JPH031529B2 - - Google Patents
Info
- Publication number
- JPH031529B2 JPH031529B2 JP62021613A JP2161387A JPH031529B2 JP H031529 B2 JPH031529 B2 JP H031529B2 JP 62021613 A JP62021613 A JP 62021613A JP 2161387 A JP2161387 A JP 2161387A JP H031529 B2 JPH031529 B2 JP H031529B2
- Authority
- JP
- Japan
- Prior art keywords
- outer ring
- roller
- ring
- roller guide
- spherical
- 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.)
- Expired - Lifetime
Links
- 230000002093 peripheral effect Effects 0.000 claims description 16
- 230000033001 locomotion Effects 0.000 description 8
- 238000010586 diagram Methods 0.000 description 5
- 238000005096 rolling process Methods 0.000 description 5
- 230000000694 effects Effects 0.000 description 3
- 230000020169 heat generation Effects 0.000 description 2
- 238000005452 bending Methods 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000004519 grease Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/30—Arrangement or mounting of transmissions in vehicles the ultimate propulsive elements, e.g. ground wheels, being steerable
-
- 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
-
- 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
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S464/00—Rotary shafts, gudgeons, housings, and flexible couplings for rotary shafts
- Y10S464/904—Homokinetic coupling
- Y10S464/905—Torque transmitted via radially extending pin
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Support Of The Bearing (AREA)
- Forging (AREA)
- Pivots And Pivotal Connections (AREA)
Description
【発明の詳細な説明】
〔産業上の利用分野〕
この発明は、主として前輪駆動式の自動車に適
用される等速自在継手に関し、特にトリポード型
等速自在継手に関するものである。DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a constant velocity universal joint mainly applied to front-wheel drive automobiles, and particularly to a tripod type constant velocity universal joint.
この種、従来の等速自在継手として、例えば第
１０図に示すように、外輪１の内面に軸方向の３
本の円筒形トラツク溝２を形成し、その外輪１の
内側に配置したトリポード部材３に半径方向の脚
軸４を突設し、各脚軸４の外側に球面ローラ５を
回転可能に、且つ軸方向にスライド可能に嵌合
し、その球面ローラ５を上記トラツク溝２の両側
のローラ案内面６に係合されたものが知られてい
る。
As a conventional constant velocity universal joint of this kind, for example, as shown in FIG.
A cylindrical track groove 2 is formed, a radial leg shaft 4 is provided protruding from a tripod member 3 disposed inside the outer ring 1, and a spherical roller 5 is rotatably provided on the outside of each leg shaft 4. It is known that the rollers are fitted so as to be slidable in the axial direction, and the spherical rollers 5 are engaged with the roller guide surfaces 6 on both sides of the track groove 2.
上記トリポード型等速自在継手において、外輪
１とトリポード部材３とが作動角をとる状態で回
動力を伝達する場合を考えると、各球面ローラ５
と円筒形トラツク溝２のローラ案内面６とは、第
１０図及び第１１図に示すように互いに斜交する
関係となり、球面ローラ５に正しい転がり運動を
させることはできない。 In the tripod type constant velocity universal joint described above, considering the case where the rotational force is transmitted in a state where the outer ring 1 and the tripod member 3 take an operating angle, each spherical roller 5
The roller guide surface 6 of the cylindrical track groove 2 and the roller guide surface 6 of the cylindrical track groove 2 are in an oblique relationship with each other as shown in FIGS. 10 and 11, and the spherical roller 5 cannot be caused to perform a correct rolling motion.
即ち、球面ローラ５は第１０図の矢印イで示す
方向に転がり移動しようとするのに対し、トラツ
ク溝２は円筒形であつて、外輪１の軸芯に平行で
あるため、球面ローラ５はトラツク溝２に拘束さ
れながら移動することになる。この結果トラツク
溝２のローラ案内面６と球面ローラ５相互間にお
いて、滑りが生じて発熱し、更にこの滑りが軸方
向のスラスト力を誘起し、振動発生の原因とな
る。 That is, the spherical roller 5 tries to roll and move in the direction shown by arrow A in FIG. 10, whereas the track groove 2 is cylindrical and parallel to the axis of the outer ring 1, It moves while being restrained by the track groove 2. As a result, sliding occurs between the roller guide surface 6 of the track groove 2 and the spherical roller 5, generating heat, and this slipping further induces a thrust force in the axial direction, causing vibration.
第１２図は継手の位相角と誘起スラスト力との
関係を示すグラフである。 FIG. 12 is a graph showing the relationship between the phase angle of the joint and the induced thrust force.
この誘起スラスト力発生のメカニズムを第９図
によつて説明する。 The mechanism of generation of this induced thrust force will be explained with reference to FIG.
第９図は外輪１とトリポード部材３が作動角を
とる状態で回動力を伝達する場合の各部材の位置
関係を示す。 FIG. 9 shows the positional relationship of each member when rotating force is transmitted with the outer ring 1 and the tripod member 3 assuming an operating angle.
継手が回転すると、トリポード部材３の脚軸４
に嵌合された球面ローラ５が外輪ローラ案内面６
に拘束されながら外輪軸方向に往復運動を繰り返
す。このとき３個の各球面ローラ５は第９図に示
す如く、点Ｐから点P′、点Ｑから点Q′、点Ｒから
点R′へとそれぞれ摺動し、次いでその反対方向
へと方向を変え、継手の１回転でローラ案内面６
上を１往復する。このような運動をするローラ案
内面６と球面ローラ５間で、動力伝達継手として
当然のことながら作用している接触力により、軸
方向にスラスト力を誘起する。 When the joint rotates, the leg shaft 4 of the tripod member 3
The spherical roller 5 fitted to the outer ring roller guide surface 6
It repeats reciprocating motion in the axial direction of the outer ring while being restrained by. At this time, each of the three spherical rollers 5 slides from point P to point P', from point Q to point Q', and from point R to point R', as shown in FIG. 9, and then slides in the opposite direction. Change the direction and rotate the roller guide surface 6 with one rotation of the joint.
Make one round trip on the top. A thrust force is induced in the axial direction by the contact force that naturally acts as a power transmission joint between the roller guide surface 6 and the spherical roller 5 that move in this manner.
継手回転時にそれぞれの球面ローラ５によつて
発生するスラスト力の方向及びその大きさは回転
位相によつて変動し、第９図に示す如く２個の球
面ローラ５は、外輪１の左方向に、又１個の球面
ローラ５は右方向に夫々引張り、圧縮のスラスト
力を誘起させる。 The direction and magnitude of the thrust force generated by each spherical roller 5 when the joint rotates varies depending on the rotation phase, and as shown in FIG. , and one spherical roller 5 induces a pulling and compressing thrust force in the right direction, respectively.
このように３個の球面ローラ５により発生する
スラスト力の総和は第１２図に示すように継手１
回により３回の周期をもつて正逆変動し、その変
動の振幅が大きいことにより、自動車に種々の振
動問題を発生させている。 The total thrust force generated by the three spherical rollers 5 is as shown in FIG.
It fluctuates in forward and reverse directions with three cycles depending on the cycle, and the amplitude of the fluctuation is large, causing various vibration problems in automobiles.
この発明は、従来のトリポード型等速自在継手
の問題点を解決し、自在継手の誘起スラスト力を
軽減することにより、振動の発生を防止すること
を技術的課題としている。
The technical problem of this invention is to solve the problems of conventional tripod type constant velocity universal joints and to prevent the occurrence of vibration by reducing the thrust force induced in the universal joint.
上記の課題を解決するため、この発明は、トリ
ポード部材の脚軸に回転自在に挿嵌されるローラ
を内側リングと外側リングとで構成し、内側リン
グの外周面を脚軸の軸心に中心をもつ球面により
形成すると共に、外側リングの内周面を円筒面に
形成し、両リングを嵌合させて内側リングの外周
面と外側リングの内周面とを接触せしめ、かつ外
側リングが、外輪のローラ案内面によつて外輪の
軸線と平行に案内される外周面を有する。
In order to solve the above problems, the present invention comprises a roller that is rotatably inserted into the leg shaft of a tripod member and is composed of an inner ring and an outer ring, and the outer peripheral surface of the inner ring is centered around the axis of the leg shaft. The inner peripheral surface of the outer ring is formed as a cylindrical surface, and both rings are fitted to bring the outer peripheral surface of the inner ring into contact with the inner peripheral surface of the outer ring, and the outer ring has It has an outer circumferential surface that is guided parallel to the axis of the outer ring by the roller guide surface of the outer ring.
上記の構成から成る等速自在継手は、内側リン
グの外周面が完全な球面をなすので、外側リング
に対して自由な角度で回転しうると共に、外側リ
ングは常にトラツク溝の方向に正しく転動する。
これによりトリポード部材がどのような作動角を
とつても、外側リングは外輪の軸線と平行な姿勢
を維持しつつ正しく転動する。そのため、滑り抵
抗が減少し、継手り誘起スラスト力が軽減する。
In the constant velocity universal joint with the above configuration, the outer peripheral surface of the inner ring is a perfect spherical surface, so it can rotate at any angle relative to the outer ring, and the outer ring always rolls correctly in the direction of the track groove. do.
As a result, no matter what operating angle the tripod member takes, the outer ring correctly rolls while maintaining a posture parallel to the axis of the outer ring. Therefore, the sliding resistance is reduced and the joint-induced thrust force is reduced.
以下、この発明の実施例を添付図面に基づいて
説明する。
Embodiments of the present invention will be described below with reference to the accompanying drawings.
第１図乃至第５図は第１の実施例を示す。外輪
１０は従来の場合と同様に閉鎖端に第１軸１１が
一体に設けられ、また内周面に軸方向の３本のト
ラツク溝１２が中心軸のまわりに120度の間隔を
おいて形成されている。各トラツク溝１２は、両
側に２つのローラ案内面１３を有している。 1 to 5 show a first embodiment. The outer ring 10 has a first shaft 11 integrally provided at the closed end as in the conventional case, and three track grooves 12 in the axial direction are formed on the inner peripheral surface at intervals of 120 degrees around the central axis. has been done. Each track groove 12 has two roller guide surfaces 13 on both sides.
外輪１０の内部に挿入されるトリポード部材１
５は、第２軸１６の一端に形成したセレーシヨン
１７に形成されると共に、段部１８とクリツプ１
９との間で抜け止め状態に保持される。このトリ
ポード部材１５は、３本の脚軸２０を有し、この
脚軸２０のまわりに嵌合した内側リング２１及び
外側リング２２からなるローラは、回転自在に支
持されている。 Tripod member 1 inserted into the outer ring 10
5 is formed on the serration 17 formed at one end of the second shaft 16, and is formed on the step portion 18 and the clip 1.
9 to prevent it from coming off. This tripod member 15 has three leg shafts 20, and a roller consisting of an inner ring 21 and an outer ring 22 fitted around the leg shafts 20 is rotatably supported.
内側リング２１は、転動体２３を介して、脚軸
２０上に嵌合し、脚軸２０の軸方向には、移動し
ないようにトリポード部材５の肩部２６及びクリ
ツプ２７により保持されている。内側リング２１
の外周には脚軸２０の軸心に中心をもつ球面であ
る外周面（以下、球面状外周面という。）２４が
形成され、外側リング２２が外嵌されており、外
側リング２２の外周にはローラ案内面１３によつ
て案内される球面でなる外周面（以下、球面状内
周面という。）２５が形成されている。また内周
には円筒面でなる内周面（以下、円筒状内周面と
いう）２８が形成してあり、内側リング２１と外
側リング２２は球面状外周面２４と円筒状内周面
２８とによつて接触案内されている。 The inner ring 21 is fitted onto the leg shaft 20 via the rolling elements 23, and is held by the shoulder portion 26 of the tripod member 5 and the clip 27 so as not to move in the axial direction of the leg shaft 20. inner ring 21
An outer circumferential surface (hereinafter referred to as a spherical outer circumferential surface) 24, which is a spherical surface centered on the axis of the leg shaft 20, is formed on the outer circumference of the leg shaft 20, and an outer ring 22 is fitted on the outer circumference of the outer ring 22. A spherical outer circumferential surface (hereinafter referred to as a spherical inner circumferential surface) 25 is formed which is guided by the roller guide surface 13. Further, an inner circumferential surface (hereinafter referred to as a cylindrical inner circumferential surface) 28 which is a cylindrical surface is formed on the inner circumference, and the inner ring 21 and the outer ring 22 have a spherical outer circumferential surface 24 and a cylindrical inner circumferential surface 28. Contact information is provided by.
第３図は、第１の実施例において、継手が作動
角をとつた状態を示すもので、内側リング２１は
外側リング２２に対して傾斜し、かつ、外側リン
グ２２の円筒状内周面２８の中で下方へ相対移動
する。これにより両リング２１，２２の相対移動
を吸収する。外側リング２２は外輪１０のローラ
案内面１３によつて外輪１０の軸線と平行に案内
され、外側リング２２はローラ案内面１３上を正
しく転動し、滑り抵抗が軽減される。 FIG. 3 shows a state in which the joint assumes an operating angle in the first embodiment, in which the inner ring 21 is inclined with respect to the outer ring 22, and the cylindrical inner circumferential surface 28 of the outer ring 22 relative movement downward within. This absorbs the relative movement of both rings 21 and 22. The outer ring 22 is guided parallel to the axis of the outer ring 10 by the roller guide surface 13 of the outer ring 10, and the outer ring 22 rolls correctly on the roller guide surface 13, reducing slip resistance.
第４図は、内側リング２１と外側リング２２と
の相対移動を説明するための図である。作動角を
とらない時のトリポード部材１５の中心がＡであ
り、Ａは外輪１０の軸線Ｘ上にある。また、外側
リング２２は、ローラ案内面１３の中心線Ｂと一
致しており、かつ、内側リング２１の中心Ｃもロ
ーラ案内面１３の中心線Ｂ上にある。作動角θを
とると、トリポード部材１５の中心ＡはA′点に
移動し、軸線Ｘより下側にずれる。この結果、内
側リング２１は、外側リング２２に対して、傾斜
すると共に、内側リング２１の中心Ｃは外側リン
グ２２の中心面より下方の位置C′へと相対移動す
る。上記の相対移動は、外側リング２２の円筒状
内周面２８上を内側リング２１の球面状外周面２
４が転がりながら移動するような格好になり、移
動は滑らかである。 FIG. 4 is a diagram for explaining relative movement between the inner ring 21 and the outer ring 22. The center of the tripod member 15 when no operating angle is taken is A, and A is on the axis X of the outer ring 10. Further, the outer ring 22 is aligned with the center line B of the roller guide surface 13, and the center C of the inner ring 21 is also on the center line B of the roller guide surface 13. When the operating angle θ is taken, the center A of the tripod member 15 moves to point A' and is shifted downward from the axis X. As a result, the inner ring 21 is inclined with respect to the outer ring 22, and the center C of the inner ring 21 is relatively moved to a position C' below the center plane of the outer ring 22. The above relative movement moves the cylindrical inner circumferential surface 28 of the outer ring 22 onto the spherical outer circumferential surface 28 of the inner ring 21.
4 looks like it's rolling and moves smoothly.
第５図は、ローラ案内面１３、外側リング２２
及び内側スライド２１の接触状態を示す横断面図
である。内側リング２１の球面状外周面２４の曲
率半径R1及び外側リング２２の球面状外周面２
５の曲率半径R2の中心は共に脚軸２０の軸線上
に位置する。外輪１０のローラ案内面１３は、外
側リング２２の球面状外周面２５の曲率半径R2
よりも大きい曲率の２つの円筒面２９，３０で構
成されており、外側リング２２の球面状外周面２
５はローラ案内面１３と２点Ｄ，Ｅでアンギユ
ラ・コンタクトしている。このアンギユラ・コン
タクトにより、外側リング２２は、外輪１０の軸
線に平行に案内される。尚、ローラ案内面１３の
中央部はグリース溜まりとして有効である。 FIG. 5 shows the roller guide surface 13 and the outer ring 22.
FIG. 3 is a cross-sectional view showing the contact state of the inner slide 21. FIG. The radius of curvature R 1 of the spherical outer peripheral surface 24 of the inner ring 21 and the spherical outer peripheral surface 2 of the outer ring 22
The centers of the curvature radius R 2 of No. 5 are both located on the axis of the leg shaft 20. The roller guide surface 13 of the outer ring 10 has a radius of curvature R 2 of the spherical outer peripheral surface 25 of the outer ring 22.
It is composed of two cylindrical surfaces 29 and 30 with a larger curvature than the spherical outer peripheral surface 2 of the outer ring 22.
5 is in angular contact with the roller guide surface 13 at two points D and E. This angular contact guides the outer ring 22 parallel to the axis of the outer ring 10. Note that the center portion of the roller guide surface 13 is effective as a grease reservoir.
第６図は、第２の実施例を示す図であり、ロー
ラ案内面１３ａの形状及び外側リング２２ａの外
周面が第１の実施例と異なるだけで、他の構成は
第１実施例と同じである。 FIG. 6 is a diagram showing the second embodiment, and the only difference from the first embodiment is the shape of the roller guide surface 13a and the outer peripheral surface of the outer ring 22a, and the other configurations are the same as the first embodiment. It is.
ローラ案内面１３ａは、角度をもつて配置され
た２つの平面３１，３２とで構成され、これに対
応して、外側リング２２の外周面は２つ円錐面３
３，３４で形成されている。外側リング２２ａ
は、ローラ案内面１３ａの２つの平面３１，３２
と外側リング２２の円錐面３３，３４の接触によ
り、外輪１０の軸線に対して平行に案内される。 The roller guide surface 13a is composed of two flat surfaces 31 and 32 arranged at an angle, and correspondingly, the outer circumferential surface of the outer ring 22 has two conical surfaces 3.
3,34. Outer ring 22a
are the two planes 31 and 32 of the roller guide surface 13a.
Due to the contact between the conical surfaces 33 and 34 of the outer ring 22, the outer ring 22 is guided parallel to the axis of the outer ring 10.
第７図は、第３の実施例を示す。この実施例の
場合も、第１の実施例と比べ、ローラ案内面１３
ｂの形状及び外側リング２２ｂの外周面の形状が
異なるだけである。 FIG. 7 shows a third embodiment. Also in this embodiment, compared to the first embodiment, the roller guide surface 13
The only difference is the shape of b and the shape of the outer peripheral surface of the outer ring 22b.
ローラ案内面１３ｂは、平面で形成されてお
り、その両側に肩部３５，３６が形成されてい
る。外側リング２２ｂの外周には円筒面３７が形
成されており、両肩部３５，３６によつて両端が
案内され、これにより外輪１０の軸線に平行に転
動される。 The roller guide surface 13b is formed as a flat surface, and shoulders 35 and 36 are formed on both sides thereof. A cylindrical surface 37 is formed on the outer periphery of the outer ring 22b, and both ends are guided by both shoulders 35 and 36, thereby rolling in parallel to the axis of the outer ring 10.
第８図は、第４の実施例を示す。この実施例の
場合、外側リング２２ｃの外周には第１の実施例
と同様に球面状外周面２５ｃが形成されている。
その曲率半径R3は第１の実施例の場合の曲率半
径R2より小さく、脚軸２０の中心とローラ案内
面１３ｃ間の距離の約40％に設定される。 FIG. 8 shows a fourth embodiment. In this embodiment, a spherical outer circumferential surface 25c is formed on the outer periphery of the outer ring 22c, as in the first embodiment.
The radius of curvature R 3 is smaller than the radius of curvature R 2 in the first embodiment, and is set to about 40% of the distance between the center of the leg shaft 20 and the roller guide surface 13c.
ローラ案内面１３ｃは上記の曲率半径R3より
も大きい曲率の２つの円筒面２９ｃ，３０ｃで構
成されており、外側リング２２ｃの球面状外周面
２５ｃは約20度の接触角αをもつて２点Ｆ，Ｇで
アンギユラー・コンタクトしている。 The roller guide surface 13c is composed of two cylindrical surfaces 29c and 30c with a radius of curvature larger than the radius of curvature R3 , and the spherical outer peripheral surface 25c of the outer ring 22c has a contact angle α of about 20 degrees. There is angular contact at points F and G.
また、外側リング２２ｃの幅は内側リング２１
の幅より小さく形成されている。このように形成
すると、上記の各実施例の場合より外輪１０の外
径を小さく抑えることができる。また、ローラ案
内面１３ｃのトラツク溝１２側のコーナ部には、
外側リング２２ｃに沿つて突出した肩部３８が形
成され、これにより外側リング２２ｃの大きな振
れを規制する。 Furthermore, the width of the outer ring 22c is the same as that of the inner ring 21.
It is formed smaller than the width of. When formed in this way, the outer diameter of the outer ring 10 can be kept smaller than in the case of each of the above embodiments. In addition, at the corner portion of the roller guide surface 13c on the track groove 12 side,
A protruding shoulder 38 is formed along the outer ring 22c, thereby restricting large swings of the outer ring 22c.
以上のような構成にしたので、この発明は下記
のような効果を有する。
With the above configuration, the present invention has the following effects.
(イ) 外側リングが外輪の軸線方向と平行な姿勢を
維持しつつ正しく転動するので、滑り抵抗が低
く、発熱及び誘起スラスト力による振動を軽減
できる。(a) Since the outer ring rolls correctly while maintaining a posture parallel to the axial direction of the outer ring, slip resistance is low and vibrations due to heat generation and induced thrust force can be reduced.
(ロ) 外側リングと内側リングとの間の接触が円筒
状内周面と球面状外周面との接触であるため、
作動角をとつたときの両リングの相対移動及び
継手の屈曲作動がいずれも滑らかであり、内部
の摩擦及び発熱も少ない。(b) Since the contact between the outer ring and the inner ring is the contact between the cylindrical inner circumferential surface and the spherical outer circumferential surface,
When the operating angle is reached, the relative movement of both rings and the bending action of the joint are both smooth, and there is little internal friction and heat generation.
(ハ) 内側リング及び外側リングは形状が簡単であ
り、加工が容易で安価である。(c) The inner ring and outer ring have a simple shape, are easy to process, and are inexpensive.
第１図はこの発明に係る等速自在継手の第１の
実施例を示す縦断側面図、第２図は、同上の横断
面図、第３図は継手が作動角をとつたときの縦断
面、第４図は、作動角をとつたときの内側リング
及び外側リングの相対移動説明図、第５図は、第
１の実施例の一部拡大横断面図、第６図は第２の
実施例の一部拡大断面図、第７図は、第３の実施
例の一部拡大横断面図、第８図は、第４の実施例
の一部拡大横断面図、第９図は、従来の継手の作
動説明図、第１０図は従来の継手を示す縦断側面
図、第１１図は同上の球面ローラの転がり状態を
示す斜視図、第１２図は、各脚軸に於ける合成さ
れた誘起スラスト力を示すグラフである。
１０……外輪、１２……トラツク溝、１３，１
３ａ，１３ｂ，１３ｃ……ローラ案内面、１５…
…トリポード部材、２１……内側リング、２２，
２２ａ，２２ｂ，２２ｃ……外側リング。
Fig. 1 is a longitudinal cross-sectional side view showing a first embodiment of the constant velocity universal joint according to the present invention, Fig. 2 is a cross-sectional view of the same, and Fig. 3 is a longitudinal cross-section when the joint assumes an operating angle. , FIG. 4 is an explanatory diagram of the relative movement of the inner ring and outer ring when the operating angle is set, FIG. 5 is a partially enlarged cross-sectional view of the first embodiment, and FIG. 6 is a diagram of the second embodiment. FIG. 7 is a partially enlarged cross-sectional view of the third embodiment, FIG. 8 is a partially enlarged cross-sectional view of the fourth embodiment, and FIG. 9 is a partially enlarged cross-sectional view of the fourth embodiment. Fig. 10 is a vertical cross-sectional side view showing a conventional joint, Fig. 11 is a perspective view showing the rolling state of the spherical roller same as above, and Fig. 12 is a diagram illustrating the combined operation of each leg axis. It is a graph showing induced thrust force. 10...Outer ring, 12...Track groove, 13,1
3a, 13b, 13c...Roller guide surface, 15...
... Tripod member, 21 ... Inner ring, 22,
22a, 22b, 22c...outer ring.
Claims (1)
外輪の内側にトリポード部材を挿入し、該トリポ
ード部材の３本の脚軸にローラを回転自在に挿嵌
し、該ローラを前記トラツク溝の外輪軸方向のロ
ーラ案内面に挿入した等速自在継手において、上
記ローラを内側リングと外側リングとにより構成
し、内側リングの外周面を脚軸の軸心に中心をも
つ球面により形成すると共に、外側リングの内周
面を円筒面に形成し、両リングを嵌合させて内側
リングの外周面と外側リングの内周面とを接触せ
しめ、かつ外側リングが、上記外輪のローラ案内
面によつて外輪の軸線と平行に案内される外周面
を有することを特徴とする等速自在継手。1 Forming three track grooves in the axial direction on the outer ring,
A constant velocity universal joint in which a tripod member is inserted inside the outer ring, a roller is rotatably inserted into the three leg shafts of the tripod member, and the roller is inserted into the roller guide surface of the track groove in the outer ring axial direction. In the above roller, the roller is composed of an inner ring and an outer ring, the outer circumferential surface of the inner ring is formed as a spherical surface centered on the axis of the leg shaft, and the inner circumferential surface of the outer ring is formed as a cylindrical surface. The rings are fitted to bring the outer peripheral surface of the inner ring into contact with the inner peripheral surface of the outer ring, and the outer ring has an outer peripheral surface that is guided in parallel to the axis of the outer ring by the roller guide surface of the outer ring. A constant velocity universal joint characterized by:
Priority Applications (7)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB8710398A GB2195167B (en) | 1986-09-17 | 1987-05-01 | Homokinetic universal joint |
| AU72482/87A AU606827B2 (en) | 1986-09-17 | 1987-05-04 | Homokinetic tripod joint |
| US07/046,322 US4786270A (en) | 1986-09-17 | 1987-05-06 | Homokinetic tripod joint |
| DE19873716962 DE3716962A1 (en) | 1986-09-17 | 1987-05-20 | HOMOKINETIC UNIVERSAL JOINT |
| FR878707740A FR2603957B1 (en) | 1986-09-17 | 1987-06-03 | UNIVERSAL HOMOCINETIC JOINT |
| KR1019870007371A KR900000651B1 (en) | 1986-09-17 | 1987-07-09 | Homokinetic tripod joint |
| IT8721936A IT1231231B (en) | 1986-09-17 | 1987-09-16 | UNIVERSAL HOMOCINETIC JOINT. |
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP14240286 | 1986-09-17 | ||
| JP61-142402 | 1986-09-17 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS63186036A JPS63186036A (en) | 1988-08-01 |
| JPH031529B2 true JPH031529B2 (en) | 1991-01-10 |
Family
ID=15314511
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP62021613A Granted JPS63186036A (en) | 1986-09-17 | 1987-01-31 | Constant velocity universal joint |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JPS63186036A (en) |
| KR (1) | KR900000651B1 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2800817A1 (en) * | 1999-11-05 | 2001-05-11 | Ntn Toyo Bearing Co Ltd | Homo kinetic joint for motor vehicle transmission has spherical surfaces on spider rollers matching surface of grooves in bowl |
| JP4652267B2 (en) * | 2006-04-17 | 2011-03-16 | Ｎｔｎ株式会社 | Tripod type constant velocity universal joint |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6837794B1 (en) | 1996-02-05 | 2005-01-04 | Ntn Corporation | Tripod type constant velocity universal joint |
| FR2819863B1 (en) * | 2001-01-23 | 2003-06-13 | Gkn Glaenzer Spicer | HOMOCINETIC TRANSMISSION JOINT AND MECHANICAL TRANSMISSION MEMBER FOR SUCH A JOINT |
| DE102010008272A1 (en) * | 2009-02-18 | 2010-09-23 | GM Global Technology Operations, Inc., Detroit | universal joint |
| JP6887355B2 (en) * | 2017-09-19 | 2021-06-16 | Ntn株式会社 | Tripod type constant velocity universal joint |
| WO2019059204A1 (en) * | 2017-09-19 | 2019-03-28 | Ntn株式会社 | Tripod-type constant-velocity universal joint |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS62104025U (en) * | 1985-12-20 | 1987-07-02 |
-
1987
- 1987-01-31 JP JP62021613A patent/JPS63186036A/en active Granted
- 1987-07-09 KR KR1019870007371A patent/KR900000651B1/en not_active IP Right Cessation
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2800817A1 (en) * | 1999-11-05 | 2001-05-11 | Ntn Toyo Bearing Co Ltd | Homo kinetic joint for motor vehicle transmission has spherical surfaces on spider rollers matching surface of grooves in bowl |
| JP4652267B2 (en) * | 2006-04-17 | 2011-03-16 | Ｎｔｎ株式会社 | Tripod type constant velocity universal joint |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS63186036A (en) | 1988-08-01 |
| KR880003771A (en) | 1988-05-30 |
| KR900000651B1 (en) | 1990-02-02 |
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