JPH09133145A - Constant velocity joint - Google Patents

Constant velocity joint

Info

Publication number
JPH09133145A
JPH09133145A JP7288891A JP28889195A JPH09133145A JP H09133145 A JPH09133145 A JP H09133145A JP 7288891 A JP7288891 A JP 7288891A JP 28889195 A JP28889195 A JP 28889195A JP H09133145 A JPH09133145 A JP H09133145A
Authority
JP
Japan
Prior art keywords
constant velocity
velocity joint
roller
roller member
needle bearing
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
JP7288891A
Other languages
Japanese (ja)
Inventor
Satoshi Kudo
智 工藤
Takeshi Takagi
武 高木
Akira Yokoyama
晃 横山
Takeshi Kayano
健 茅野
Tsutomu Kawakatsu
勉 川勝
Naohiro Ogura
尚宏 小倉
Shoichi Nakao
彰一 中尾
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Honda Motor Co Ltd
Original Assignee
Honda Motor Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Honda Motor Co Ltd filed Critical Honda Motor Co Ltd
Priority to JP7288891A priority Critical patent/JPH09133145A/en
Publication of JPH09133145A publication Critical patent/JPH09133145A/en
Pending legal-status Critical Current

Links

Classifications

    • 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
    • F16D3/202—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 one coupling part having radially projecting pins, e.g. tripod joints
    • F16D3/205—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 one coupling part having radially projecting pins, e.g. tripod joints the pins extending radially outwardly from the coupling part
    • F16D3/2055—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 one coupling part having radially projecting pins, e.g. tripod joints the pins extending radially outwardly from the coupling part having three pins, i.e. true tripod joints
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/20—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
    • F16D3/202—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 one coupling part having radially projecting pins, e.g. tripod joints
    • F16D2003/2026—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 one coupling part having radially projecting pins, e.g. tripod joints with trunnion rings, i.e. with tripod joints having rollers supported by a ring on the trunnion

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Automatic Assembly (AREA)

Abstract

PROBLEM TO BE SOLVED: To enlarge an operating angle of a driven shaft as well as to check such a fact that any vibration is transmitted to the side of a spider shaft, securing a good vibro-cutoff characteristic by installing an inner roller member along the longitudinal direction of a needle bearing free of slide motion. SOLUTION: A clearance 61 is partitioned off in an interval between two plane parts 52a, 52b and two peripheral surface parts 60a, 60b of a roller inner 56, while since the roller inner 56 is installed along the longitudinal direction of a needle bearing 66 free of sliding displacement, an operating angle of a driven shaft 34 can be made larger. In addition, such a possibility that a vibration might be transmitted from the side of an outer cup 32 to the side of the spider shaft 48a is checkable owing to the needle bearing 66 to be interposed between a roller outer 68 and the roller inner 56. Therefore, a good vibro-cutoff characteristic is securable.

Description

【発明の詳細な説明】Detailed Description of the Invention

【０００１】[0001]

【発明の属する技術分野】本発明は、例えば、自動車の
駆動力伝達部において、駆動軸と従動軸とを連結させる
等速ジョイントに関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a constant velocity joint for connecting a drive shaft and a driven shaft in, for example, a driving force transmitting portion of an automobile.

【０００２】[0002]

【従来の技術】従来より、自動車の駆動力伝達部では、
駆動軸の回転力を従動軸を介して各車軸へと伝達させる
ために等速ジョイントが用いられている。ここで、第１
の従来技術に係る等速ジョイントを図９に示す。この等
速ジョイント１は、アウタカップ２の内壁面に軸方向に
沿って延在する３本のローラガイド溝３ａ〜３ｃが画成
され、前記アウタカップ２内にはスパイダ４が配設され
る。2. Description of the Related Art Conventionally, in a driving force transmitting section of an automobile,
A constant velocity joint is used to transmit the torque of the drive shaft to each axle via a driven shaft. Here, the first
FIG. 9 shows a constant velocity joint according to the related art. In the constant velocity joint 1, three roller guide grooves 3a to 3c extending in the axial direction are defined on the inner wall surface of the outer cup 2, and a spider 4 is arranged in the outer cup 2.

【０００３】前記スパイダ４にはローラガイド溝３ａ〜
３ｃに向かって膨出するスパイダ軸５ａ〜５ｃがそれぞ
れ形成され、前記スパイダ軸５ａ（５ｂ、５ｃ）の外周
面にはリング状の内側ローラ６がそれぞれ外嵌され、さ
らに、前記内側ローラ６の外周部にはニードル７および
外側ローラ８を保持するホルダ９が設けられる。前記外
側ローラ８が摺接するローラガイド溝３ａ（３ｂ、３
ｃ）の湾曲面には、該外側ローラ８の傾きを規制する端
面規制部１０が膨出形成される。The spider 4 has roller guide grooves 3a ...
Spider shafts 5a to 5c bulging toward 3c are formed respectively, and ring-shaped inner rollers 6 are externally fitted to the outer peripheral surfaces of the spider shafts 5a (5b, 5c), respectively. A holder 9 for holding the needle 7 and the outer roller 8 is provided on the outer peripheral portion. Roller guide grooves 3a (3b, 3b) with which the outer roller 8 is in sliding contact
On the curved surface of c), an end face restricting portion 10 that restricts the inclination of the outer roller 8 is bulged.

【０００４】なお、前記ホルダ９の底面部にはローラガ
イド溝３ａ側に向かって突出するフランジ１１が設けら
れ、また、前記ニードル７は外側ローラ８とホルダ９と
の間に設けられたサークリップ１４およびワッシャ１５
によって保持される。この場合、従動軸に連結されるス
パイダ４に対して大きな作動角が付与されることによ
り、湾曲するローラガイド溝３ａに沿って外側ローラ８
が摺動変位する。このため、ホルダ９の上部側端部１２
をアウタカップ２の上面部１３に当接させ、あるいはホ
ルダ９のフランジ１１を端面規制部１０に当接させるこ
とにより、ローラガイド溝３ａに対する外側ローラ８の
傾斜角度が所定範囲となるように規制している。A flange 11 projecting toward the roller guide groove 3a is provided on the bottom surface of the holder 9, and the needle 7 is a circlip provided between the outer roller 8 and the holder 9. 14 and washer 15
Is held by In this case, a large operating angle is given to the spider 4 connected to the driven shaft, so that the outer roller 8 moves along the curved roller guide groove 3a.
Is slidingly displaced. Therefore, the upper end 12 of the holder 9
Is brought into contact with the upper surface portion 13 of the outer cup 2 or the flange 11 of the holder 9 is brought into contact with the end surface regulating portion 10 so that the inclination angle of the outer roller 8 with respect to the roller guide groove 3a is regulated within a predetermined range. ing.

【０００５】次に、第２の従来技術に係る等速ジョイン
トを図１０に示す。この等速ジョイント１６は、略円柱
状を呈するスパイダ軸１７の外周面にニードル１８を介
してローラ１９が直接的に外嵌される構成が採用されて
いる。なお、参照符号２０はスパイダ２１に連結される
従動側シャフトである。Next, FIG. 10 shows a constant velocity joint according to the second prior art. The constant velocity joint 16 has a structure in which a roller 19 is directly fitted onto the outer peripheral surface of a spider shaft 17 having a substantially cylindrical shape via a needle 18. The reference numeral 20 is a driven shaft connected to the spider 21.

【０００６】[0006]

【発明が解決しようとする課題】しかしながら、第１の
従来技術に係る等速ジョイント１では、外側ローラ８の
傾きをホルダ９の上部側端部１２およびフランジ１１に
よって規制しているため、前記ホルダ９の上部側端部１
２およびフランジ１１と、アウタカップ２の内壁面との
クリアランス管理を精度良く行う必要があり、煩雑とな
る不具合がある。However, in the constant velocity joint 1 according to the first prior art, the inclination of the outer roller 8 is restricted by the upper end 12 of the holder 9 and the flange 11, so that the holder is Upper end 1 of 9
The clearance between the inner wall surface of the outer cup 2 and the flange 2 and the flange 11 has to be accurately controlled, which causes a problem of complexity.

【０００７】また、ホルダ９の上部側端部１２またはフ
ランジ１１が外側ローラ８の傾きを規制するためにアウ
タカップ２の内壁面に当接する際に摺動摩擦が発生し、
前記摺動摩擦によって外側ローラ８の摺動変位が阻害さ
れるおそれがある。さらに、駆動軸側で誘起された振動
がアウタカップ２から外側ローラ８に接触するフランジ
１１を経由し内側ローラ６を介してスパイダ軸５ａに伝
達され、最終的にはスパイダ４に連結される従動軸側に
伝搬されるため、振動遮断特性が劣化するという不都合
がある。Sliding friction occurs when the upper end 12 of the holder 9 or the flange 11 contacts the inner wall surface of the outer cup 2 in order to regulate the inclination of the outer roller 8.
The sliding friction may hinder the sliding displacement of the outer roller 8. Further, the vibration induced on the drive shaft side is transmitted from the outer cup 2 to the spider shaft 5a via the inner roller 6 via the flange 11 that contacts the outer roller 8, and finally is connected to the spider 4 as a driven shaft. Since it is propagated to the side, there is a disadvantage that the vibration isolation characteristic deteriorates.

【０００８】さらにまた、第２の従来技術に係る等速ジ
ョイント１６では、図１０に示されるような球面を有す
る内側ローラ６が設けられていないため、従動側シャフ
ト２０の軸線方向に対する揺動角度（作動角度）が規制
されてしまうという不都合がある。またさらに、前述し
た等速ジョイント１、１６では、部品点数が多く、製造
コストが高騰するという不都合がある。Furthermore, in the constant velocity joint 16 according to the second prior art, since the inner roller 6 having a spherical surface as shown in FIG. 10 is not provided, the swing angle of the driven shaft 20 with respect to the axial direction. There is an inconvenience that the (operating angle) is restricted. Further, the constant velocity joints 1 and 16 described above have a large number of parts, which causes a problem of high manufacturing cost.

【０００９】本発明は、前記種々の不都合および問題点
を悉く克服するためになされたものであり、摺動摩擦を
発生させることなく傾き角度を規制するとともに、駆動
側に誘起した振動が従動側に伝搬することを阻止し、さ
らに、構造の簡素化を図ることにより小型・軽量化を達
成し、しかも製造コストを削減することが可能な等速ジ
ョイントを提供することを目的とする。The present invention has been made in order to overcome the various inconveniences and problems described above. The inclination angle is regulated without generating sliding friction, and the vibration induced on the driving side is transmitted to the driven side. It is an object of the present invention to provide a constant velocity joint that can prevent propagation and can achieve size and weight reduction by further simplifying the structure and further reduce manufacturing cost.

【００１０】[0010]

【課題を解決するための手段】前記の目的を達成するた
めに、本発明は、所定間隔離間し軸線方向に沿って延在
する複数のトラック溝が内周面に設けられ、一方の伝導
軸に連結される筒状のアウタ部材と、前記アウタ部材の
開口する内空部内に挿入されて他方の伝導軸に連結され
るインナ部材とを有する等速ジョイントにおいて、前記
トラック溝の方向に沿って膨出するスパイダ軸と、前記
スパイダ軸に外嵌される内側ローラ部材と、前記内側ロ
ーラ部材と非接触状態に形成され、前記トラック溝に沿
って摺動変位する外側ローラ部材と、前記内側ローラ部
材と外側ローラ部材との間に介装されるニードルベアリ
ングと、を備え、前記内側ローラ部材は、前記ニードル
ベアリングの長手方向に沿って前記スパイダ軸と一体的
に摺動自在に形成されることを特徴とする。In order to achieve the above-mentioned object, the present invention provides a plurality of track grooves, which are spaced apart by a predetermined distance and extend along the axial direction, on the inner peripheral surface, and one of the conductive shafts is provided. In a constant velocity joint having a tubular outer member connected to the outer member, and an inner member inserted into the inner space of the outer member and connected to the other conductive shaft, along the direction of the track groove. A swelling spider shaft, an inner roller member fitted onto the spider shaft, an outer roller member formed in a non-contact state with the inner roller member and slidingly displaced along the track groove, and the inner roller And a needle bearing interposed between the outer roller member and the outer roller member, wherein the inner roller member is integrally slidable with the spider shaft along the longitudinal direction of the needle bearing. Characterized in that it is.

【００１１】この場合、前記ニードルベアリングは、外
側ローラの内周面に画成された環状溝に保持されるよう
に形成すると好適である。。また、外側ローラ部材の頂
部は、内側ローラ部材の頂部よりもトラック溝側に突出
して形成され、前記外側ローラ部材の頂部が前記トラッ
ク溝に当接することにより該外側ローラ部材の傾斜角度
を規制する。In this case, it is preferable that the needle bearing is formed so as to be retained in an annular groove defined on the inner peripheral surface of the outer roller. . Further, the top portion of the outer roller member is formed so as to protrude toward the track groove side from the top portion of the inner roller member, and the inclination angle of the outer roller member is regulated by contacting the top portion of the outer roller member with the track groove. .

【００１２】本発明によれば、内側ローラ部材がニード
ルベアリングの長手方向に沿って摺動自在に設けられて
いるため、従動軸の作動角を大きくすることが可能とな
る。また、内側ローラ部材と外側ローラ部材との間に介
装されるニードルベアリングによってアウタ部材からス
パイダ軸側に振動が伝達されることが阻止され、良好な
振動遮断特性を得ることができる。According to the present invention, since the inner roller member is provided slidably along the longitudinal direction of the needle bearing, the working angle of the driven shaft can be increased. Further, the needle bearing interposed between the inner roller member and the outer roller member prevents the vibration from being transmitted from the outer member to the spider shaft side, so that good vibration isolation characteristics can be obtained.

【００１３】[0013]

【発明の実施の形態】次に、本発明に係る等速ジョイン
トについて好適な実施の形態を挙げ、添付の図面を参照
しながら以下詳細に説明する。図１において参照符号３
０は、本発明の第１の実施の形態に係る等速ジョイント
を示し、この等速ジョイント３０は、図示しない駆動軸
の一端部に一体的に連結されて開口部を有する筒状のア
ウタカップ（アウタ部材）３２と、従動軸３４の一端部
に固着されてアウタカップ３２の孔部内に収納されるイ
ンナ部材３６とから基本的に構成される。BEST MODE FOR CARRYING OUT THE INVENTION Next, preferred embodiments of a constant velocity joint according to the present invention will be described in detail below with reference to the accompanying drawings. Reference numeral 3 in FIG.
Reference numeral 0 indicates a constant velocity joint according to the first embodiment of the present invention, and this constant velocity joint 30 is a tubular outer cup (which is integrally connected to one end of a drive shaft (not shown) and has an opening. The outer member 32 and an inner member 36 fixed to one end of the driven shaft 34 and housed in the hole of the outer cup 32.

【００１４】前記アウタカップ３２の内周面には、軸線
方向に沿って延在し、軸心の回りにそれぞれ１２０度の
間隔をおいて３本のトラック溝３８ａ〜３８ｃ（但し、
３８ｂ、３８ｃは図示せず）が画成される。各トラック
溝３８ａ（３８ｂ、３８ｃ）は、フラットに形成された
平面部４０と、後述するローラアウタに摺接し相互に対
向する湾曲面からなるローラ案内溝４４とから構成され
る。なお、前記アウタカップ３２の開口部は、図示しな
い可撓性ブーツによって閉塞される。On the inner peripheral surface of the outer cup 32, three track grooves 38a to 38c (provided that they extend along the axial direction and are spaced 120 degrees around the axis respectively).
38b and 38c are not shown). Each track groove 38a (38b, 38c) is composed of a flat portion 40 formed flat and a roller guide groove 44 formed of a curved surface which is in sliding contact with a roller outer to be described later and faces each other. The opening of the outer cup 32 is closed by a flexible boot (not shown).

【００１５】図２に示されるように、従動軸３４にはリ
ング状のスパイダ４６が外嵌され、前記スパイダ４６の
外周面には、それぞれトラック溝３８ａ（３８ｂ、３８
ｃ）に向かって膨出し軸心の回りに１２０度の間隔をお
いて３本のスパイダ軸４８ａ（４８ｂ、４８ｃ）が固着
される。各スパイダ軸４８ａ（４８ｂ、４８ｃ）は、従
動軸３４の軸線と略直交する方向に沿って相互に対向す
る第１球面部５０ａ、５０ｂ（図１参照）と、前記軸線
方向に沿って相互に対向する平面部５２ａ、５２ｂ（図
４参照）とを有する。なお、前記第１球面部５０ａ、５
０ｂと平面部５２ａ、５２ｂとの境界部分には、面取り
部５４が形成されている（図２参照）。As shown in FIG. 2, a ring-shaped spider 46 is fitted onto the driven shaft 34, and track grooves 38a (38b, 38) are formed on the outer peripheral surface of the spider 46, respectively.
The three spider shafts 48a (48b, 48c) are fixed at intervals of 120 degrees around the bulging shaft center toward c). The spider shafts 48a (48b, 48c) and the first spherical surface portions 50a, 50b (see FIG. 1) that face each other along a direction substantially orthogonal to the axis of the driven shaft 34, and mutually along the axial direction. It has the plane parts 52a and 52b (refer FIG. 4) which oppose. Incidentally, the first spherical surface portions 50a, 5
A chamfered portion 54 is formed at the boundary between 0b and the flat portions 52a and 52b (see FIG. 2).

【００１６】前記スパイダ軸４８ａの外周面には円筒状
のローラインナ（内側ローラ）５６が外嵌され、前記ロ
ーラインナ５６の内壁面には、前記第１球面部５０ａ、
５０ｂに対応する第２球面部５８ａ、５８ｂ（図１参
照）と、周面部６０ａ、６０ｂ（図４参照）とが形成さ
れる。この場合、前記スパイダ軸４８ａの第１球面部５
０ａ、５０ｂとローラインナ５６の第２球面部５８ａ、
５８ｂとはそれぞれ接触して形成され、一方、該スパイ
ダ軸４８ａの平面部５２ａ、５２ｂとローラインナ５６
の周面部６０ａ、６０ｂとの間には、間隙６１が画成さ
れている（図３参照）。A cylindrical row liner (inner roller) 56 is externally fitted to the outer peripheral surface of the spider shaft 48a, and the inner wall surface of the row liner 56 has the first spherical surface portion 50a,
Second spherical surfaces 58a and 58b (see FIG. 1) corresponding to 50b and peripheral surface portions 60a and 60b (see FIG. 4) are formed. In this case, the first spherical surface portion 5 of the spider shaft 48a
0a, 50b and the second spherical surface portion 58a of the row liner 56,
58b are formed in contact with each other, while the flat portions 52a and 52b of the spider shaft 48a and the row liner 56 are formed.
A gap 61 is defined between the peripheral surface portions 60a and 60b (see FIG. 3).

【００１７】前記ローラインナ５６の第２球面部５８
ａ、５８ｂの上部には略円弧状の溝部が形成され、前記
溝部に略リング状の回り止め部材６２が嵌着される。こ
の回り止め部材６２には、下方側に向かって所定長だけ
突出する断面略コの字状の係止部６４ａ、６４ｂ（図２
並びに図３参照）が相互に対向して形成される。前記ロ
ーラインナ５６の外周部には複数のニードルベアリング
６６を介してローラアウタ（外側ローラ）６８が外嵌さ
れ、前記ローラアウタ６８の外周面は、ローラ案内溝４
４の断面形状に対応する曲線状に形成される。各ニード
ルベアリング６６はローラアウタ６８の内壁面に形成さ
れた環状凹部（環状溝）７０内に保持され、前記ローラ
インナ５６は、ニードルベアリング６６の長手方向に沿
って上下方向に摺動自在に形成される（図４および図５
参照）。The second spherical surface portion 58 of the row liner 56.
Substantially arcuate groove portions are formed in the upper portions of a and 58b, and a substantially ring-shaped detent member 62 is fitted in the groove portions. The detent member 62 has locking portions 64a and 64b (see FIG. 2) that have a substantially U-shaped cross section and project downward by a predetermined length.
And (see FIG. 3) are formed facing each other. A roller outer (outer roller) 68 is fitted onto the outer peripheral portion of the row liner 56 via a plurality of needle bearings 66, and the outer peripheral surface of the roller outer 68 has a roller guide groove 4
4 is formed in a curved shape corresponding to the sectional shape of 4. Each needle bearing 66 is held in an annular recess (annular groove) 70 formed on the inner wall surface of the roller outer 68, and the row liner 56 is formed so as to be vertically slidable along the longitudinal direction of the needle bearing 66. (Figs. 4 and 5
reference).

【００１８】ローラアウタ６８はローラ案内溝４４に摺
接して図１の矢印方向並びに図４の左右方向に摺動自在
に設けられ、前記ローラアウタ６８の上部側端部７２が
トラック溝３８ａの平面部４０に当接することにより該
ローラアウタ６８の傾斜角度が規制される。本発明の第
１の実施の形態に係る等速ジョイント３０は、基本的に
は以上のように構成されるものであり、次に、その動作
並びに作用効果について説明する。The roller outer 68 is slidably in contact with the roller guide groove 44 so as to be slidable in the arrow direction in FIG. 1 and in the left and right direction in FIG. 4. The upper end 72 of the roller outer 68 is the flat surface portion 40 of the track groove 38a. The contact angle with the roller outer 68 regulates the inclination angle of the roller outer 68. The constant velocity joint 30 according to the first embodiment of the present invention is basically configured as described above. Next, its operation and action and effect will be described.

【００１９】図示しない駆動軸が回転すると、その回転
力はアウタカップ３２を介してインナ部材３６に伝達さ
れ、スパイダ軸４８ａ〜４８ｃを通じて従動軸３４が所
定方向に回転する。すなわち、アウタカップ３２の回転
力は、トラック溝３８ａ（３８ｂ、３８ｃ）に摺動する
ローラアウタ６８、前記ローラアウタ６８に保持される
ニードルベアリング６６およびローラインナ５６を介し
てスパイダ軸４８ａ（４８ｂ、４８ｃ）に伝達され、前
記スパイダ軸４８ａ（４８ｂ、４８ｃ）に係合する従動
軸３４が回転する。When a drive shaft (not shown) rotates, its rotational force is transmitted to the inner member 36 via the outer cup 32, and the driven shaft 34 rotates in a predetermined direction through the spider shafts 48a to 48c. That is, the rotational force of the outer cup 32 is transmitted to the spider shaft 48a (48b, 48c) via the roller outer 68 sliding in the track grooves 38a (38b, 38c), the needle bearing 66 held by the roller outer 68, and the row liner 56. Then, the driven shaft 34 that engages with the spider shaft 48a (48b, 48c) rotates.

【００２０】この場合、駆動軸あるいは従動軸３４が傾
斜すると、ローラアウタがトラック溝３８ａ〜３８ｃに
沿って転動する。このため、駆動軸の回転速度はアウタ
カップ３２に対する従動軸３４の傾斜角度に影響される
ことなく、常時、一定の回転速度で従動軸３４に伝達さ
れる。ここで、ローラアウタ６８がトラック溝３８ａ
（３８ｂ、３８ｃ）から所定角度傾斜した場合、前記ロ
ーラアウタ６８はローラ案内溝４４に沿って図１に示す
矢印方向に摺動し、その結果、前記ローラアウタ６８の
上部側端部７２がトラック溝３８ａ（３８ｂ、３８ｃ）
の平面部４０に当接して該ローラアウタ６８の傾斜角度
を規制する。また、図５に示されるように、従動軸３４
が上下方向に向かって所定角度傾斜した場合も同様に、
ローラアウタ６８の上部側端部７２がトラック溝３８ａ
（３８ｂ、３８ｃ）の平面部４０に当接して該ローラア
ウタ６８の傾斜角度を規制する。In this case, when the drive shaft or the driven shaft 34 is inclined, the roller outer rolls along the track grooves 38a to 38c. Therefore, the rotation speed of the drive shaft is always transmitted to the driven shaft 34 at a constant rotation speed without being influenced by the inclination angle of the driven shaft 34 with respect to the outer cup 32. Here, the roller outer 68 is located in the track groove 38a.
When tilted at a predetermined angle from (38b, 38c), the roller outer 68 slides in the direction of the arrow shown in FIG. 1 along the roller guide groove 44, and as a result, the upper end 72 of the roller outer 68 is moved to the track groove 38a. (38b, 38c)
It contacts the flat surface portion 40 of the above and regulates the inclination angle of the roller outer 68. Further, as shown in FIG. 5, the driven shaft 34
Similarly, when is tilted by a predetermined angle in the vertical direction,
The upper end 72 of the roller outer 68 has the track groove 38a.
It abuts the flat surface portion 40 of (38b, 38c) to regulate the inclination angle of the roller outer 68.

【００２１】このように、トラック溝３８ａ（３８ｂ、
３８ｃ）に対するローラアウタ６８の傾斜角度の規制
は、該ローラアウタ６８の上部側端部７２によって直接
行われるため、図９に示されるホルダ９と上面部１３と
の間のクリアランス管理並びにローラガイド溝３ａ（３
ｂ、３ｃ）の精度管理をする必要がなく、簡便に製造す
ることが可能となる。In this way, the track grooves 38a (38b,
38c), the inclination angle of the roller outer 68 is regulated directly by the upper end 72 of the roller outer 68, and therefore the clearance between the holder 9 and the upper surface 13 shown in FIG. 9 and the roller guide groove 3a ( Three
It is not necessary to control the accuracy of (b, 3c), and it is possible to easily manufacture.

【００２２】また、ローラアウタ６８とローラインナ５
６との間に介装されるニードルベアリング６６によっ
て、アウタカップ３２側からスパイダ軸４８ａ（４８
ｂ、４８ｃ）側に振動が伝達されることを阻止すること
ができる。このため、良好な振動遮断特性を得ることが
できる。さらに、スパイダ軸４８ａ（４８ｂ、４８ｃ）
の軸線を回転軸としてローラインナ５６が球面部５０
ａ、５０ｂに沿って回転した場合、前記ローラインナ５
６に内接された係止部６４ａ、６４ｂが面取り部５４に
接触して、該ローラインナ５６の回り止めの機能を発揮
する。このため、前記ローラインナ５６は、前記係止部
６４ａ、６４ｂによって図３の矢印方向に９０度回転す
ることが阻止されるため、スパイダ軸４８ａ（４８ｂ、
４８ｃ）からの脱抜を防止することができる。Further, the roller outer 68 and the row liner 5
The needle bearing 66 interposed between the spider shaft 48a and the spider shaft 48a (48
It is possible to prevent the vibration from being transmitted to the (b, 48c) side. Therefore, good vibration isolation characteristics can be obtained. Furthermore, spider shaft 48a (48b, 48c)
With the axis of the rotation axis as the rotation axis, the row liner 56
When rotating along a and 50b, the row liner 5
The locking portions 64a and 64b inscribed in 6 contact the chamfered portion 54 to exert the function of preventing the row liner 56 from rotating. Therefore, the row liner 56 is prevented from rotating by 90 degrees in the arrow direction of FIG. 3 by the locking portions 64a and 64b, so that the spider shaft 48a (48b,
It is possible to prevent withdrawal from 48c).

【００２３】さらにまた、図９に示す第１の従来技術と
比較して、本実施の形態ではニードルベアリング６６を
保持するサークリップおよびワッシャを設ける必要がな
いため、構造が簡素化されて部品点数が減少し廉価に製
造することができるとともに、小型・軽量化を図ること
が可能となる。この場合、スパイダ軸４８ａ（４８ｂ、
４８ｃ）の平面部５２ａ、５２ｂとローラインナ５６の
周面部６０ａ、６０ｂとの間に間隙６１が画成されると
ともに、ローラインナ５６がニードルベアリング６６の
長手方向（上下方向）に沿って摺動変位自在に設けられ
ているため、従動軸３４の作動角を大きくすることがで
きる（図５参照）。前記間隙６１を介してスパイダ軸４
８ａ（４８ｂ、４８ｃ）とローラインナ５６との摺動部
位にグリスが進入しやすいため、潤滑性に優れ耐久性が
向上した等速ジョイント３０を得ることができる。Furthermore, as compared with the first prior art shown in FIG. 9, in the present embodiment, since it is not necessary to provide the circlip and the washer for holding the needle bearing 66, the structure is simplified and the number of parts is reduced. Can be manufactured at low cost, and can be made smaller and lighter. In this case, the spider shaft 48a (48b,
48c) has a gap 61 defined between the flat surface portions 52a and 52b and the peripheral surface portions 60a and 60b of the row liner 56, and the row liner 56 can be slidably displaced along the longitudinal direction (vertical direction) of the needle bearing 66. Since it is provided in the drive shaft 34, the operating angle of the driven shaft 34 can be increased (see FIG. 5). Spider shaft 4 through the gap 61
Since grease easily enters the sliding portion between the 8a (48b, 48c) and the row liner 56, the constant velocity joint 30 having excellent lubricity and improved durability can be obtained.

【００２４】またさらに、本実施の形態では、ニードル
ベアリング６６を保持するサークリップおよびワッシャ
を設けていないため、ニードルベアリング６６の長手方
向の寸法を従来技術に比較して伸張することが可能とな
る。このため、ニードルベアリング６６のゆがみ（Ｓｋ
ｅｗ）を防止し、ローラインナ５６をニードルベアリン
グ６６に沿って円滑に摺動させることができる。Further, in the present embodiment, since the circlip and the washer for holding the needle bearing 66 are not provided, it is possible to extend the dimension of the needle bearing 66 in the longitudinal direction as compared with the prior art. . Therefore, the distortion of the needle bearing 66 (Sk
ew) can be prevented and the row liner 56 can be slid smoothly along the needle bearing 66.

【００２５】次に、本発明の第２の実施の形態に係る等
速ジョイント８０を図６に示す。なお、本実施の形態で
は、以下の点で図１に示す等速ジョイント３０と異なる
ものであり、その他の同一の構成要素には同一の参照符
号を付して説明する。本実施の形態に係る等速ジョイン
ト８０では、円柱状に形成されたスパイダ軸８２ａ（８
２ｂ、８２ｃ）に対して外周面が球面状に形成されたカ
ラー８４を嵌入し、前記スパイダ軸８２ａ（８２ｂ、８
２ｃ）に画成された環状溝に嵌着されたサークリップ８
６によって前記カラー８４を係止し且つ抜脱を防止して
いる。Next, FIG. 6 shows a constant velocity joint 80 according to a second embodiment of the present invention. The present embodiment is different from the constant velocity joint 30 shown in FIG. 1 in the following points, and other same components will be described with the same reference numerals. In the constant velocity joint 80 according to the present embodiment, the spider shaft 82a (8
2b, 82c), a collar 84 having an outer peripheral surface formed into a spherical shape is fitted, and the spider shaft 82a (82b, 8c) is inserted.
Circlip 8 fitted in the annular groove defined in 2c)
6 locks the collar 84 and prevents it from coming off.

【００２６】なお、ローラインナ８８の内壁面は、図７
Ａに示されるように、カラー８４の外周面に対応してそ
の断面が曲線状に形成され、また、ローラインナ８８の
内周面の下部には相互に対向する一組の切欠部８９ａ、
８９ｂが形成される。組み付けに際しては、前記切欠部
８９ａ、８９ｂを介してカラー８４をローラインナ８８
の内壁面に挿入し約９０度回転させた後、前記カラー８
４にスパイダ軸８２ａ（８２ｂ、８２ｃ）を嵌入し、さ
らに、スパイダ軸８２ａ（８２ｂ、８２ｃ）にサークリ
ップ８６を嵌着してカラー８４を係止することができ
る。The inner wall surface of the row liner 88 is shown in FIG.
As shown in A, the cross-section is formed in a curved shape corresponding to the outer peripheral surface of the collar 84, and a pair of cutouts 89a facing each other is formed in the lower portion of the inner peripheral surface of the row liner 88.
89b is formed. At the time of assembling, the collar 84 is mounted on the collar 84 through the notches 89a and 89b.
After inserting into the inner wall of the and rotating it about 90 degrees,
The spider shafts 82a (82b, 82c) can be fitted into the spider 4, and the circlip 86 can be further fitted into the spider shafts 82a (82b, 82c) to lock the collar 84.

【００２７】次に、第３の実施の形態に係る等速ジョイ
ント９０を図８に示す。本実施の形態に係る等速ジョイ
ント９０は、図６に示す等速ジョイント８０と比較して
スパイダ軸８２ａ（８２ｂ、８２ｃ）に対するカラー８
４の係止方法が異なる。すなわち、図６に示す等速ジョ
イント８０では、サークリップ８６によってカラー８４
を係止しているのに対し、本実施の形態に係る等速ジョ
イント９０では、スパイダ軸８２ａ（８２ｂ、８２ｃ）
の頭部９２をかしめることによりカラー８４を係止して
いる点で異なる。Next, FIG. 8 shows a constant velocity joint 90 according to the third embodiment. The constant velocity joint 90 according to the present embodiment is different from the constant velocity joint 80 shown in FIG. 6 in that the collar 8 for the spider shaft 82a (82b, 82c) is provided.
The locking method of 4 is different. That is, in the constant velocity joint 80 shown in FIG.
In contrast to this, in the constant velocity joint 90 according to the present embodiment, the spider shaft 82a (82b, 82c) is locked.
The difference is that the collar 84 is locked by caulking the head 92 of the.

【００２８】なお、第２および第３の実施の形態に係る
等速ジョイント８０、９０の作用効果は、第１の実施の
形態に係る等速ジョイント３０と同一であることから、
その詳細な説明を省略する。Since the constant velocity joints 80 and 90 according to the second and third embodiments have the same operational effects as the constant velocity joint 30 according to the first embodiment,
A detailed description thereof will be omitted.

【００２９】[0029]

【発明の効果】本発明に係る等速ジョイントによれば、
以下の効果が得られる。すなわち、内側ローラ部材がニ
ードルベアリングの長手方向に沿って摺動自在に設けら
れているため、従動軸の作動角を大きくすることが可能
となる。また、内側ローラ部材と外側ローラ部材との間
に介装されるニードルベアリングによってアウタ部材か
らスパイダ軸側に振動が伝達されることが阻止され、良
好な振動遮断特性を得ることができる。According to the constant velocity joint of the present invention,
The following effects can be obtained. That is, since the inner roller member is provided slidably along the longitudinal direction of the needle bearing, the working angle of the driven shaft can be increased. Further, the needle bearing interposed between the inner roller member and the outer roller member prevents the vibration from being transmitted from the outer member to the spider shaft side, so that good vibration isolation characteristics can be obtained.

【００３０】さらに、本発明では、ニードルベアリング
を保持するサークリップおよびワッシャを設ける必要が
ないため、構造が簡素化されて部品点数が減少し廉価に
製造することができる。従って、小型・軽量化された等
速ジョイントを得ることができる。Further, according to the present invention, since it is not necessary to provide the circlip and the washer for holding the needle bearing, the structure is simplified, the number of parts is reduced, and the manufacturing cost can be reduced. Therefore, it is possible to obtain a compact and lightweight constant velocity joint.

【図面の簡単な説明】[Brief description of the drawings]

【図１】本発明の第１の実施の形態に係る等速ジョイン
トの部分断面図である。FIG. 1 is a partial cross-sectional view of a constant velocity joint according to a first embodiment of the present invention.

【図２】図１に示す等速ジョイントを構成するインナ部
材の分割斜視図である。2 is a divided perspective view of an inner member constituting the constant velocity joint shown in FIG. 1. FIG.

【図３】図１に示す等速ジョイントを構成するインナ部
材の平面図である。3 is a plan view of an inner member forming the constant velocity joint shown in FIG. 1. FIG.

【図４】図１のＩＶ−ＩＶ線に沿った部分断面図であ
る。FIG. 4 is a partial cross-sectional view taken along the line IV-IV of FIG.

【図５】図４に示す状態において、従動軸が下方側に所
定角度傾斜した状態の説明図である。5 is an explanatory view of a state where the driven shaft is inclined downward by a predetermined angle in the state shown in FIG.

【図６】本発明の第２の実施の形態に係る等速ジョイン
トの部分断面図である。FIG. 6 is a partial sectional view of a constant velocity joint according to a second embodiment of the present invention.

【図７】図７Ａは、図６に示す等速ジョイントを構成す
るローラインナの中央縦断面図、図７Ｂは、図６に示す
等速ジョイントを構成するローラインナの底面図であ
る。7A is a central longitudinal sectional view of a row liner forming the constant velocity joint shown in FIG. 6, and FIG. 7B is a bottom view of the row liner forming the constant velocity joint shown in FIG.

【図８】本発明の第３の実施の形態に係る等速ジョイン
トの部分断面図である。FIG. 8 is a partial cross-sectional view of a constant velocity joint according to a third embodiment of the present invention.

【図９】第１の従来技術に係る等速ジョイントの部分断
面図である。FIG. 9 is a partial sectional view of a constant velocity joint according to a first conventional technique.

【図１０】第２の従来技術に係る等速ジョイントの部分
断面図である。FIG. 10 is a partial sectional view of a constant velocity joint according to a second conventional technique.

【符号の説明】[Explanation of symbols]

３０、８０、９０…等速ジョイント ３２…アウタ
カップ ３４…従動軸 ３６…インナ
部材 ４６…スパイダ ４８ａ〜４８
ｃ…スパイダ軸 ５６…ローラインナ ６２…回り止
め部材 ６４ａ、６４ｂ…係止部 ６６…ニード
ルベアリング ６８…ローラアウタ ７２…上部側
端部30, 80, 90 ... Constant velocity joint 32 ... Outer cup 34 ... Driven shaft 36 ... Inner member 46 ... Spider 48a-48
c ... Spider shaft 56 ... Row liner 62 ... Rotation stop member 64a, 64b ... Locking portion 66 ... Needle bearing 68 ... Roller outer 72 ... Upper end

───────────────────────────────────────────────────── フロントページの続き (72)発明者 茅野 健 栃木県真岡市松山町19 本田技研工業株式 会社栃木製作所内 (72)発明者 川勝 勉 栃木県真岡市松山町19 本田技研工業株式 会社栃木製作所内 (72)発明者 小倉 尚宏 栃木県真岡市松山町19 本田技研工業株式 会社栃木製作所内 (72)発明者 中尾 彰一 栃木県真岡市松山町19 本田技研工業株式 会社栃木製作所内 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Ken Chino 19 In Tochigi Works, Honda Motor Co., Ltd. Matsuyama-cho, Moka-shi, Tochigi Prefecture (72) Inventor Tsutomu Kawakatsu 19 Matsuyama-machi, Moka-shi, Tochigi Honda Co., Ltd. Tochigi Co., Ltd. (72) Inventor Naohiro Ogura 19 Tochigi Plant, Honda Motor Co., Ltd. 19 Matsuyama Town, Moka City, Tochigi Prefecture (72) Inventor Shoichi Nakao 19 Matsuyama Town, Moka City, Tochigi Prefecture Tochigi Co., Ltd.

Claims (3)

【特許請求の範囲】[Claims] 【請求項１】所定間隔離間し軸線方向に沿って延在する
複数のトラック溝が内周面に設けられ、一方の伝導軸に
連結される筒状のアウタ部材と、前記アウタ部材の開口
する内空部内に挿入されて他方の伝導軸に連結されるイ
ンナ部材とを有する等速ジョイントにおいて、 前記トラック溝の方向に沿って膨出するスパイダ軸と、 前記スパイダ軸に外嵌される内側ローラ部材と、 前記内側ローラ部材と非接触状態に形成され、前記トラ
ック溝に沿って摺動変位する外側ローラ部材と、 前記内側ローラ部材と外側ローラ部材との間に介装され
るニードルベアリングと、 を備え、前記内側ローラ部材は、前記ニードルベアリン
グの長手方向に沿って前記スパイダ軸と一体的に摺動自
在に形成されることを特徴とする等速ジョイント。1. A cylindrical outer member having a plurality of track grooves, which are spaced from each other by a predetermined distance and extend along the axial direction, are provided on an inner peripheral surface, and are connected to one of the conductive shafts, and the outer member is opened. A constant velocity joint having an inner member that is inserted into the inner space and connected to the other transmission shaft, wherein a spider shaft that bulges along the direction of the track groove and an inner roller that is externally fitted to the spider shaft. A member, an outer roller member which is formed in a non-contact state with the inner roller member and is slidably displaced along the track groove, and a needle bearing which is interposed between the inner roller member and the outer roller member, The constant velocity joint, wherein the inner roller member is formed so as to be slidable integrally with the spider shaft along the longitudinal direction of the needle bearing. 【請求項２】請求項１記載の等速ジョイントにおいて、
ニードルベアリングは、外側ローラの内周面に画成され
た環状溝に保持されることを特徴とする等速ジョイン
ト。2. The constant velocity joint according to claim 1,
The needle bearing is held in an annular groove defined on the inner peripheral surface of the outer roller, which is a constant velocity joint. 【請求項３】請求項１または２記載の等速ジョイントに
おいて、外側ローラ部材の頂部は、内側ローラ部材の頂
部よりもトラック溝側に突出して形成され、前記外側ロ
ーラ部材の頂部が前記トラック溝に当接することにより
該外側ローラ部材の傾斜角度を規制する機能を営むこと
を特徴とする等速ジョイント。3. The constant velocity joint according to claim 1, wherein the top portion of the outer roller member is formed so as to project toward the track groove side more than the top portion of the inner roller member, and the top portion of the outer roller member is formed in the track groove. A constant velocity joint having a function of restricting an inclination angle of the outer roller member by abutting against the outer roller member.
JP7288891A 1995-11-07 1995-11-07 Constant velocity joint Pending JPH09133145A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP7288891A JPH09133145A (en) 1995-11-07 1995-11-07 Constant velocity joint

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP7288891A JPH09133145A (en) 1995-11-07 1995-11-07 Constant velocity joint

Publications (1)

Publication Number Publication Date
JPH09133145A true JPH09133145A (en) 1997-05-20

Family

ID=17736121

Family Applications (1)

Application Number Title Priority Date Filing Date
JP7288891A Pending JPH09133145A (en) 1995-11-07 1995-11-07 Constant velocity joint

Country Status (1)

Country Link
JP (1) JPH09133145A (en)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002147482A (en) * 2000-10-16 2002-05-22 Delphi Technologies Inc Tripod type constant velocity joint
JP2002266888A (en) * 2001-03-08 2002-09-18 Honda Motor Co Ltd Constant velocity joint
FR2869965A1 (en) * 2004-05-10 2005-11-11 Gkn Driveline Sa Sa BEARING ASSEMBLY AND CORRESPONDING HOMOCINETIC SEAL
WO2011074449A1 (en) * 2009-12-15 2011-06-23 本田技研工業株式会社 Constant velocity joint

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002147482A (en) * 2000-10-16 2002-05-22 Delphi Technologies Inc Tripod type constant velocity joint
JP2002266888A (en) * 2001-03-08 2002-09-18 Honda Motor Co Ltd Constant velocity joint
FR2869965A1 (en) * 2004-05-10 2005-11-11 Gkn Driveline Sa Sa BEARING ASSEMBLY AND CORRESPONDING HOMOCINETIC SEAL
US7476156B2 (en) 2004-05-10 2009-01-13 Gkn Driveline International Gmbh Homokinetic joint
WO2011074449A1 (en) * 2009-12-15 2011-06-23 本田技研工業株式会社 Constant velocity joint
CN102656381A (en) * 2009-12-15 2012-09-05 本田技研工业株式会社 Constant velocity joint

Similar Documents

Publication Publication Date Title
US5069653A (en) Tripot type constant velocity universal joint
US7654908B2 (en) Tripod type constant velocity universal joint
US5391013A (en) Tripod joint
EP0861992B1 (en) Constant velocity universal joint
JPH0310808B2 (en)
JP3043280B2 (en) Constant velocity joint
US6764406B2 (en) Constant velocity joint of tripod type
JPH03144118A (en) Constant-velocity joint
US6328669B1 (en) Toroidal type continuously variable transmission
JPH09133145A (en) Constant velocity joint
US20040248656A1 (en) Tripod constant velocity universal joint
US7118484B2 (en) Cross joint
US7695371B2 (en) Constant velocity joint
JP3204427B2 (en) Tripod type constant velocity joint
JP3875030B2 (en) Constant velocity universal joint
JP2957121B2 (en) Constant velocity joint
JPH01250619A (en) Equi-velocity joint
JPH09133147A (en) Constant velocity joint
JP3949865B2 (en) Constant velocity universal joint
JP2002213478A (en) Constant velocity universal joint
JP4064067B2 (en) Constant velocity joint
JP3913380B2 (en) Constant velocity joint and its assembly method
JPH0235052Y2 (en)
JPH10311344A (en) Uniform joint
JP4026679B2 (en) Constant velocity joint

Legal Events

Date Code Title Description
A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20040824

A02 Decision of refusal

Free format text: JAPANESE INTERMEDIATE CODE: A02

Effective date: 20041221