異なる点は、シャフト１の肩部１ｄを大径にして、内方部材３ａとの接触面積を大きくした点にある。これにより、内方部材３ａの端部とシャフト１の肩部１ｄとの当接部Ｃ２の摩擦力が増大し、スプライン１ｂの根元部Ａへの応力集中がより一層緩和される。   FIG. 5 shows a third embodiment of the present invention. The third embodiment is different from the second embodiment in that the shoulder 1d of the shaft 1 has a large diameter and the contact area with the inner member 3a is increased. As a result, the frictional force of the contact portion C2 between the end portion of the inner member 3a and the shoulder portion 1d of the shaft 1 increases, and the stress concentration on the root portion A of the spline 1b is further alleviated.

図６は、本発明の実施の形態４を示している。この実施の形態４では、シャフト１の軸端面７に形成した圧入部１０に端面部材１１を圧入して、内方部材３ａの他方の端部をシャフト１の肩部１ｄに押し当てることにより、内方部材３ａを端面部材１１とシャフト１の肩部１ｄとで軸方向に挟持固定している。これにより、シャフト１と内方部材３ａとは、端面部材１１と内方部材３ａの端面との当接部Ｃ１、内方部材３ａの端部とシャフト１の肩部１ｄとの当接部Ｃ２に発生する摩擦力により軸方向及び回転方向に相互に拘束される。この実施の形態４では、捩りの支点は、シャフト１のスプライン１ｂの根元部Ａと当接部Ｃ１、Ｃ２の３箇所になり、上述した実施の形態２、３に対して捩りの支点が１箇所少なくなる。   FIG. 6 shows a fourth embodiment of the present invention. In the fourth embodiment, the end surface member 11 is press-fitted into the press-fit portion 10 formed on the shaft end surface 7 of the shaft 1, and the other end portion of the inner member 3a is pressed against the shoulder portion 1d of the shaft 1, The inner member 3a is clamped and fixed in the axial direction by the end face member 11 and the shoulder 1d of the shaft 1. Thereby, the shaft 1 and the inner member 3a are in contact with the end face member 11 and the end face of the inner member 3a, and the contact part C2 between the end of the inner member 3a and the shoulder 1d of the shaft 1 Are mutually restrained in the axial direction and the rotational direction by the frictional force generated in In the fourth embodiment, there are three twisting fulcrums, that is, the root portion A of the spline 1b of the shaft 1 and the contact portions C1 and C2, and the twisting fulcrum is 1 in the second and third embodiments. There are fewer places.

図７は、本発明の実施の形態５を示している。この実施の形態５では、端面部材１２に螺子部１３を一体に設け、端面部材１２をシャフト１の軸端面７に締め付けて、内方部材３ａの他方の端部をシャフト１の肩部１ｄに押し当てることにより、内方部材３ａを端面部材１２とシャフト１の肩部１ｄとで軸方向に挟持固定している。この実施の形態５でも、捩りの支点は、シャフト１のスプライン１ｂの根元部Ａと当接部Ｃ１、Ｃ２の３箇所になり、上述した実施の形態２、３に対して捩りの支点が１箇所少なくなる。   FIG. 7 shows a fifth embodiment of the present invention. In the fifth embodiment, the end surface member 12 is integrally provided with the screw portion 13, the end surface member 12 is fastened to the shaft end surface 7 of the shaft 1, and the other end portion of the inner member 3 a is connected to the shoulder portion 1 d of the shaft 1. By pressing, the inner member 3a is clamped and fixed in the axial direction by the end face member 12 and the shoulder portion 1d of the shaft 1. Also in the fifth embodiment, there are three torsion fulcrums, that is, the root portion A of the spline 1b of the shaft 1 and the contact portions C1 and C2, and the torsion fulcrum is 1 in comparison with the second and third embodiments described above. There are fewer places.

実施の形態１を示す一部断面図である。1 is a partial cross-sectional view showing a first embodiment. 図１のスプライン部にかかる応力状態を示す図である。It is a figure which shows the stress state concerning a spline part of FIG. 実施の形態２を示す一部断面図である。5 is a partial cross-sectional view showing a second embodiment. FIG. 図３のスプライン部にかかる応力状態を示す特性図である。It is a characteristic view which shows the stress state concerning the spline part of FIG. 実施の形態３を示す一部断面図である。6 is a partial cross-sectional view showing a third embodiment. FIG. 実施の形態４を示す一部断面図である。FIG. 6 is a partial cross-sectional view showing a fourth embodiment. 実施の形態５を示す一部断面図である。FIG. 10 is a partial cross-sectional view showing a fifth embodiment. 自動車の動力伝達系を示す図である。It is a figure which shows the power transmission system of a motor vehicle. 従来の動力伝達構造を示す一部断面図である。It is a partial sectional view showing a conventional power transmission structure.

符号の説明Explanation of symbols

１ シャフト
３ａ 内方部材
１ｂ，３ｄ スプライン
６ 溶着部（拘束部）
７ 軸端面
Ｃ１、Ｃ２、Ｃ３ 当接部（拘束部）
Ａ スプラインの根元部 DESCRIPTION OF SYMBOLS 1 Shaft 3a Inner member 1b, 3d Spline 6 Welding part (restraint part)
7 Shaft end faces C1, C2, C3 Contact part (restraint part)
A Spline root

Claims (3)

等速自在継手の内方部材の内周に形成したスプラインと、シャフトの端部外周に形成したスプラインとを互いに嵌合させた動力伝達構造において、
前記内方部材とシャフトとを軸方向及び回転方向に相互に拘束する拘束部を設け、
前記シャフトに捩りトルクが負荷されたときの捩りの支点が、前記シャフトのスプラインの根元部と前記拘束部になるようにしたことを特徴とする動力伝達構造。 In the power transmission structure in which the spline formed on the inner periphery of the inner member of the constant velocity universal joint and the spline formed on the outer periphery of the end of the shaft are fitted to each other,
Providing a restraining portion that restrains the inner member and the shaft in the axial direction and the rotational direction;
A power transmission structure characterized in that a torsion fulcrum when a torsional torque is applied to the shaft is a root portion of the spline of the shaft and the restraint portion. 前記拘束部は、前記シャフトの軸端と前記内方部材とを相互に固着することにより構成されていることを特徴とする請求項１記載の動力伝達構造。   The power transmission structure according to claim 1, wherein the restraining portion is configured by fixing the shaft end of the shaft and the inner member to each other. 前記拘束部は、前記シャフトと前記内方部材とを摩擦力により拘束するものであることを特徴とする請求項１記載の動力伝達構造。

The power transmission structure according to claim 1, wherein the restraining portion restrains the shaft and the inward member by a frictional force.

JP2004265782A 2004-09-13 2004-09-13 Power transmission structure Withdrawn JP2006077963A (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2463176A1 (en) * 2010-12-07 2012-06-13 JTEKT Corporation Shaft-and-yoke coupling structure and vehicle steering system

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2463176A1 (en) * 2010-12-07 2012-06-13 JTEKT Corporation Shaft-and-yoke coupling structure and vehicle steering system
CN102530052A (en) * 2010-12-07 2012-07-04 株式会社捷太格特 Shaft-and-yoke coupling structure and vehicle steering system
US8500564B2 (en) 2010-12-07 2013-08-06 Jtekt Corporation Shaft-and-yoke coupling structure and vehicle steering system

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