JP2005214395A - Uniform motion universal joint for steering device, and steering device - Google Patents
Uniform motion universal joint for steering device, and steering device Download PDFInfo
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- JP2005214395A JP2005214395A JP2004025805A JP2004025805A JP2005214395A JP 2005214395 A JP2005214395 A JP 2005214395A JP 2004025805 A JP2004025805 A JP 2004025805A JP 2004025805 A JP2004025805 A JP 2004025805A JP 2005214395 A JP2005214395 A JP 2005214395A
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- boot
- universal joint
- constant velocity
- velocity universal
- steering device
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62D—MOTOR VEHICLES; TRAILERS
- B62D1/00—Steering controls, i.e. means for initiating a change of direction of the vehicle
- B62D1/02—Steering controls, i.e. means for initiating a change of direction of the vehicle vehicle-mounted
- B62D1/16—Steering columns
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62D—MOTOR VEHICLES; TRAILERS
- B62D1/00—Steering controls, i.e. means for initiating a change of direction of the vehicle
- B62D1/02—Steering controls, i.e. means for initiating a change of direction of the vehicle vehicle-mounted
- B62D1/16—Steering columns
- B62D1/20—Connecting steering column to steering gear
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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
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/84—Shrouds, e.g. casings, covers; Sealing means specially adapted therefor
- F16D3/843—Shrouds, e.g. casings, covers; Sealing means specially adapted therefor enclosed covers
- F16D3/845—Shrouds, e.g. casings, covers; Sealing means specially adapted therefor enclosed covers allowing relative movement of joint parts due to the flexing of the cover
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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
- 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
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- General Engineering & Computer Science (AREA)
- Sealing Devices (AREA)
- Diaphragms And Bellows (AREA)
- Steering Controls (AREA)
- Steering-Linkage Mechanisms And Four-Wheel Steering (AREA)
Abstract
Description
本発明は自動車のステアリング装置用等速自在継手および同継手を用いたステアリング装置に関する。 The present invention relates to a constant velocity universal joint for a steering device of an automobile and a steering device using the joint.
自動車のステアリング用軸継手として固定型等速自在継手を用いれば、任意の作動角で等速性を確保することができるので、車両の設計自由度が増す利点がある。 If a fixed type constant velocity universal joint is used as a steering shaft joint of an automobile, constant velocity can be ensured at an arbitrary operating angle, so that there is an advantage that the degree of freedom in designing the vehicle is increased.
この固定型等速自在継手は、球状内面に複数の曲線状のトラック溝を有する外側継手部材と、球状外面に複数の曲線状のトラック溝を有する内側継手部材と、外側継手部材および内側継手部材のトラック溝間に組み込まれたボールと、ボールを保持する保持器とで構成される。 The fixed type constant velocity universal joint includes an outer joint member having a plurality of curved track grooves on a spherical inner surface, an inner joint member having a plurality of curved track grooves on a spherical outer surface, and an outer joint member and an inner joint member. It is comprised with the ball | bowl incorporated between these track grooves, and the holder | retainer which hold | maintains a ball | bowl.
この等速自在継手では、駆動側と従動側で連結すべき二軸のうち、一方の軸部材が内側継手部材に連結され、他方の軸部材が外側継手部材に連結されて前述の二軸が作動角をとっても等速で回転トルクを伝達し得る構造を具備する。 In this constant velocity universal joint, of the two shafts to be connected on the driving side and the driven side, one shaft member is connected to the inner joint member, the other shaft member is connected to the outer joint member, and the two shafts described above are connected. It has a structure capable of transmitting rotational torque at a constant speed even when the operating angle is taken.
この種の等速自在継手では、潤滑剤としてグリースが封入されており、そのグリースが外部へ漏洩したり、あるいは、外部から継手内部へ水やダスト等の異物が侵入したりすることを防止する目的から、等速自在継手の外側継手部材と軸部材との間に密封用ブーツを装着するのが一般的である。 In this type of constant velocity universal joint, grease is sealed as a lubricant to prevent the grease from leaking to the outside or foreign materials such as water and dust from entering the inside of the joint from the outside. For the purpose, a sealing boot is generally mounted between the outer joint member of the constant velocity universal joint and the shaft member.
このブーツは、等速自在継手の外側継手部材の外周に嵌着される大径部と、内側継手部材に連結された軸部材の外周に嵌着される小径部と、前記大径部と小径部の間の蛇腹状のベロー部からなる。ブーツの大径部と小径部とは、円筒状のブーツ取り付け部位として、等速自在継手および軸部材の外周に嵌着された後、金属製のブーツバンドで締め付けられて気密的に固定される（例えば、特許文献１，２参照）。
ブーツ材料としては、従来、クロロプレンゴムが広く使用されている。ブーツ材料には耐屈曲性、耐水性、耐候性、耐熱性、耐寒性、耐油性等が要求される。動力伝達用のドライブシャフトに使用する等速自在継手の場合、トルクが負荷されていない状態の回転抵抗値が多少大きくても駆動力と比較して微小であり問題とならないが、自動車のステアリング装置用等速自在継手の場合、回転抵抗を低く抑える必要がある。回転抵抗には等速自在継手の内部抵抗のほか、ブーツの硬さが大きく影響する。特に低温時、起動トルクや回転抵抗が増大し、ステアリング操作性の低下につながるおそれがある。 Conventionally, chloroprene rubber has been widely used as a boot material. The boot material is required to have bending resistance, water resistance, weather resistance, heat resistance, cold resistance, oil resistance, and the like. In the case of a constant velocity universal joint used for a drive shaft for power transmission, even if the rotational resistance value with no torque applied is somewhat large, it is small compared to the driving force, but this does not cause a problem. For constant velocity universal joints, it is necessary to keep the rotational resistance low. In addition to the internal resistance of the constant velocity universal joint, the hardness of the boot greatly affects the rotational resistance. Particularly at low temperatures, the starting torque and rotational resistance increase, which may lead to a decrease in steering operability.
そこで、本発明の目的は、ブーツの材料を改良することにより、ステアリング装置用等速自在継手の回転抵抗を低下させることにある。 Therefore, an object of the present invention is to reduce the rotational resistance of the constant velocity universal joint for a steering device by improving the material of the boot.
本発明のステアリング装置用等速自在継手は、等速自在継手内部からのグリース漏洩や等速自在継手内部への異物侵入を防止するためのブーツを具備した等速自在継手であって、前記ブーツの材料の硬さが、ＪＩＳ Ｋ ６２５３デュロメータ硬さＡタイプにより、常温時（２５℃）で５５以下、低温時（−４０℃）で８５以下であることを特徴とするものである。 The constant velocity universal joint for a steering device according to the present invention is a constant velocity universal joint provided with a boot for preventing grease leakage from the inside of the constant velocity universal joint and foreign matter intrusion into the constant velocity universal joint, According to JIS K 6253 durometer hardness A type, the material hardness is 55 or less at normal temperature (25 ° C.) and 85 or less at low temperature (−40 ° C.).
そのようなブーツ材料を例示するならば、シリコーンゴム（ＶＭＱ）または低硬度クロロプレンゴムを挙げることができる。低硬度クロロプレンゴムとは、特に低温時の硬さを低くした特殊なクロロプレンゴムであって、具体的には、ＪＩＳ Ｋ ６２５３デュロメータ硬さＡタイプによる硬さが、常温時（２５℃）で５５以下、低温（−４０℃）で８５以下のものをいう。 Examples of such boot materials include silicone rubber (VMQ) or low hardness chloroprene rubber. The low hardness chloroprene rubber is a special chloroprene rubber having a particularly low hardness at low temperatures. Specifically, the hardness according to JIS K 6253 durometer hardness A type is 55 at room temperature (25 ° C.). Hereinafter, the low temperature (−40 ° C.) means 85 or less.
本発明の等速自在継手は電動パワーステアリング装置をはじめとする種々タイプのステアリング装置に用いることができる。 The constant velocity universal joint of the present invention can be used for various types of steering devices including an electric power steering device.
本発明によれば、ブーツの硬度が低下したことにより、等速自在継手の起動トルクや回転抵抗が低下する（図２８参照）。したがって、本発明のステアリング装置用等速自在継手を用いたステアリング装置は操作性が向上する。 According to the present invention, the starting torque and rotational resistance of the constant velocity universal joint are reduced due to the decrease in the hardness of the boot (see FIG. 28). Therefore, the operability of the steering device using the constant velocity universal joint for a steering device of the present invention is improved.
以下、本発明の実施の形態を図面に従って説明する。なお、以下ではステアリング用固定型等速自在継手の一種であるツェッパ型（ＢＪ）を例にとって説明するが、本発明はこれに限定されることなく、アンダーカットフリー型（ＵＪ）にも適用可能である。 Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the following, a Zepper type (BJ), which is a kind of a fixed type constant velocity universal joint for steering, will be described as an example. However, the present invention is not limited to this and can be applied to an undercut free type (UJ). It is.
まず、ステアリング装置について簡単に説明する。図２６に示すように、ステアリング装置は、ステアリングホイールｐの回転運動を、一または複数のステアリングシャフトｎからなるステアリングコラムを介してステアリングギヤｑに伝達することにより、タイロッドｒの往復運動に変換するようにしたものである。車載スペース等との兼ね合いでステアリングシャフトｎを一直線に配置できない場合に、ステアリングシャフトｎ間に一または複数の自在継手ｍを配置し、ステアリングシャフトｎを屈曲させた状態でもステアリングギヤｑに正確な回転運動を伝達できるようにしている。図２６は１個の等速自在継手ｍを使用した場合、図２７は２個の等速自在継手を使用した場合を示す。 First, the steering device will be briefly described. As shown in FIG. 26, the steering device converts the rotational motion of the steering wheel p into the reciprocating motion of the tie rod r by transmitting the rotational motion of the steering wheel p to the steering gear q via the steering column consisting of one or a plurality of steering shafts n. It is what I did. When the steering shaft n cannot be arranged in a straight line due to the in-vehicle space, etc., one or more universal joints m are arranged between the steering shafts n, and the steering gear q can be rotated accurately even when the steering shaft n is bent. It is possible to transmit exercise. 26 shows a case where one constant velocity universal joint m is used, and FIG. 27 shows a case where two constant velocity universal joints are used.
等速自在継手は、図１に示すように、複数のトラック溝１ａを形成した球状の内径面１ｂを有する外側継手部材である外輪１と、複数のトラック溝２ａを形成した球状の外径面２ｂを有する内側継手部材である内輪２と、外輪１のトラック溝１ａと内輪２のトラック溝２ａとの協働で形成されるボールトラックに配された複数のボール３と、外輪１の内径面１ｂと内輪２の外径面２ｂとの間に配置され、ボール３を収容するためのポケット４ａを円周方向等間隔に有する保持器４とを主要な構成要素とする。 As shown in FIG. 1, the constant velocity universal joint includes an outer ring 1 that is an outer joint member having a spherical inner surface 1b having a plurality of track grooves 1a and a spherical outer surface having a plurality of track grooves 2a. An inner ring 2 which is an inner joint member having 2b, a plurality of balls 3 arranged on a ball track formed in cooperation with a track groove 1a of the outer ring 1 and a track groove 2a of the inner ring 2, and an inner diameter surface of the outer ring 1 A cage 4 disposed between 1b and the outer diameter surface 2b of the inner ring 2 and having pockets 4a for accommodating the balls 3 at equal intervals in the circumferential direction is a main component.
トラック溝１ａ，２ａは軸方向に延びる曲線状をなし、通常は６本（８個ボールの場合は８本）がそれぞれ外輪１の内径面１ｂおよび内輪２の外径面２ｂに球面状に形成される。また、内輪２の内周にセレーションやスプライン等のトルク伝達手段を介して軸部材である中間シャフト５を結合している。 The track grooves 1a and 2a have a curved shape extending in the axial direction, and normally six (eight in the case of eight balls) are formed in a spherical shape on the inner diameter surface 1b of the outer ring 1 and the outer diameter surface 2b of the inner ring 2, respectively. Is done. Further, an intermediate shaft 5 that is a shaft member is coupled to the inner periphery of the inner ring 2 via torque transmission means such as serrations and splines.
このＢＪ型等速自在継手では、外輪１のトラック溝１ａの溝底が曲面状になった部位の中心（外輪トラック中心）Ｏ1は、外輪１の内径面１ｂの球面中心に対して、また、内輪２のトラック溝２ａの溝底が曲面状になった部位の中心（内輪トラック中心）Ｏ2は、内輪２の外径面２ｂの球面中心に対して、それぞれ軸方向に等距離だけ反対側にオフセットされている。 In this BJ type constant velocity universal joint, the center (outer ring track center) O 1 of the portion where the groove bottom of the track groove 1 a of the outer ring 1 is curved is the center of the spherical surface of the inner diameter surface 1 b of the outer ring 1 and The center (inner ring track center) O 2 of the portion where the groove bottom of the track groove 2a of the inner ring 2 is curved is opposite to the spherical center of the outer diameter surface 2b of the inner ring 2 by an equal distance in the axial direction. Is offset to the side.
保持器４の外周面４ｂの球面中心、および保持器の外周面４ｂの案内面となる外輪１の内径面１ｂの球面中心は、いずれも継手中心Ｏに一致している。また、保持器４の内周面４ｃの球面中心、および保持器の内周面４ｃの案内面となる内輪２の外径面２ｂの球面中心も、同様に継手中心Ｏに一致している。それ故、外輪トラック中心Ｏ1のオフセット量は、外輪トラック中心Ｏ1と継手中心Ｏとの間の軸方向距離となり、内輪トラック中心Ｏ2のオフセット量は、内輪トラック中心Ｏ2と継手中心Ｏとの間の軸方向距離となり、両者は等しい。 The spherical center of the outer peripheral surface 4b of the cage 4 and the spherical center of the inner surface 1b of the outer ring 1 serving as a guide surface for the outer peripheral surface 4b of the cage are all coincident with the joint center O. Further, the spherical center of the inner peripheral surface 4c of the cage 4 and the spherical center of the outer diameter surface 2b of the inner ring 2 serving as the guide surface of the inner peripheral surface 4c of the cage also coincide with the joint center O. Therefore, the offset amount of the outer ring track center O 1 becomes axial distance between the outer race track center O 1 and the joint center O, the offset amount of the inner race track center O 2 is the inner ring track center O 2 and the joint center O The axial distance between and is equal.
以上から、一対のトラック溝１ａ，２ａにより外輪１の開口側から奥部側へ縮小する楔状のボールトラックが形成され、このボールトラックに各ボール３が転動可能に組み込まれている。なお、保持器４の外周面４ｂおよび内周面４ｃの球面中心を継手中心Ｏに一致させているが、これらの球面中心を継手中心Ｏに対して軸方向のそれぞれ反対側に等距離だけオフセットさせることもできる。この等速自在継手では、外輪１と内輪２とが作動角をとると、保持器４に案内されたボール３が常にどの作動角においてもその作動角の二等分面内に維持され、継手の等速性が確保される。 As described above, the pair of track grooves 1a and 2a form a wedge-shaped ball track that shrinks from the opening side to the back side of the outer ring 1, and each ball 3 is incorporated in the ball track so as to be able to roll. The spherical centers of the outer peripheral surface 4b and the inner peripheral surface 4c of the cage 4 are made to coincide with the joint center O, but these spherical centers are offset by an equal distance from the joint center O on the opposite sides in the axial direction. It can also be made. In this constant velocity universal joint, when the outer ring 1 and the inner ring 2 take an operating angle, the ball 3 guided by the cage 4 is always maintained within the bisector of the operating angle at any operating angle. Is constant speed.
この実施形態の等速自在継手では、中間シャフト５の軸端に押圧部材１０を設けてある。押圧部材１０は、押圧部１１としてボール、弾性部材１２として圧縮コイルばね、押圧部１１と弾性部材１２をアッセンブリとするためのケース１３から構成される。この弾性部材１２は、押圧部１１を通じて弾性力として作用する。また、押圧部１１は、受け部１５との接点が球状であれば、その他の部分の形状は任意でもよい。ケース１３は、内輪２とセレーション結合で一体化された中間シャフト５の先端部に圧入あるいは接着材などによる適宜の手段で固定される。 In the constant velocity universal joint of this embodiment, the pressing member 10 is provided at the shaft end of the intermediate shaft 5. The pressing member 10 includes a ball as the pressing portion 11, a compression coil spring as the elastic member 12, and a case 13 for using the pressing portion 11 and the elastic member 12 as an assembly. The elastic member 12 acts as an elastic force through the pressing portion 11. Moreover, as long as the contact part with the receiving part 15 is spherical, the press part 11 may have any other shape. The case 13 is fixed to the front end portion of the intermediate shaft 5 integrated with the inner ring 2 by serration coupling by an appropriate means such as press fitting or adhesive.
保持器４の外輪奥部側の端部には、受け部材１４が取り付けられる。この受け部材１４は、保持器４の外輪奥部側の端部開口を覆う蓋状をなし、部分球面状の球面部１４ａとその外周に環状に形成された取付け部１４ｂとで構成される。球面部１４ａの内面（中間シャフト５と対向する面）は凹球面状で、この凹球面部は押圧部１１からの押圧力を受ける受け部１５として機能する。取付け部１４ｂは、保持器４の端部に圧入、溶接等の適宜の手段で固定されている。 A receiving member 14 is attached to an end of the retainer 4 on the outer ring back side. The receiving member 14 has a lid shape that covers the end opening of the cage 4 on the outer ring back side, and includes a spherical portion 14a having a partially spherical shape and a mounting portion 14b that is formed annularly on the outer periphery thereof. The inner surface of the spherical portion 14a (the surface facing the intermediate shaft 5) has a concave spherical shape, and this concave spherical portion functions as a receiving portion 15 that receives a pressing force from the pressing portion 11. The attachment portion 14b is fixed to the end portion of the cage 4 by appropriate means such as press-fitting and welding.
以上の構成において、中間シャフト５を内輪２の内周に嵌合し、止め輪１６等で両者を位置決めすると、押圧部材１０の押圧部１１と受け部材１４の受け部１５とが互いに当接し、弾性部材１２が圧縮される。これにより内輪２が外輪１の開口側に押圧され、両者間に軸方向の相対移動が生じる。内輪２のトラック溝２ａの形状は、外輪１の奥側に向かって拡径しているため、この相対移動によりトラックのラジアルすきまが詰められ、回転バックラッシュが防止されるようになる。 In the above configuration, when the intermediate shaft 5 is fitted to the inner circumference of the inner ring 2 and both are positioned by the retaining ring 16 or the like, the pressing portion 11 of the pressing member 10 and the receiving portion 15 of the receiving member 14 come into contact with each other, The elastic member 12 is compressed. As a result, the inner ring 2 is pressed toward the opening side of the outer ring 1, and an axial relative movement occurs between the two. Since the shape of the track groove 2a of the inner ring 2 increases toward the inner side of the outer ring 1, the radial clearance of the track is reduced by this relative movement, and rotation backlash is prevented.
この種の等速自在継手では、潤滑剤としてグリースが封入されており、そのグリースが外部へ漏洩したり、あるいは、外部から継手内部へ水やダスト等の異物が侵入したりすることを防止する目的から、等速自在継手の外輪１と中間シャフト５との間に密封用ブーツを装着する。このブーツについて、図１乃至図２５に示す各実施形態および変形例を以下に詳述する。 In this type of constant velocity universal joint, grease is sealed as a lubricant to prevent the grease from leaking to the outside or foreign materials such as water and dust from entering the inside of the joint from the outside. For the purpose, a sealing boot is mounted between the outer ring 1 of the constant velocity universal joint and the intermediate shaft 5. About this boot, each embodiment shown in FIG. 1 thru | or FIG. 25 and a modification are explained in full detail below.
図１に示す第１の実施形態における等速自在継手のブーツ２１は、外輪１の外周に嵌着される大径部２１ａと、内輪２に連結された中間シャフト５の外周に嵌着される小径部２１ｂと、大径部２１ａと小径部２１ｂの間のベロー部２１ｃからなる。 A boot 21 of a constant velocity universal joint in the first embodiment shown in FIG. 1 is fitted on the outer circumference of a large diameter portion 21 a fitted on the outer circumference of the outer ring 1 and the intermediate shaft 5 connected to the inner ring 2. It consists of a small diameter portion 21b and a bellows portion 21c between the large diameter portion 21a and the small diameter portion 21b.
ブーツ２１の大径部２１ａと小径部２１ｂの両端部は、円筒状のブーツ取り付け部位として、外輪１および中間シャフト５の外周に嵌着された後、金属製のブーツバンド２４，２５で締め付けられて気密的に固定される。つまり、外輪１および中間シャフト５の外周に、ブーツ２１の大径部２１ａおよび小径部２１ｂが嵌合される環状の凹溝２２，２３を形成する。一方、ブーツ２１の大径部２１ａおよび小径部２１ｂの内周に、環状の凸部２１ｆ，２１ｇを形成する。 Both ends of the large-diameter portion 21a and the small-diameter portion 21b of the boot 21 are fitted to the outer circumference of the outer ring 1 and the intermediate shaft 5 as cylindrical boot attachment portions, and then tightened with metal boot bands 24 and 25. And airtightly fixed. That is, annular concave grooves 22 and 23 into which the large diameter portion 21 a and the small diameter portion 21 b of the boot 21 are fitted are formed on the outer circumferences of the outer ring 1 and the intermediate shaft 5. On the other hand, annular convex portions 21f and 21g are formed on the inner periphery of the large diameter portion 21a and the small diameter portion 21b of the boot 21.
このブーツ２１は、大径部２１ａおよび小径部２１ｂの内周の凸部２１ｆ，２１ｇを外輪１および中間シャフト５の外周の凹溝２２，２３に収容させる。この時、前述の凸部２１ｆ，２１ｇおよび凹溝２２，２３は、その円周方向に沿う両側にテーパ面を有するので、相互に接合するテーパ面により位置合わせされる。この位置合わせ状態で、大径部２１ａおよび小径部２１ｂの外周をブーツバンド２４，２５にて締め付けることにより、ブーツ２１が外輪１および中間シャフト５に固定される。 In the boot 21, the convex portions 21 f and 21 g on the inner periphery of the large diameter portion 21 a and the small diameter portion 21 b are accommodated in the concave grooves 22 and 23 on the outer periphery of the outer ring 1 and the intermediate shaft 5. At this time, since the convex portions 21f and 21g and the concave grooves 22 and 23 have tapered surfaces on both sides along the circumferential direction, they are aligned by the tapered surfaces joined to each other. In this alignment state, the boot 21 is fixed to the outer ring 1 and the intermediate shaft 5 by tightening the outer circumferences of the large diameter portion 21 a and the small diameter portion 21 b with the boot bands 24 and 25.
図１の実施形態の等速自在継手では、一対の山部２１ｄおよび谷部２１ｅからなるベロー部２１ｃを有し、その山谷部２１ｄ，２１ｅが継手軸方向に向く形状としている。このように一対の山谷部２１ｄ，２１ｅが継手軸方向に向く形状としたことにより、外輪１に対して中間シャフト５が作動角をとった時（図２参照）に、ブーツ伸長を径方向ではなく軸方向に確保することで、ベロー部２１ｃでの接触面圧を低減することができる。なお、図３に示す変形例のブーツ３１のように山谷部３１ｄ，３１ｅ側のブーツ外径を、外輪１に装着された大径部３１ａの外径よりも大きくした形状とすることも可能である。 The constant velocity universal joint of the embodiment of FIG. 1 has a bellows portion 21c composed of a pair of peak portions 21d and valley portions 21e, and the peak and valley portions 21d and 21e are shaped to face the joint axial direction. Thus, when the intermediate shaft 5 takes an operating angle with respect to the outer ring 1 (see FIG. 2), the boot extension is caused in the radial direction by forming the pair of valley portions 21d and 21e so as to face the joint axial direction. By ensuring in the axial direction, the contact surface pressure at the bellows portion 21c can be reduced. It is also possible to make the outer diameter of the boots on the side of the mountain and valley portions 31d and 31e larger than the outer diameter of the large-diameter portion 31a attached to the outer ring 1, as in the modified boot 31 shown in FIG. is there.
図４は、大径部４１ａからベロー部４１ｃにかけて外輪１の外周面から離間するように外方へ拡径させた形状とした第２の実施形態を示す。この実施形態のブーツ４１は、大径部４１ａからベロー部４１ｃにかけてその大径部４１ａよりも大きな径となるように拡径した形状を有する。なお、大径部４１ａからベロー部４１ｃまでは同一径を有する。この実施形態の変更例として、図５に示すように大径部５１ａからベロー部５１ｃにかけて拡径させた後、徐々に縮径させた形状としてもよい。また、図６に示すように大径部６１ａからベロー部６１ｃにかけて拡径させた後、急激に縮径させた形状としてもよい。このようにすれば、外輪１に対して中間シャフト５が作動角をとった時、外方へ拡径させた部位が逃がしとなって、ブーツ伸長側で外輪１の外周面とブーツ４１，５１，６１の内周面が接触することを回避できる。 FIG. 4 shows a second embodiment in which the diameter is increased outward from the outer diameter surface of the outer ring 1 from the large diameter portion 41a to the bellows portion 41c. The boot 41 of this embodiment has a shape expanded from the large diameter portion 41a to the bellows portion 41c so as to have a larger diameter than the large diameter portion 41a. The large diameter portion 41a to the bellows portion 41c have the same diameter. As a modification of this embodiment, as shown in FIG. 5, the diameter may be gradually reduced from the large diameter part 51a to the bellows part 51c and then gradually reduced. Moreover, as shown in FIG. 6, after making it diameter-expand from the large diameter part 61a to the bellows part 61c, it is good also as a shape diameter-reduced rapidly. In this way, when the intermediate shaft 5 takes an operating angle with respect to the outer ring 1, the part expanded outwardly becomes a relief, and the outer peripheral surface of the outer ring 1 and the boots 41 and 51 on the boot extension side. , 61 can be prevented from coming into contact with each other.
図７は、ベロー部７１ｃにおける二つの山部７１ｄ1，７１ｄ2を離間配置させ、中間シャフト５に装着される小径部７１ｂ側に位置する一方の山部７１ｄ2を軸方向に撓ませた形状とした第３の実施形態の等速自在継手を示す。二つの山部７１ｄ1，７１ｄ2の離間距離を大きくとることで、外輪１に対して中間シャフト５が作動角をとった状態でも山部同士が強い接触状態になることはない。 FIG. 7 shows a shape in which two peak portions 71d 1 and 71d 2 in the bellows portion 71c are spaced apart and one peak portion 71d 2 located on the side of the small diameter portion 71b attached to the intermediate shaft 5 is bent in the axial direction. The constant velocity universal joint of 3rd Embodiment which was made is shown. By increasing the distance between the two peak portions 71d 1 and 71d 2 , the peak portions do not come into strong contact with each other even when the intermediate shaft 5 has an operating angle with respect to the outer ring 1.
図８は、ベロー部８１ｃが、可撓性材料からなり、一つの山部８１ｄを有する形状とした第４の実施形態の等速自在継手を示す。前述のような山部同士の接触が発生することがない形状、つまり、一つの山部８１ｄを有する形状とすることで作動角をとった状態におけるブーツ伸長不足を、可撓性を持たせることにより補完することができる。 FIG. 8 shows a constant velocity universal joint according to a fourth embodiment in which the bellows portion 81c is made of a flexible material and has a single peak portion 81d. By providing a shape that does not cause contact between the ridges as described above, that is, a shape having one ridge 81d, it is possible to give flexibility to the boot extension shortage in a state where the operating angle is taken. Can be complemented by
図９は、ベロー部９１ｃを、小径部９１ｂがブーツ９１の内部に収納されるような形状とした第５の実施形態の等速自在継手を示す。つまり、この等速自在継手では、中間シャフト５に装着された小径部９１ｂから延びる部位を軸方向に延在させ、軸方向に向く山部９１ｄを形成した形状を具備する。このような構成とすれば、図１０に示すように大きな作動角をとった状態でもブーツ伸長を十分に確保することができる。 FIG. 9 shows a constant velocity universal joint according to a fifth embodiment in which the bellows portion 91 c is shaped such that the small diameter portion 91 b is housed inside the boot 91. That is, this constant velocity universal joint has a shape in which a portion extending from the small diameter portion 91b attached to the intermediate shaft 5 is extended in the axial direction to form a mountain portion 91d facing in the axial direction. With such a configuration, it is possible to sufficiently ensure boot extension even in a state where a large operating angle is taken as shown in FIG.
なお、図１１に示す第６の実施形態のようにブーツ１０１の軸方向中央部位、つまり、大径部１０１ａと山部１０１ｄとの間に厚肉部３７を設けるようにしてもよい。このようにすれば、ブーツ１０１の剛性を向上させることができる。なお、厚肉部３７としては、図１１に示すように連続的に厚肉状態とする形態以外に、断続的に厚肉状態とする形態、例えば円周方向に突起３８（図１６参照）を一体的に設ける形態が可能である。また、突起を設ける場合、ブーツ外径の増加を防ぐためにブーツ内周面に突起を設けるのが望ましいが、等速自在継手の取り付け部周辺の空間に制約がなければ、ブーツ外周面に突起を設けてもよい。 In addition, you may make it provide the thick part 37 between the axial direction center parts of the boot 101, ie, the large diameter part 101a, and the peak part 101d like 6th Embodiment shown in FIG. In this way, the rigidity of the boot 101 can be improved. In addition to the form of continuously thickening as shown in FIG. 11, the thick part 37 has a form of intermittently thickening, for example, a protrusion 38 (see FIG. 16) in the circumferential direction. A form in which they are provided integrally is possible. In addition, when providing a protrusion, it is desirable to provide a protrusion on the inner peripheral surface of the boot to prevent an increase in the outer diameter of the boot, but if there is no restriction on the space around the mounting portion of the constant velocity universal joint, the protrusion is provided on the outer peripheral surface of the boot. It may be provided.
図１２は、ベロー部１１１ｃから大径部１１１ａにかけて徐々に厚肉にした構造を有する第７の実施形態の等速自在継手を示す。このようにすれば、大きな作動角をとった状態でもブーツ伸長側で外輪１の外周面とブーツ１１１の内周面が接触することを回避できる。また、図１３に示す第８の実施形態のようにベロー部１２１ｃから大径部１２１ａにかけてブーツ内周面が所定の角度αでもって外輪１の外周面に接する構造としてもよい。このようにすれば、外輪１の外周面からブーツ１２１の内周面を逃がした形状となり、作動角をとった時にブーツ伸長側で外輪１の外周面とブーツ１２１の内周面が接触することを回避できる。 FIG. 12 shows a constant velocity universal joint according to a seventh embodiment having a structure in which the thickness is gradually increased from the bellows portion 111c to the large diameter portion 111a. In this way, it is possible to avoid contact between the outer peripheral surface of the outer ring 1 and the inner peripheral surface of the boot 111 on the boot extension side even in a state where a large operating angle is taken. Further, as in the eighth embodiment shown in FIG. 13, the inner peripheral surface of the boot may be in contact with the outer peripheral surface of the outer ring 1 at a predetermined angle α from the bellows part 121c to the large diameter part 121a. If it does in this way, it will become the shape which escaped the inner peripheral surface of the boot 121 from the outer peripheral surface of the outer ring 1, and when the operating angle is taken, the outer peripheral surface of the outer ring 1 and the inner peripheral surface of the boot 121 will contact on the boot extension side Can be avoided.
図１４に示す第９の実施形態の等速自在継手では、大径部１３１ａの外径が、その大径部１３１ａに締着されるブーツバンド２４の締付け時最大径よりも大きくなるように、ブーツバンド締付け溝３９の深さを設定した構造を有する。このようにすれば、大きな作動角をとった時、ブーツバンド２４上に倒れこんできたブーツ１３１とブーツバンド２４の接触を回避することができる。 In the constant velocity universal joint of the ninth embodiment shown in FIG. 14, the outer diameter of the large-diameter portion 131a is larger than the maximum diameter at the time of tightening of the boot band 24 fastened to the large-diameter portion 131a. The boot band fastening groove 39 has a set depth. In this way, it is possible to avoid the contact between the boot 131 and the boot band 24 that has fallen on the boot band 24 when a large operating angle is taken.
また、図１５に示す第１０の実施形態のように大径部１４１ａの外周面にあるエッジ部４２，４３を面取り加工（例えばＲ加工）すれば、大きな作動角をとった時に倒れこんできたブーツ１４１とエッジ部４２，４３の接触面圧を低減でき、ブーツ１４１の耐久性向上が図れる。なお、この実施形態では、等速自在継手の外輪１に装着される大径部１４１ａに適用した場合について説明したが、中間シャフト５に装着される小径部についても適用可能である。 Moreover, if the edge parts 42 and 43 in the outer peripheral surface of the large-diameter part 141a are chamfered (for example, R-processed) as in the tenth embodiment shown in FIG. The contact surface pressure between the boot 141 and the edge portions 42 and 43 can be reduced, and the durability of the boot 141 can be improved. In this embodiment, the case where the constant velocity universal joint is applied to the large diameter portion 141a attached to the outer ring 1 has been described. However, the present invention can also be applied to a small diameter portion attached to the intermediate shaft 5.
図１６に示す第１１の実施形態の等速自在継手では、外輪１の外周面に凸部２７を円周方向に沿って形成し、その外輪１の外周面に嵌着されたブーツアダプタ２６の端部２６ａを前述の凸部２７に沿わせて加締めることによりブーツアダプタ２６を外輪１に固定し、ベロー部１５１ｃを、大径部１５１ａがブーツ１５１の内部に収納されるような形状、つまり、ブーツアダプタ２６に装着された大径部１５１ａから延びる部位を軸方向に延在させ、軸方向に向く山部１５１ｄ’を形成した形状とする。このようにすれば、大きな作動角をとった状態でも十分なブーツ伸長を確保することができ、ブーツ１５１の接触面圧の低減化が図れる。なお、外輪１へのブーツアダプタ２６の取り付けに際しては、外輪１とブーツアダプタ２６間にＯリング２８を介挿することによりシール性を確保する。 In the constant velocity universal joint of the eleventh embodiment shown in FIG. 16, a convex portion 27 is formed along the circumferential direction on the outer peripheral surface of the outer ring 1, and the boot adapter 26 fitted on the outer peripheral surface of the outer ring 1. The boot adapter 26 is fixed to the outer ring 1 by caulking the end portion 26a along the convex portion 27, and the bellows portion 151c is shaped so that the large-diameter portion 151a is housed inside the boot 151, that is, A portion extending from the large-diameter portion 151a attached to the boot adapter 26 is extended in the axial direction to form a mountain portion 151d ′ facing in the axial direction. In this way, sufficient boot extension can be ensured even when a large operating angle is taken, and the contact surface pressure of the boot 151 can be reduced. When the boot adapter 26 is attached to the outer ring 1, the sealing performance is ensured by inserting an O-ring 28 between the outer ring 1 and the boot adapter 26.
なお、この実施形態では、ブーツアダプタ２６を外輪１の外周面に形成した凸部２７に加締めることにより固定した場合について説明したが、図１７に示す第１２の実施形態のように外輪１の外周面に溝などの凹部２９を形成し、その凹部２９の形状に沿うようにブーツアダプタ３６の端部３６ａを加締めるようにしてもよい。図１８は、外輪１の外周面に溝などの凹部２９を形成し、その凹部２９の形状に沿うようにブーツアダプタ３６の端部３６ａを加締めた実施形態において、大きな作動角をとった状態を示す。また、図１６および図１７に示す実施形態におけるブーツ１５１は、中間シャフト５に装着される小径部１５１ｂがブーツ１５１の内部に収まるような形状としたが、図１９および図２０に示すように中間シャフト５に装着される小径部１６１ｂがブーツ１６１の外部に配置されるような形状とすることも可能である。 In this embodiment, the case where the boot adapter 26 is fixed by crimping to the convex portion 27 formed on the outer peripheral surface of the outer ring 1 has been described. However, as in the twelfth embodiment shown in FIG. A recess 29 such as a groove may be formed on the outer peripheral surface, and the end 36 a of the boot adapter 36 may be crimped along the shape of the recess 29. FIG. 18 shows a state in which a large operating angle is taken in an embodiment in which a recess 29 such as a groove is formed on the outer peripheral surface of the outer ring 1 and the end 36a of the boot adapter 36 is crimped along the shape of the recess 29. Indicates. Further, the boot 151 in the embodiment shown in FIGS. 16 and 17 is shaped so that the small-diameter portion 151b attached to the intermediate shaft 5 fits inside the boot 151. However, as shown in FIGS. It is also possible to adopt a shape in which the small diameter portion 161b attached to the shaft 5 is disposed outside the boot 161.
図２１に示す第１５の実施形態の等速自在継手では、大きな作動角をとった時にブーツ内圧が上昇する変化量を小さくした形状のブーツ１７１を具備する。ここで、大きな作動角をとった時にブーツ内圧が上昇する変化量を小さくした形状として、外輪１に取り付けられる大径部１７１ａと中間シャフト５に取り付けられる小径部１７１ｂとの間に位置するベロー部１７１ｃは、継手軸方向に向く一つの山部１７１ｄを大径部１７１ａ側に形成した形状としている。なお、この図２１と図２３乃至図２５では、外輪１の内部構造（内輪２、ボール３および保持器４）は、前述した各実施形態と同様であるために図示省略している。 The constant velocity universal joint of the fifteenth embodiment shown in FIG. 21 includes a boot 171 having a shape in which the amount of change in which the boot internal pressure rises when the large operating angle is taken is reduced. Here, the bellows part located between the large-diameter part 171a attached to the outer ring 1 and the small-diameter part 171b attached to the intermediate shaft 5 as a shape in which the amount of change in which the boot internal pressure increases when a large operating angle is taken is reduced. 171c has a shape in which one peak portion 171d facing the joint axial direction is formed on the large diameter portion 171a side. In FIG. 21 and FIGS. 23 to 25, the internal structure of the outer ring 1 (the inner ring 2, the ball 3 and the cage 4) is omitted because it is the same as in the above-described embodiments.
ベロー部１７１ｃは、継手中心Ｏからの曲率半径ＳＲの球状内面を持つ小径側の第一ベロー部１７１ｃ1と、継手軸方向に向く一つの山部１７１ｄを持つ大径側の第二ベロー部１７１ｃ2からなる。この第一ベロー部１７１ｃ1は、例えば硬質ゴム、硬質樹脂または金属からなる硬質部材であり、第二ベロー部１７１ｃ2は、例えばＣＲやシリコン等のゴムまたは軟質樹脂からなる軟質部材である。 Bellows portion 171c includes a first bellows portion 171c 1 of the small diameter side with spherical inner surface of the curvature radius SR from the joint center O, the second bellows portion 171c of the large diameter side with a single crest 171d facing the joint axis It consists of two . The first bellows part 171c 1 is a hard member made of, for example, hard rubber, hard resin or metal, and the second bellows part 171c 2 is a soft member made of rubber or soft resin such as CR or silicon.
第一ベロー部１７１ｃ1は、図２２に示すように小径部１７１ｂの内周面に凸部７３を円周方向に沿って形成し、その凸部７３を中間シャフト５の外周に形成された凹溝７２に嵌合させることにより小径部１７１ｂが位置決めされる。なお、中間シャフト５へのブーツ取り付けに際しては、中間シャフト５とブーツ１７１の小径部１７１ｂ間にＯリング７４を介挿することによりシール性を確保する。 As shown in FIG. 22, the first bellows portion 171 c 1 is formed with a convex portion 73 along the circumferential direction on the inner peripheral surface of the small diameter portion 171 b, and the convex portion 73 is a concave formed on the outer periphery of the intermediate shaft 5. The small diameter portion 171b is positioned by fitting in the groove 72. When attaching the boot to the intermediate shaft 5, the sealing performance is secured by inserting an O-ring 74 between the intermediate shaft 5 and the small diameter portion 171 b of the boot 171.
図２１に示すように前述の第一ベロー部１７１ｃ1の大径側端部には凹陥部７５が円周方向に沿って形成され、また、第二ベロー部１７１ｃ2の小径側端部には凸部７６が円周方向に沿って形成され、これら凸部７６を凹陥部７５に圧入又は接着嵌合させることにより第一ベロー部１７１ｃ1と第二ベロー部１７１ｃ2を連結させている。一方、ブーツ１７１の大径部１７１ａ、つまり、前述の第二ベロー部１７１ｃ2の大径側端部を金属製のブーツアダプタ７７を介して外輪１に固定している。このブーツアダプタ７７は、外輪１の外周面に沿わせて加締めることにより抜け止め固定されている。また、ブーツアダプタ７７と外輪１の外周面との間にＯリング７４´を介挿することによりシール性を確保している。 As shown in FIG. 21, a concave portion 75 is formed along the circumferential direction at the large-diameter end of the first bellows 171c 1 described above, and at the small-diameter end of the second bellows 171c 2 The convex portions 76 are formed along the circumferential direction, and the first bellows portion 171c 1 and the second bellows portion 171c 2 are connected by press fitting or adhesively fitting the convex portions 76 to the concave portions 75. On the other hand, the large-diameter portion 171 a of the boot 171, that is, the large-diameter side end of the second bellows portion 171 c 2 is fixed to the outer ring 1 via a metal boot adapter 77. The boot adapter 77 is fixed and secured by crimping along the outer peripheral surface of the outer ring 1. Further, an O-ring 74 ′ is inserted between the boot adapter 77 and the outer peripheral surface of the outer ring 1 to ensure sealing performance.
なお、この実施形態では、継手中心Ｏから第一ベロー部１７１ｃ1と第二ベロー部１７１ｃ2との連結部分までの曲率半径ｒ1を、継手中心Ｏからブーツアダプタ７７のブーツ固定部分までの曲率半径ｒ2よりも大きく設定する必要がある。このように設定することにより、作動角をとった時にブーツ１７１がブーツアダプタ７７に干渉することを防止している（図２３参照）。 In this embodiment, the radius of curvature r 1 from the joint center O to the connecting portion between the first bellows part 171c 1 and the second bellows part 171c 2 is the curvature from the joint center O to the boot fixing part of the boot adapter 77. it is necessary to set larger than the radius r 2. By setting in this way, the boot 171 is prevented from interfering with the boot adapter 77 when the operating angle is taken (see FIG. 23).
この実施形態の等速自在継手では、前述したようなブーツ形状としたことにより、ブーツ１７１の内部容積を小さくするとともに、図２３に示すように作動角をとった時にブーツ１７１の内容積の変化を少なくすることができ、その結果、大きな作動角をとった時にブーツ内圧が上昇する変化量を小さくことができる。 In the constant velocity universal joint of this embodiment, since the boot shape is as described above, the internal volume of the boot 171 is reduced, and the change in the internal volume of the boot 171 when the operating angle is taken as shown in FIG. As a result, the amount of change in which the boot internal pressure rises when a large operating angle is taken can be reduced.
なお、この実施形態では、ベロー部１７１ｃを第一ベロー部１７１ｃ1と第二ベロー部１７１ｃ2からなる形状としたが、図２４および図２５に示すように以前の実施形態のように第一ベロー部と第二ベロー部を一体化した単一のベロー部１８１ｃで構成することも可能である。この実施形態のベロー部１８１ｃは、長軸ａおよび短軸ｂからなる楕円（図２４の点線で示す）の一部をなす形状を有しているが、単一円弧となる形状でもよい。 In this embodiment, although the bellows portion 171c and the first bellows portion 171c 1 and shape made of the second bellows portion 171c 2, first bellows as in previous embodiments as shown in FIGS. 24 and 25 It is also possible to configure with a single bellows part 181c in which the part and the second bellows part are integrated. The bellows portion 181c of this embodiment has a shape that forms a part of an ellipse (shown by the dotted line in FIG. 24) composed of the major axis a and the minor axis b, but may have a single arc shape.
また、大きな作動角をとった時にブーツ内圧が上昇する変化量を小さくするブーツとしては、図示しないが、前述のベロー部に通気孔を設けた構造であってもよい。このように通気孔を設ければ、ブーツ内圧が上昇することを抑制することができる。 Further, as a boot for reducing the amount of change in which the boot internal pressure rises when a large operating angle is taken, a structure in which a vent hole is provided in the bellows portion described above may be used. Providing vent holes in this way can suppress an increase in boot internal pressure.
種々のブーツの形状について述べたが、本発明は特許文献１および特許文献２に示されているようないわゆる蛇腹タイプのブーツ（図２７参照）にも適用することができるのは言うまでもない。図２８は、クロロプレンゴム（ＣＲ）、低硬度ＣＲ、シリコーンゴム（ＶＭＱ）といった３種のブーツ材料について、等速自在継手の回転抵抗を測定した結果を示す。ここで使用したブーツは蛇腹タイプである。図２８（Ａ）は常温（２５℃）の場合、図２８（Ｂ）は低温（−４０°）の場合である。ここに、低硬度ＣＲとは、特に低温時の硬さを低くした特殊なクロロプレンゴムであって、具体的には、ＪＩＳ Ｋ ６２５３デュロメータ硬さＡタイプによる硬さが、常温時（２５℃）で５５以下、低温（−４０℃）で８５以下のものをいう。クロロプレンゴム製のブーツを使用した従来の等速自在継手に比べて、低硬度ＣＲ製のブーツを使用したものとシリコーンゴム製のブーツを使用したものはいずれも、回転抵抗が１／２以下に低下している。 Although various boot shapes have been described, it goes without saying that the present invention can also be applied to a so-called bellows type boot (see FIG. 27) as shown in Patent Document 1 and Patent Document 2. FIG. 28 shows the results of measuring the rotational resistance of a constant velocity universal joint for three types of boot materials such as chloroprene rubber (CR), low hardness CR, and silicone rubber (VMQ). The boot used here is a bellows type. FIG. 28A shows the case of normal temperature (25 ° C.), and FIG. 28B shows the case of low temperature (−40 °). Here, the low hardness CR is a special chloroprene rubber in which the hardness at low temperature is particularly low. Specifically, the hardness according to JIS K 6253 durometer hardness A type is normal temperature (25 ° C.). 55 or less at low temperature (−40 ° C.). Compared to conventional constant velocity universal joints using chloroprene rubber boots, the rotation resistance of those using low hardness CR boots and silicone rubber boots is 1/2 or less. It is falling.
１ 外側継手部材（外輪）
２ 内側継手部材（内輪）
５ 軸部材（中間シャフト）
２１ ブーツ
1 Outer joint member (outer ring)
2 Inner joint member (inner ring)
5 Shaft member (intermediate shaft)
21 boots
Claims (4)
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2004025805A JP2005214395A (en) | 2004-02-02 | 2004-02-02 | Uniform motion universal joint for steering device, and steering device |
| PCT/JP2004/019848 WO2005073583A1 (en) | 2004-02-02 | 2004-12-28 | Constant velocity universal joint for steering device and steering device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2004025805A JP2005214395A (en) | 2004-02-02 | 2004-02-02 | Uniform motion universal joint for steering device, and steering device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JP2005214395A true JP2005214395A (en) | 2005-08-11 |
Family
ID=34823998
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2004025805A Withdrawn JP2005214395A (en) | 2004-02-02 | 2004-02-02 | Uniform motion universal joint for steering device, and steering device |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP2005214395A (en) |
| WO (1) | WO2005073583A1 (en) |
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| WO2010024434A1 (en) * | 2008-09-01 | 2010-03-04 | Ntn株式会社 | Boot for steering device, constant-velocity universal joint for steering device, and steering device |
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| JP2003313434A (en) * | 2002-02-25 | 2003-11-06 | Sumitomo Chem Co Ltd | Thermoplastic elastomer composition |
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- 2004-02-02 JP JP2004025805A patent/JP2005214395A/en not_active Withdrawn
- 2004-12-28 WO PCT/JP2004/019848 patent/WO2005073583A1/en active Application Filing
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