JP3053636B2 - Outer ring for anti-vibration constant velocity joint - Google Patents
Outer ring for anti-vibration constant velocity jointInfo
- Publication number
- JP3053636B2 JP3053636B2 JP2140529A JP14052990A JP3053636B2 JP 3053636 B2 JP3053636 B2 JP 3053636B2 JP 2140529 A JP2140529 A JP 2140529A JP 14052990 A JP14052990 A JP 14052990A JP 3053636 B2 JP3053636 B2 JP 3053636B2
- Authority
- JP
- Japan
- Prior art keywords
- outer cylinder
- interference
- vibration
- cylinder
- constant velocity
- 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 - Fee Related
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
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Springs (AREA)
- Vibration Prevention Devices (AREA)
Description
【発明の詳細な説明】 〔産業上の利用分野〕 この発明は防振型等速ジョイントに用いる外輪に関す
るものである。Description: TECHNICAL FIELD The present invention relates to an outer ring used for a vibration-proof constant velocity joint.
〔従来の技術〕 駆動系が関与する自動車の音振問題を解決する一つの
手段として、第７図及び第８図に示すように、等速ジョ
イント用外輪１の外筒部２を、外側外筒３と内側外筒４
との組合せにより構成し、両者の間の円筒状間隙にゴム
等の弾性部材でなる防振材５を介在させることが知られ
ている。[Prior Art] As one means for solving the sound vibration problem of an automobile involving a drive system, as shown in FIGS. 7 and 8, an outer cylinder portion 2 of an outer ring 1 for a constant velocity joint is provided by an outer outer portion. Tube 3 and inner outer tube 4
It is known that a vibration isolator 5 made of an elastic member such as rubber is interposed in a cylindrical gap between the two.
なお、図中６はトリポード部材、７はブーツである。 In the drawings, reference numeral 6 denotes a tripod member, and reference numeral 7 denotes a boot.
上記の防振材５は、等速ジョイントを通じて伝達され
る振動をその伝達途中において吸収する作用がある。The vibration isolator 5 has an effect of absorbing the vibration transmitted through the constant velocity joint during the transmission.
しかしながら、過大なトルクが負荷されると、外側外
筒３と内側外筒４とが回転方向に相対変位するため、防
振材５が過大に変形し、損傷を受けるおそれがある。ま
た、過大なトルク負荷により、防振材５が圧縮応力とせ
ん断応力とを同時に受け、防振材５の損傷を助長する可
能性もある。However, when an excessive torque is applied, the outer outer cylinder 3 and the inner outer cylinder 4 are relatively displaced in the rotation direction, so that the vibration isolator 5 may be excessively deformed and damaged. Moreover, the vibration isolator 5 may receive compressive stress and shear stress at the same time due to an excessive torque load, which may promote damage to the vibration isolator 5.
そこで、この発明は、外側外筒と内側外筒の回転方向
の相対変位を一定以下に制限し、防振材に作用するトル
ク負荷は、純せん断のみとすることで防振材の耐久性を
向上させることを技術的課題とする。Therefore, the present invention limits the relative displacement of the outer outer cylinder and the inner outer cylinder in the rotational direction to a certain value or less, and reduces the durability of the vibration isolator by limiting the torque load acting on the vibration isolator to pure shearing only. Improving it is a technical issue.
上記の課題を解決する第一に手段は、外側外筒と内側
外筒との組合せによりジョイント用外輪の外筒部を構成
し、上記の外側外筒と内側外筒との間に弾性材でなる防
振材を介在してなり、トルク負荷時において上記外側外
筒と内側外筒が回転方向に相対変位することがある防振
型等速ジョイント用外輪において、上記の外側外筒の内
径面の周方向等分位置に干渉用突条を軸方向に沿って設
け、上記の内側外筒の外径面の周方向等分位置に上記の
各干渉用突条がジョイント回転方向に所要のすきまをお
いて嵌まる複数の干渉用嵌合溝を設け、上記各干渉用突
条相互間の外側外筒の内径面と上記各干渉用嵌合溝相互
間の内側外筒の外径面との間に上記の防振材を介在した
構成としたものである。A first means for solving the above-mentioned problem is to form an outer cylinder portion of a joint outer ring by a combination of an outer outer cylinder and an inner outer cylinder, and to use an elastic material between the outer outer cylinder and the inner outer cylinder. In the outer ring for a vibration-isolating type constant velocity joint, the outer outer cylinder and the inner outer cylinder may be relatively displaced in the rotational direction when a torque load is applied, the inner diameter surface of the outer outer cylinder An interference ridge is provided along the axial direction at an equally-spaced position in the circumferential direction, and each of the interference ridges is required in the joint rotation direction at a position equally-spaced in the circumferential direction on the outer diameter surface of the inner outer cylinder. A plurality of interference fitting grooves are provided so as to fit therein, and the inner diameter surface of the outer outer cylinder between the interference protrusions and the outer diameter surface of the inner outer cylinder between the interference fitting grooves are provided. The configuration is such that the above-described vibration damping material is interposed therebetween.
第二の手段は、上記の干渉用突条相互間の外側外筒の
内径面に薄板部材を介在せしめ、その薄板部材の内面に
上記の防振材を接着した構成としたものである。The second means has a structure in which a thin plate member is interposed on the inner surface of the outer outer cylinder between the interference protrusions, and the above-mentioned vibration damping material is adhered to the inner surface of the thin plate member.
第三の手段は、上記の干渉用突条と、上記の干渉用嵌
合溝の両内壁面との間に形成された各すきまＸの中心角
をそれぞれαとし、上記の干渉用突条と、上記の防振材
の立ち上り部との間の距離Ｙの中心角をそれぞれβとし
たとき、α≦βの関係を有する構成としたものである。The third means is that the central angle of each of the clearances X formed between the interference ridge and the inner wall surfaces of the interference fitting groove is α, and the interference ridge is When the central angle of the distance Y between the rising portion of the vibration isolator and the center portion is β, the configuration has a relationship of α ≦ β.
上記構成の外輪において、トルク負荷が作用して内側
外筒と外側外筒とのジョイント回転方向の相対変位が一
定以上に達すると、干渉用突条と干渉用嵌合溝とが衝合
し干渉しあう。このため、それ以上の相対変位が制限さ
れ、防振材の異常変形が避けられる。In the outer ring having the above configuration, when a torque load acts and the relative displacement of the inner outer cylinder and the outer cylinder in the joint rotation direction reaches a certain value or more, the interference ridge and the interference fitting groove collide with each other and interfere. Each other. For this reason, further relative displacement is restricted, and abnormal deformation of the vibration isolator can be avoided.
第二の手段の場合は、薄板部材が外側外筒に対する内
側外筒のジョイント回転方向の相対位置を決める作用を
行うと共に、外側外筒と防振材の間のすべりを防止す
る。In the case of the second means, the thin plate member performs an operation of determining a relative position of the inner outer cylinder in the joint rotation direction with respect to the outer outer cylinder, and prevents slippage between the outer outer cylinder and the vibration isolator.
更に、第三の手段の場合は、内側外筒と外側外筒の相
対変位が最大限に達しても、防振材が内側外筒の外径面
から露出することなく、従って防振材の半径方向への張
り出しが防止できる。Further, in the case of the third means, even when the relative displacement between the inner outer cylinder and the outer outer cylinder reaches the maximum, the vibration damping material is not exposed from the outer diameter surface of the inner outer cylinder, and therefore, the vibration damping material is Overhang in the radial direction can be prevented.
第１図及び第２図に示す第１実施例の等速ジョイント
用の外輪10は、外筒部11と軸部12とから成る。外筒部11
は、軸部12と一体の有底カップ形の外側外筒13と、その
内側に嵌合される内側外筒14との組合せにより構成され
る。The outer race 10 for a constant velocity joint according to the first embodiment shown in FIGS. 1 and 2 comprises an outer cylinder 11 and a shaft 12. Outer cylinder 11
Is constituted by a combination of a bottomed cup-shaped outer cylinder 13 integrated with the shaft 12 and an inner cylinder 14 fitted inside the outer cylinder 13.
外側外筒13の内面には、周方向に３等分された間隔を
おいて、干渉用突条16が形成される。干渉用突条16はト
ラック溝17の溝底18を形成する位置に設けられる。Interference ridges 16 are formed on the inner surface of the outer cylinder 13 at equal intervals in the circumferential direction. The interference ridge 16 is provided at a position where the groove bottom 18 of the track groove 17 is formed.
内側外筒14は、外側外筒13底面と対向した閉塞壁19を
有し、その閉塞壁19の周縁から開放端にわたり、周方向
に３等分された間隔をおいて干渉用嵌合溝20が設けられ
る。各嵌合溝20は、前記の干渉用突条16の幅より若干広
く形成され、その両側内面が干渉用突条16の外側面と若
干のすき間Ｘをおいて相い対向する。また、上記の干渉
用嵌合溝20の内径側に断面円弧形のトラック溝壁面21が
形成され、前述の溝底18とあわせてトラック溝17を構成
する。The inner outer cylinder 14 has a closed wall 19 facing the bottom surface of the outer outer cylinder 13, and extends from the peripheral edge to the open end of the closed wall 19 at equal intervals in the circumferential direction at intervals of three equal intervals. Is provided. Each fitting groove 20 is formed to be slightly wider than the width of the interference ridge 16, and the inner surfaces on both sides thereof are opposed to the outer surface of the interference ridge 16 with a slight gap X therebetween. A track groove wall surface 21 having an arc-shaped cross section is formed on the inner diameter side of the interference fitting groove 20, and forms a track groove 17 together with the groove bottom 18.
上記の干渉用嵌合溝20によって３等分された内側外筒
14の外周面と、干渉用突条16によって３等分された外側
外筒13の内周面との間に、薄板部材22と、ゴム等の弾性
体でなる防振材23が介在される。薄板部材22は外側外筒
13の内周面に沿って挿入され、その両側辺が干渉用突条
16にそれぞれ当接される。また、その薄板部材22と防振
材23及び内側外筒14の外径面はそれぞれ接着される。Inner outer cylinder divided into three by the above-mentioned interference fitting groove 20
A thin plate member 22 and an anti-vibration member 23 made of an elastic material such as rubber are interposed between the outer peripheral surface of 14 and the inner peripheral surface of the outer outer cylinder 13 divided into three by the interference ridge 16. . Thin plate member 22 is an outer cylinder
13 are inserted along the inner peripheral surface of the
16 abut each. Further, the outer diameter surfaces of the thin plate member 22, the vibration isolator 23, and the inner outer cylinder 14 are bonded to each other.
第１実施例は以上のごときものであり、３本のトラッ
ク溝17に１つのトリポード部材が挿入され、等速ジョイ
ントとして使用される。等速ジョイントにトルク負荷が
作用して外側外筒13と内側外筒14とがジョイントの回転
方向に一定以上相対変位すると、すき間Ｘが０となり干
渉用突条16と干渉用嵌合溝20の側面が相互に衝合して干
渉しあうので、それ以上の相対変位が制限され、防振材
23の異常変形が避けられる。また、薄板部材22は、外側
外筒13と防振材23間のすべりを防止する。The first embodiment is as described above. One tripod member is inserted into three track grooves 17 and used as a constant velocity joint. When a torque load acts on the constant velocity joint and the outer outer cylinder 13 and the inner outer cylinder 14 are relatively displaced in the rotational direction of the joint by a certain amount or more, the gap X becomes zero and the interference ridge 16 and the interference fitting groove 20 As the sides abut each other and interfere with each other, further relative displacement is limited,
23 abnormal deformation can be avoided. Further, the thin plate member 22 prevents slippage between the outer cylinder 13 and the vibration isolator 23.
第３図に示す第２実施例は、外側外筒13及び内側外筒
14が共に有底カップ形であるが、外側外筒13の内径面に
形成される干渉用突条16は、前述のものに比べ幅が狭
く、その分だけ各突条16間の内周面の幅が広くなってい
る。The second embodiment shown in FIG.
Although both 14 are cup-shaped with a bottom, the interference ridges 16 formed on the inner diameter surface of the outer cylinder 13 are narrower than those described above, and the inner peripheral surface between the ridges 16 is correspondingly smaller. Has become wider.
内側外筒14には、その外径面に上記の干渉用突条16と
周方向に若干のすき間Ｘをもって嵌合する干渉用嵌合溝
20が形成され、その干渉用嵌合溝20間の内側外筒14の外
周面は、両方の突条16間に挿入される。また、外側外筒
13の内周面と、内側外筒14の外周面の間に薄板部材22と
防振材23が介在され、前述の場合と同様に接着される。
また、薄板部材22の両側辺は、それぞれ干渉用突条16の
側面に当接される。The inner outer cylinder 14 has an interference fitting groove which fits on the outer diameter surface of the inner outer cylinder 14 with the interference ridge 16 with a slight clearance X in the circumferential direction.
20 are formed, and the outer peripheral surface of the inner outer cylinder 14 between the interference fitting grooves 20 is inserted between both the ridges 16. Also, outer outer cylinder
A thin plate member 22 and an anti-vibration material 23 are interposed between the inner peripheral surface of 13 and the outer peripheral surface of the inner outer cylinder 14, and are bonded in the same manner as described above.
Further, both sides of the thin plate member 22 are in contact with the side surfaces of the interference ridge 16 respectively.
上記の第２実施例の場合も、干渉用突条16の両側面
と、干渉用嵌合溝20の両側内側面とが、周方向に若干の
すき間Ｘをおいて対向しているため、一定以上大きいト
ルク負荷が作用すると、両方の対向面が衝合し、干渉す
る。Also in the case of the second embodiment, since both side surfaces of the interference ridge 16 and both side inner surfaces of the interference fitting groove 20 are opposed to each other with a small gap X in the circumferential direction, they are constant. When a large torque load acts, both opposing surfaces abut and interfere with each other.
なお、第２実施例の場合は、第１実施例に比べ、防振
材23の容積が増えるので、防振材23の耐久性が増し、ま
た干渉用突条16と干渉用嵌合溝20との接触面積も増える
ので、防振材23の異常変形を確実に防止することができ
る。In the case of the second embodiment, since the volume of the vibration isolator 23 is increased as compared with the first embodiment, the durability of the vibration isolator 23 is increased, and the interference ridge 16 and the interference fitting groove 20 are increased. Therefore, the abnormal deformation of the vibration isolator 23 can be reliably prevented.
第４図に示す第３実施例は、いわゆるダブルオフセッ
ト型等速ジョイントの外輪の場合であり、内側外筒14の
内面に複数のボール溝25を備えている。The third embodiment shown in FIG. 4 is a case of an outer ring of a so-called double offset type constant velocity joint, in which a plurality of ball grooves 25 are provided on the inner surface of the inner outer cylinder 14.
外側外筒13と内側外筒14間にそれぞれ干渉用突条16と
干渉用嵌合溝20を形成する点及び両者の外周面と内周面
との間に薄板部材22と防振材23を介在させる構成も第２
実施例の場合と同様であり、同様の作用を行う。The thin plate member 22 and the vibration isolator 23 are formed between the outer outer tube 13 and the inner outer tube 14 at the point where the interference ridge 16 and the interference fitting groove 20 are formed, respectively, and between the outer peripheral surface and the inner peripheral surface thereof. Second configuration
This is the same as the embodiment, and performs the same operation.
上記の第１〜第３のいずれの実施例においても薄板部
材22は、外側外筒13に対する内側外筒14の位置決め作用
を行うが、この薄板部材22を省略し、外側外筒14の外周
面との間に防振材23のみを介在する構成としてもよい。
このようにすると内側外筒14の位置が定まり難いが、ト
ルク負荷作用時に干渉用突条16と干渉用嵌合溝20とを干
渉させることにより、防振材23の異常変形を防止すると
いう所期の目的は達成することができる。In any of the first to third embodiments, the thin plate member 22 performs the positioning operation of the inner outer tube 14 with respect to the outer outer tube 13, but the thin plate member 22 is omitted and the outer peripheral surface of the outer outer tube 14 is omitted. And only the vibration isolator 23 may be interposed therebetween.
In this case, the position of the inner outer cylinder 14 is difficult to be determined. However, by interfering the interference ridge 16 and the interference fitting groove 20 when a torque load is applied, abnormal deformation of the vibration isolator 23 is prevented. The purpose of the period can be achieved.
次に、第５図に示した第４実施例は、基本的構造は、
第２図に示した第１実施例の場合と同様であるが、この
場合は、干渉用突条16と、干渉用嵌合溝20の内側面との
間の各すきまＸに対応した中心角をαとし、また干渉用
突条16と、防振材23の立ち上り部26との間の各距離Ｙに
対応した中心角をβとした場合に、α≦βの関係がある
ように構成している。Next, in a fourth embodiment shown in FIG. 5, the basic structure is as follows.
2 is the same as that of the first embodiment shown in FIG. 2, but in this case, the center angle corresponding to each clearance X between the interference ridge 16 and the inner surface of the interference fitting groove 20. Is set to α, and when a central angle corresponding to each distance Y between the interference ridge 16 and the rising portion 26 of the vibration isolator 23 is set to β, the relationship is established such that α ≦ β. ing.
このように構成すると、内側外筒14と外側外筒13とが
第６図に示すように、最大限に相対変位して一方のすき
まＸが０になり、他方のすきまが2Xになった場合でも、
防振材23は内側外筒14により覆われる。このため、すき
ま2Xの部分から防振材23の側面部分がジョイント内方へ
張り出すことが防止できる。With this configuration, when the inner outer cylinder 14 and the outer outer cylinder 13 are maximally displaced relative to each other as shown in FIG. 6 so that one clearance X becomes 0 and the other clearance becomes 2X. But
The vibration isolator 23 is covered by the inner outer cylinder 14. Therefore, it is possible to prevent the side surface portion of the vibration isolator 23 from protruding inward from the gap 2X.
以上のように、この発明は外側外筒と内側外筒の間
に、トルク負荷が一定以上大きくなると相互に干渉する
干渉用の突条と干渉用嵌合溝を設けたものであるから、
防振材に作用するトルク負荷は純ねじり方向（純せん
断）であり、圧縮応力とせん断応力が同時に作用するこ
とを防止することができる。このため、防振材の耐久性
を向上させる効果がある。As described above, since the present invention is provided between the outer outer cylinder and the inner outer cylinder, the interference ridge and the interference fitting groove are provided to interfere with each other when the torque load becomes larger than a certain value.
The torque load acting on the vibration isolator is in a pure torsion direction (pure shear), and it is possible to prevent simultaneous action of compressive stress and shear stress. Therefore, there is an effect of improving the durability of the vibration damping material.
更に、すきまＸと距離Ｙとをそれぞれ対応する中心角
α及びβとの関係をα≦βの関係に設定することによ
り、防振材側面部の半径方向への張り出しが防止でき、
張り出し部分に生じる応力集中を避け防振材の耐久性を
一層向上させることができる。Further, by setting the relationship between the central angles α and β corresponding to the clearance X and the distance Y to α ≦ β, it is possible to prevent the side portions of the vibration-proof material from protruding in the radial direction,
It is possible to avoid stress concentration occurring in the overhang portion and further improve the durability of the vibration isolator.
第１図は第１実施例の断面図、第２図は第１図のII−II
線の断面図、第３図は第２実施例の断面図、第４図は第
３実施例の断面図、第５図は第４実施例の断面図、第６
図は第５図の場合変位時しの一部拡大断面図、第７図は
従来例の断面図、第８図は第７図のVIII−VIII線の断面
図である。 10……外輪、11……外筒部、12……軸部、13……外側外
筒、14……内側外筒、16……干渉用突条、17……トラッ
ク溝、18……溝底、19……閉塞壁、20……干渉用嵌合
溝、21……壁面、22……薄板部材、23……防振材、25…
…ボール溝、26……立ち上り部。FIG. 1 is a cross-sectional view of the first embodiment, and FIG. 2 is a II-II of FIG.
3 is a sectional view of the second embodiment, FIG. 4 is a sectional view of the third embodiment, FIG. 5 is a sectional view of the fourth embodiment, and FIG.
FIG. 5 is a partially enlarged sectional view of FIG. 5 when displaced, FIG. 7 is a sectional view of a conventional example, and FIG. 8 is a sectional view taken along line VIII-VIII of FIG. 10 ... outer ring, 11 ... outer cylinder, 12 ... shaft, 13 ... outer outer cylinder, 14 ... inner outer cylinder, 16 ... interference ridge, 17 ... track groove, 18 ... groove Bottom, 19… Closed wall, 20… Interference fitting groove, 21… Wall surface, 22… Thin plate member, 23… Anti-vibration material, 25…
… Ball groove, 26 …… the rising part.
フロントページの続き (56)参考文献 特開 昭48−83243（ＪＰ，Ａ) 特開 平２−217623（ＪＰ，Ａ) 特開 平２−217624（ＪＰ，Ａ) 特開 平２−168025（ＪＰ，Ａ) 実開 昭62−69645（ＪＰ，Ｕ) 実開 平２−109019（ＪＰ，Ｕ) (58)調査した分野(Int.Cl.7，ＤＢ名) F16D 3/205 F16D 3/20 Continuation of front page (56) References JP-A-48-83243 (JP, A) JP-A-2-217623 (JP, A) JP-A-2-217624 (JP, A) JP-A 2-168025 (JP) , A) Shokai Sho 62-69645 (JP, U) Shokai Hei 2-109019 (JP, U) (58) Fields investigated (Int. Cl. 7 , DB name) F16D 3/205 F16D 3/20
Claims (3)
イント用外輪の外筒部を構成し、上記の外側外筒と内側
外筒との間に弾性材でなる防振材を介在してなり、トル
ク負荷時において上記外側外筒と内側外筒が回転方向に
相対変位することがある防振型等速ジョイント用外輪に
おいて、上記の外側外筒の内径面の周方向等分位置に干
渉用突条を軸方向に沿って設け、上記の内側外筒の外径
面の周方向等分位置に上記の各干渉用突条がジョイント
回転方向に所要のすきまをおいて嵌まる複数の干渉用嵌
合溝を設け、上記各干渉用突条相互間の外側外筒の内径
面と上記各干渉用嵌合溝相互間の内側外筒の外径面との
間に上記の防振材を介在したことを特徴とする防振型等
速ジョイント用外輪。An outer cylinder portion of a joint outer ring is constituted by a combination of an outer outer cylinder and an inner outer cylinder, and a vibration isolator made of an elastic material is interposed between the outer outer cylinder and the inner outer cylinder. In the outer ring for a vibration-isolating type constant velocity joint in which the outer outer cylinder and the inner outer cylinder may be relatively displaced in the rotational direction at the time of torque load, the outer outer cylinder and the inner cylinder are positioned at equal circumferential positions on the inner surface of the outer outer cylinder. A plurality of interference ridges are provided along the axial direction, and the interference ridges are fitted at equal circumferential positions on the outer diameter surface of the inner outer cylinder with a required clearance in the joint rotation direction. An interference fitting groove is provided, and the vibration damping material is provided between an inner diameter surface of the outer outer cylinder between the interference protrusions and an outer diameter surface of the inner outer cylinder between the interference fitting grooves. An outer ring for an anti-vibration type constant velocity joint, characterized by interposing
面に薄板部材を介在せしめ、その薄板部材の内面に上記
の防振材を接着したことを特徴とする請求項（１）に記
載の防振型等速ジョイント用外輪。2. A thin plate member is interposed on the inner surface of the outer cylinder between the interference projections, and the vibration isolator is bonded to the inner surface of the thin plate member. The outer ring for a vibration-proof type constant velocity joint described in (2).
の両内壁面との間に形成された各すきまＸの中心角をそ
れぞれαとし、上記の干渉用突条と、上記の防振材の立
ち上り部との間の距離Ｙの中心角をそれぞれβとしたと
き、α≦βの関係を有することを特徴とする請求項
（１）又は（２）に記載の防振型等速ジョイント用外
輪。The center angle of each of the clearances X formed between the interference ridge and the inner wall surfaces of the interference fitting groove is α, and the interference ridge is The anti-vibration device according to claim 1, wherein when a central angle of a distance Y between the rising portion of the anti-vibration material and β is β, a relationship of α ≦ β is satisfied. Outer ring for type constant velocity joints.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2140529A JP3053636B2 (en) | 1990-02-19 | 1990-05-29 | Outer ring for anti-vibration constant velocity joint |
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2-37792 | 1990-02-19 | ||
| JP3779290 | 1990-02-19 | ||
| JP2140529A JP3053636B2 (en) | 1990-02-19 | 1990-05-29 | Outer ring for anti-vibration constant velocity joint |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH03272322A JPH03272322A (en) | 1991-12-04 |
| JP3053636B2 true JP3053636B2 (en) | 2000-06-19 |
Family
ID=26376937
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2140529A Expired - Fee Related JP3053636B2 (en) | 1990-02-19 | 1990-05-29 | Outer ring for anti-vibration constant velocity joint |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3053636B2 (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102013101069A1 (en) * | 2013-02-01 | 2014-08-07 | Tschan Gmbh | Elastic coupling |
| JP7142593B2 (en) * | 2019-03-14 | 2022-09-27 | Ntn株式会社 | Outer joint member for constant velocity universal joint |
-
1990
- 1990-05-29 JP JP2140529A patent/JP3053636B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH03272322A (en) | 1991-12-04 |
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