WO2006126328A1 - Constant velocity joint - Google Patents

Constant velocity joint Download PDF

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Publication number
WO2006126328A1
WO2006126328A1 PCT/JP2006/306038 JP2006306038W WO2006126328A1 WO 2006126328 A1 WO2006126328 A1 WO 2006126328A1 JP 2006306038 W JP2006306038 W JP 2006306038W WO 2006126328 A1 WO2006126328 A1 WO 2006126328A1
Authority
WO
WIPO (PCT)
Prior art keywords
boot
outer ring
constant velocity
ring member
velocity joint
Prior art date
Application number
PCT/JP2006/306038
Other languages
French (fr)
Japanese (ja)
Inventor
Shigeru Okubo
Yuuki Miyashita
Fumihiko Tsujimoto
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.
Publication of WO2006126328A1 publication Critical patent/WO2006126328A1/en

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16JPISTONS; CYLINDERS; SEALINGS
    • F16J3/00Diaphragms; Bellows; Bellows pistons
    • F16J3/04Bellows
    • F16J3/041Non-metallic bellows
    • F16J3/042Fastening details
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16DCOUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/84Shrouds, e.g. casings, covers; Sealing means specially adapted therefor
    • F16D3/843Shrouds, e.g. casings, covers; Sealing means specially adapted therefor enclosed covers
    • F16D3/845Shrouds, e.g. casings, covers; Sealing means specially adapted therefor enclosed covers allowing relative movement of joint parts due to the flexing of the cover
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16DCOUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/20Universal 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
    • F16D3/202Universal 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
    • F16D3/205Universal 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
    • F16D3/2055Universal 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

Definitions

  • the present invention relates to a constant velocity joint provided with a bush mounting portion of an outer ring member to which a fixing portion of a resin boot is fixed by a boot band.
  • a constant velocity joint as a joint is generally used in order to transmit a rotational driving force to a driving shaft force driven shaft.
  • This constant velocity joint is fitted with bellows-shaped boots for the purpose of preventing leakage of grease enclosed in the joint and preventing foreign objects from entering the joint.
  • one end of the boot is mounted so as to close the opening of the outer cup constituting the constant velocity joint, and the other end of the boot surrounds the outer periphery of the driven shaft.
  • the one end portion and the other end portion of the boot are fastened and fixed with a large-diameter and small-diameter boot band, respectively.
  • the greave boots are less elastic than the rubber boots, and therefore, special contrivance is required in the mounting structure with the mating member where the state of fitting into the mating member tends to become unstable. .
  • the convex portion 5 does not fit well with the engaging groove 2 and the fixing portion of the boot 4 shifts to the back side or the near side of the outer ring member 1 and it is difficult to reliably position the boot mounting portion.
  • Patent Document 1 Japanese Patent Application Laid-Open No. 7-280092
  • Patent Document 2 Japanese Patent Laid-Open No. 11-166624
  • a general object of the present invention is to provide an end portion of an outer ring member capable of reliably and simply positioning a fixed portion of the boot with respect to a boot mounting portion of the outer ring member when the boot band is tightened.
  • the object is to provide a constant velocity joint having a shape.
  • the end surface force of the outer ring member is set to L (mm) as a predetermined distance separated along the horizontal direction to the top of the inclined surface, and the inclination angle of the inclined surface with respect to the mounting surface is ⁇ ( L and 0 are set in a range that satisfies the following relational expressions (1) to (5).
  • the outer ring is based on a range that satisfies all the relational expressions (1) to (5).
  • the boo- band is tightened by setting the value of the predetermined distance L that is spaced along the horizontal direction from the end surface of the member to the top of the inclined surface and the value of the inclination angle ⁇ of the inclined surface with respect to the mounting surface.
  • the boot fixing portion is reliably positioned without being displaced with respect to the boot mounting portion of the outer ring member, and further, a predetermined sealing property can be secured, and a suitable outer ring member considering workability is also provided.
  • the end shape can be set.
  • the L (mm) and 0 (degrees) are expressed by the following relational expressions (6) and (7). It should be set to a range that satisfies all.
  • FIG. 1 is a longitudinal sectional view along the axial direction of a tripart type constant velocity joint according to an embodiment of the present invention.
  • FIG. 2 is a partially enlarged longitudinal sectional view of an outer ring member constituting the constant velocity joint of FIG.
  • FIG. 3 is a partially enlarged longitudinal sectional view of an outer ring member according to a first modification.
  • FIG. 4 is a partially enlarged longitudinal sectional view of an outer ring member according to a second modification.
  • FIG. 5 is a partially enlarged longitudinal sectional view of a boot constituting the constant velocity joint of FIG.
  • FIG. 6 is a partially enlarged longitudinal sectional view of a boot according to a modification.
  • FIG. 7 is a characteristic diagram showing an allowable range in the relationship between L and ⁇ .
  • FIG. 8 is a longitudinal sectional view along the axial direction of a Barfield type constant velocity joint according to another embodiment of the present invention.
  • FIG. 9 is a partially enlarged longitudinal sectional view showing a boot mounting structure in the prior art.
  • reference numeral 10 indicates a tripod type constant velocity joint according to an embodiment of the present invention, and this constant velocity joint 10 is integrally connected to one end of a first shaft (not shown).
  • a bottomed cylindrical outer ring member 12 having an opening 11 and an inner member 16 fixed to one end of the second shaft 14 and housed in the hole of the outer ring member 12.
  • the constant velocity joint 10 has a small-diameter fixing portion (not shown) in which one end which is a large-diameter fixing portion 18 is fitted to an outer peripheral surface (boot mounting portion 20 described later) of the outer ring member 12. And the other end portion of the second shaft 14 fitted on the outer peripheral portion of the second shaft 14 and the large-diameter fixing portion 18 of the boot 22 to the boot mounting portion 20 of the outer ring member 12.
  • a large-diameter boot nond 24 to be fixed and a small-diameter boot band (not shown) for fixing a small-diameter fixing portion (not shown) of the boot 22 to the outer peripheral surface of the second shaft 14 are included.
  • Three guide grooves 26a to 26c are formed on the inner wall surface of the outer ring member 12 so as to extend along the axial direction and have an interval of 120 degrees around the shaft center ( However, the guide grooves 26b and 26c are not shown).
  • the guide grooves 26a to 26c are composed of a ceiling portion whose section is formed in a curved shape, and a sliding portion which is opposed to each other on both sides of the ceiling portion and is formed in an arc shape in section.
  • a spider 28 including a ring-shaped portion is selectively fitted to the second shaft 14, and the outer surface of the spider 28 bulges toward the guide grooves 26a to 26c, and 120 degrees around the axis.
  • Three traons 30a to 30c are formed in a body at intervals of the interval (however, the traon 30c is not shown).
  • Each of the trillions 30a (30b, 30c) is formed in a columnar shape having a constant outer diameter.
  • a ring-shaped roller member 34 is externally fitted to the outer periphery of the traon 30a (30b, 30c) via a plurality of rolling elements 32.
  • the rolling element 32 may be a rolling bearing including a needle, a roller and the like, for example. It is to be noted that a roller member (ring body) that does not have the rolling element 32 is directly attached to the outer peripheral surface of the trolley 30a (30b, 30c) so as to be slidable.
  • the outer ring member 12 includes a cup portion 12a having an opening 11 and a shaft portion 12b formed integrally with the cup portion 12a.
  • a boot mounting portion 20 to which a large-diameter fixing portion 18 at the end portion of the boot 22 is attached is formed on the outer peripheral surface in the vicinity of the edge portion on the opening 11 side of the outer ring member 12.
  • the boot mounting portion 20 has an outer ring member 12 having an opening 11.
  • a mounting surface 36 formed of an annular surface having a substantially flat cross-section formed by cutting along the circumferential direction by a predetermined width from the end surface 35 of the shaft to the shaft portion 12b side, and a shaft continuous to the mounting surface 36
  • An annular inclined surface 44 that is formed on the side of the portion 12b and is inclined by an inclination angle ⁇ with respect to the mounted surface 36 having a substantially flat cross section is provided.
  • L be a predetermined distance along the horizontal direction parallel to the axis T1 of the outer ring member 12, which is the spacing between the end surface 35 of the outer ring member 12 and the top 45 of the inclined surface 44.
  • an engagement groove 38 having a predetermined groove bottom 42 may be provided at a substantially central portion of the mounted surface 36 having a substantially flat cross section.
  • a pair of annular protrusions 40a and 40b may be formed to bulge out at adjacent portions on both sides of the engaging groove 38 therebetween.
  • the boot 22 has a bellows portion having a corrugated section in which peaks and valleys are alternately continuous, and an outer diameter D2 of the boot mounting portion 20 of the outer ring member 12 is provided at one end portion of the bellows portion. (See FIG. 5), and the other end of the bellows part is provided with a fixing part (smaller diameter corresponding to the outer diameter of the second shaft 14). (Not shown).
  • the inner diameter D1 of the fixing portion 18 of the boot 22 and the outer diameter D2 of the outer ring member 12 are set so as to satisfy the relationship of D1 ⁇ D2.
  • the fixing portion 18 attached to the boot mounting portion 20 of the outer ring member 12 has an engaging groove 38 (see FIGS. 3 and 3) of the boot mounting portion 20 of the outer ring member 12.
  • the annular protrusion 46 positioned in association with (see FIG. 4) may be bulged.
  • T2 represents the axis of the boot 22.
  • the constant velocity joint 10 is basically configured as described above.
  • the fixing portion 18 of the boot 22 is attached to the outer ring member 12.
  • a method for setting the end shape of the outer ring member 12 (the shape of the boot mounting portion 20) will be described.
  • the inner diameter D1 of the fixing portion 18 of the boot 22 and the outer diameter D2 of the boot mounting portion 20 of the outer ring member 12 are set so as to satisfy the relationship of D1 ⁇ D2. And good
  • This permissible range ⁇ ⁇ is a range that satisfies all the following relational expressions (1) to (5) between L (mm) and 0 (degrees), and includes the following (1) to (5 ) Is set by the area surrounded by the relational expression.
  • straight lines (1) to (5) indicate straight lines corresponding to the above relational expressions, respectively.
  • the inclination angle ⁇ is less than 20 degrees, the amount of riding on the inclined surface 44 of the end of the boot 22 will increase and the sealing performance and positioning will deteriorate, and if the inclination angle ⁇ exceeds 60 degrees, the inclination will increase. This is because the machining of the surface 44 becomes difficult.
  • the optimum range ⁇ (see shaded area) is the following (6), (7) of L (mm) and ⁇ (degrees) ) Should be set according to the area surrounded by the relational expression.
  • the contents of Eq. (6) are divided into straight lines (6A) and straight lines (6B), and the contents of Eq. (7) are divided into straight lines (7A) and straight lines (7B). ⁇ .
  • the boot band 24 is tightened by setting the end shape of the outer ring member 12 (the shape of the boot mounting portion 20) based on the allowable range M set as described above.
  • the fixing portion 18 of the boot 22 can be reliably positioned with respect to the boot mounting portion 20 of the outer ring member 12.
  • the end surface force of the outer ring member 12 in the allowable range M shown in FIG. The value of a predetermined distance L that is separated from the top 45 of the inclined surface 44 that continues to the mounted surface 36 via 36 and the value of the inclination angle ⁇ of the inclined surface 44 with respect to the mounted surface 36 are set.
  • the fixing portion 18 of the boot 22 is securely positioned with respect to the boot mounting portion 20 without being displaced toward the shaft portion 12b side or the end surface 35 side.
  • the end surface 35 of the outer ring member 12 is determined as the reference surface, and a simple distance from the end surface 35 of the outer ring member 12 to the top 45 of the inclined surface 44 is L ( Since it is set by a simple shape, the method for setting the end shape of the outer ring member 12 can be simplified, and the end shape of the outer ring member 12 can be easily set and changed.
  • the end shape of the outer ring member 12 (the shape of the boot mounting portion 20) constituting the tripod type constant velocity joint 10 is described, but the present invention is not limited to this.
  • the present invention can also be applied to the end shape of the outer ring member 102 of the Barfield type constant velocity joint 100 as shown in FIG. Note that the same components are denoted by the same reference numerals, and detailed description thereof is omitted.
  • the constant velocity joint 100 is accommodated in an outer ring member 102 having a shaft portion 102b connected to a first shaft (not shown) and an opening 106 of the outer ring member 102 connected to the second shaft 104. And an inner member 108.
  • Six first guide grooves 110 are formed on the inner wall of the outer ring member 102 so as to extend along the axial direction and are spaced by 60 degrees around the axis.
  • the inner member 108 is formed on the inner ring 114 formed with a plurality of second guide grooves 112 corresponding to the first guide grooves 110 along the circumferential direction of the outer peripheral surface, and on the inner wall surface of the outer ring member 102.
  • a plurality of (for example, six) rotating torque transmitting functions disposed between the first guiding groove 110 formed on the outer ring 114 and the second guiding groove 112 formed on the outer diameter surface of the inner ring 114.
  • a retainer 120 formed between the outer ring member 102 and the inner ring 114.
  • the retainer 118 is formed along the circumferential direction.
  • the setting of the predetermined distance L provided at the end portion of the outer ring member 102 and the inclination angle ⁇ of the inclined surface 44 is based on the setting range M or the optimum range N as in the case of the tripod type outer ring member 12. Detailed description thereof will be omitted.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sealing Devices (AREA)
  • Diaphragms And Bellows (AREA)

Abstract

A constant velocity joint where a distance L (mm) and an inclination angle θ (degree) are set in an allowable range M satisfying the expressions of (1)-(5) below, the distance L (mm) being a predetermined horizontal distance between an end face (35) of an outer ring member (12) and a top section (45) of a slope (44), the inclination angle θ (degree) being the angle of the slope (44) relative to a surface (36). (1) L ≤ -0.018θ + 15.807 (2) L ≤ -0.1438θ + 21.597 (3) L ≥ -0.0885θ + 16.106 (4) θ ≥ 20 (5) θ ≤ 60

Description

明 細 書  Specification
等速ジョイント 技術分野  Constant Velocity Joint Technology Field
[0001] 本発明は、榭脂ブーツの固定部がブーツバンドによって固定される外輪部材のブ 一ッ取付部が設けられた等速ジョイントに関する。  [0001] The present invention relates to a constant velocity joint provided with a bush mounting portion of an outer ring member to which a fixing portion of a resin boot is fixed by a boot band.
背景技術  Background art
[0002] 例えば、自動車等の車両において、駆動軸力 従動軸に対して回転駆動力を伝達 するために、継手としての等速ジョイントが一般的に使用されている。この等速ジョイ ントには、ジョイント内部に封入されたグリスの漏れ出し防止やジョイント内部への異 物進入防止を目的として蛇腹形状のブーツが装着されて 、る。  For example, in a vehicle such as an automobile, a constant velocity joint as a joint is generally used in order to transmit a rotational driving force to a driving shaft force driven shaft. This constant velocity joint is fitted with bellows-shaped boots for the purpose of preventing leakage of grease enclosed in the joint and preventing foreign objects from entering the joint.
[0003] 具体的には、ブーツの一端部が等速ジョイントを構成するァウタカップの開口部を 閉塞するように装着され、ブーツの他端部がドリブン側のシャフトの外周部を囲繞す るように嵌着され、前記ブーツの一端部及び他端部は、それぞれ、大径及び小径の ブーツバンドで締め付けて固定される。  [0003] Specifically, one end of the boot is mounted so as to close the opening of the outer cup constituting the constant velocity joint, and the other end of the boot surrounds the outer periphery of the driven shaft. The one end portion and the other end portion of the boot are fastened and fixed with a large-diameter and small-diameter boot band, respectively.
[0004] この等速ジョイント用のブーツとしては、ゴム材料力 なるゴムブーツと、榭脂製材料 力 なる榭脂ブーツとが一般的に用いられており、近時では、耐回転膨張性や耐久 性等の観点力 榭脂ブーツが多用される傾向にある。  [0004] As a boot for this constant velocity joint, a rubber boot having a rubber material strength and a resin boot having a rubber material strength are generally used. Recently, rotational expansion resistance and durability have been increased. Viewpoint power etc. There is a tendency that rosin boots are frequently used.
[0005] 特に、榭脂ブーツは、ゴムブーツと比較して弾性が小さ 、ため、相手部材への嵌め 込み状態が不安定になり易ぐ相手部材との取付構造において特別な工夫が必要と される。  [0005] In particular, the greave boots are less elastic than the rubber boots, and therefore, special contrivance is required in the mounting structure with the mating member where the state of fitting into the mating member tends to become unstable. .
[0006] 従来技術に係るこの種の榭脂ブーツ取付構造に関し、例えば、特許文献 1及び特 許文献 2には、図 9に示されるように、外輪部材 1のブーツ取付部の外周に環状の係 合溝 2と前記係合溝 2の両側に配置された環状の突起部 3a、 3bとが一体的に形成さ れ、ブーツ端部の固定部 4に設けられた環状の凸部 5を前記係合溝 2に嵌め合わせ て両者の位置決めをした後、前記固定部 4をブーツバンド 6で締め付けて固定するこ とが開示されている。  [0006] With respect to this type of grease boot mounting structure according to the prior art, for example, in Patent Document 1 and Patent Document 2, as shown in FIG. 9, an annular ring is formed on the outer periphery of the boot mounting portion of the outer ring member 1. The engaging groove 2 and the annular protrusions 3a and 3b disposed on both sides of the engaging groove 2 are integrally formed, and the annular protrusion 5 provided on the fixing portion 4 at the boot end is formed as the above-mentioned It is disclosed that after the fitting groove 2 is fitted and positioned, the fixing portion 4 is fastened and fixed by a boot band 6.
[0007] 例えば、特許文献 1の段落 [0005]には、ブーツの固定部 4の抜け止め強度とシー ル性を確保するために、ブーツの固定部 4の凸部 5の高さを比較的大きく設定する必 要があるとし、一方、榭脂ブーツは一般に硬度が HD50程度と高ぐゴムブーツに比 ベて弾性変形しにくいので、凸部 5が高すぎると相手部材 (等速ジョイントの外輪、軸 )への嵌合作業が困難になる、と記載されている。 [0007] For example, in paragraph [0005] of Patent Document 1, the retaining strength 4 and the seal of the fixing portion 4 of the boot are described. It is necessary to set the height of the convex part 5 of the fixed part 4 of the boot relatively large in order to ensure the smoothness. On the other hand, the grease boot is generally more rigid than the rubber boot with a hardness of about HD50. It is described that it is difficult to be elastically deformed, so that if the convex portion 5 is too high, it is difficult to fit the mating member (the outer ring and the shaft of the constant velocity joint).
[0008] しかしながら、前記特許文献 1及び特許文献 2に開示された榭脂ブーツの取付構 造では、ブーツの固定部 4をブーツバンド 6で締め付けた際、前記ブーツの固定部 4 の内壁に対して突起部 3a、 3bが食 、込むためにシール性が向上すると一応思われ るが、榭脂ブーツの固定部 4を外輪部材 1の端部に対して装着する嵌合作業を容易 に遂行するために前記凸部 5の高さを低く設定するとシール性を劣化させると共に、 ブーツバンド 6を締め付けたときに係合溝 2に対して前記凸部 5がうまく嵌合せずにブ ーッの固定部 4が外輪部材 1の奥側又は手前側にずれてしまいブーツ取付部に対し て確実な位置決めが困難である。  [0008] However, in the grease boot mounting structure disclosed in Patent Document 1 and Patent Document 2, when the boot fixing portion 4 is fastened with the boot band 6, the boot fixing portion 4 is against the inner wall of the boot fixing portion 4. The protrusions 3a and 3b are eaten up and inserted, and it seems that the sealing performance is improved. However, it is easy to perform the fitting work of attaching the fixing part 4 of the grease boot to the end of the outer ring member 1. Therefore, if the height of the convex portion 5 is set low, the sealing performance deteriorates, and when the boot band 6 is tightened, the convex portion 5 does not fit well with the engaging groove 2 and the fixing portion of the boot 4 shifts to the back side or the near side of the outer ring member 1 and it is difficult to reliably position the boot mounting portion.
[0009] 特許文献 1 :特開平 7— 280092号公報  Patent Document 1: Japanese Patent Application Laid-Open No. 7-280092
特許文献 2:特開平 11― 166624号公報  Patent Document 2: Japanese Patent Laid-Open No. 11-166624
発明の開示  Disclosure of the invention
[0010] 本発明の一般的な目的は、ブーツバンドを締め付けたときにブーツの固定部を外 輪部材のブーツ取付部に対して確実に且つ簡便に位置決めすることが可能な外輪 部材の端部形状を有する等速ジョイントを提供することにある。  [0010] A general object of the present invention is to provide an end portion of an outer ring member capable of reliably and simply positioning a fixed portion of the boot with respect to a boot mounting portion of the outer ring member when the boot band is tightened. The object is to provide a constant velocity joint having a shape.
[0011] 本発明では、外輪部材の端面力 前記傾斜面の頂部までの水平方向に沿って離 間する所定距離を L (mm)とし、前記被装着面に対する前記傾斜面の傾斜角度を Θ (度)とした場合、前記 L及び 0は、下記(1)〜(5)の関係式を充足する範囲に設定さ れるとよ 、。  In the present invention, the end surface force of the outer ring member is set to L (mm) as a predetermined distance separated along the horizontal direction to the top of the inclined surface, and the inclination angle of the inclined surface with respect to the mounting surface is Θ ( L and 0 are set in a range that satisfies the following relational expressions (1) to (5).
[0012] (l) L≤-0. 018 Θ + 15. 807  [0012] (l) L≤-0. 018 Θ + 15. 807
(2) L≤-0. 1438 θ + 21. 597  (2) L≤-0. 1438 θ + 21. 597
(3) L≥-0. 0885 θ + 16. 106  (3) L≥-0. 0885 θ + 16. 106
(4) θ≥20  (4) θ≥20
(5) θ≤60  (5) θ≤60
[0013] 本発明によれば、上記(1)〜(5)の関係式を全て充足する範囲に基づいて、外輪 部材の端面から傾斜面の頂部までの水平方向に沿って離間する所定距離 Lの値と、 被装着面に対する傾斜面の傾斜角度 Θの値とをそれぞれ設定することにより、ブー ッバンドを締め付けたときに、ブーツ固定部が外輪部材のブーツ取付部に対してず れることがなく確実に位置決めされ、さらに、所定のシール性を確保することができる と共に、加工性をも考慮した好適な外輪部材の端部形状を設定することができる。 [0013] According to the present invention, the outer ring is based on a range that satisfies all the relational expressions (1) to (5). When the boo- band is tightened by setting the value of the predetermined distance L that is spaced along the horizontal direction from the end surface of the member to the top of the inclined surface and the value of the inclination angle Θ of the inclined surface with respect to the mounting surface. In addition, the boot fixing portion is reliably positioned without being displaced with respect to the boot mounting portion of the outer ring member, and further, a predetermined sealing property can be secured, and a suitable outer ring member considering workability is also provided. The end shape can be set.
[0014] この場合、傾斜角度 Θが 20度未満であるとブーツ端部の傾斜面に対する乗り上げ 量が増大してシール性及び位置決め性が劣化すると共に、前記傾斜角度 Θ力 ½0度 を超えると前記傾斜面の機械加工が困難となる。  [0014] In this case, if the inclination angle Θ is less than 20 degrees, the amount of riding on the inclined surface of the boot end portion increases, the sealing performance and positioning performance deteriorate, and if the inclination angle Θ force exceeds ½0 degrees, Machining of inclined surfaces becomes difficult.
[0015] さらに、シール特性、位置決め性、及び加工性等を総合的に勘案された最適範囲 として、前記 L (mm)及び 0 (度)は、下記(6)、 (7)の関係式を全て充足する範囲に 設定されるとよい。  [0015] Further, as an optimal range that comprehensively considers seal characteristics, positioning properties, workability, etc., the L (mm) and 0 (degrees) are expressed by the following relational expressions (6) and (7). It should be set to a range that satisfies all.
[0016] (6) L= 14. 7±0. 3  [0016] (6) L = 14. 7 ± 0.3
(7) Θ =45± 1. 5  (7) Θ = 45 ± 1.5
図面の簡単な説明  Brief Description of Drawings
[0017] [図 1]本発明の実施の形態に係るトリポート型の等速ジョイントの軸線方向に沿った縦 断面図である。  FIG. 1 is a longitudinal sectional view along the axial direction of a tripart type constant velocity joint according to an embodiment of the present invention.
[図 2]図 1の等速ジョイントを構成する外輪部材の部分拡大縦断面図である。  2 is a partially enlarged longitudinal sectional view of an outer ring member constituting the constant velocity joint of FIG.
[図 3]第 1変形例に係る外輪部材の部分拡大縦断面図である。  FIG. 3 is a partially enlarged longitudinal sectional view of an outer ring member according to a first modification.
[図 4]第 2変形例に係る外輪部材の部分拡大縦断面図である。  FIG. 4 is a partially enlarged longitudinal sectional view of an outer ring member according to a second modification.
[図 5]図 1の等速ジョイントを構成するブーツの部分拡大縦断面図である。  5 is a partially enlarged longitudinal sectional view of a boot constituting the constant velocity joint of FIG.
[図 6]変形例に係るブーツの部分拡大縦断面図である。  FIG. 6 is a partially enlarged longitudinal sectional view of a boot according to a modification.
[図 7]Lと Θとの関係における許容範囲を示す特性図である。  FIG. 7 is a characteristic diagram showing an allowable range in the relationship between L and Θ.
[図 8]本発明の他の実施の形態に係るバーフィールド型の等速ジョイントの軸線方向 に沿った縦断面図である。  FIG. 8 is a longitudinal sectional view along the axial direction of a Barfield type constant velocity joint according to another embodiment of the present invention.
[図 9]従来技術におけるブーツ取付構造を示す部分拡大縦断面図である。  FIG. 9 is a partially enlarged longitudinal sectional view showing a boot mounting structure in the prior art.
発明を実施するための最良の形態  BEST MODE FOR CARRYING OUT THE INVENTION
[0018] 図 1において参照符号 10は、本発明の実施の形態に係るトリポート型の等速ジョイ ントを示し、この等速ジョイント 10は、図示しない第 1軸の一端部に一体的に連結され て開口部 11を有する有底円筒状の外輪部材 12と、第 2軸 14の一端部に固着されて 外輪部材 12の孔部内に収納されるインナ部材 16とを含む。 In FIG. 1, reference numeral 10 indicates a tripod type constant velocity joint according to an embodiment of the present invention, and this constant velocity joint 10 is integrally connected to one end of a first shaft (not shown). A bottomed cylindrical outer ring member 12 having an opening 11 and an inner member 16 fixed to one end of the second shaft 14 and housed in the hole of the outer ring member 12.
[0019] さらに前記等速ジョイント 10は、大径な固定部 18である一端部が前記外輪部材 12 の端部外周面 (後述するブーツ取付部 20)に嵌着され小径な固定部(図示せず)で ある他端部が前記第 2軸 14の外周部に嵌着される榭脂製のブーツ 22と、前記ブー ッ 22の大径な固定部 18を外輪部材 12のブーツ取付部 20に固定する大径なブーツ ノンド 24と、前記ブーツ 22の小径な固定部(図示せず)を第 2軸 14の外周面に固定 する小径なブーツバンド(図示せず)とを含む。  Furthermore, the constant velocity joint 10 has a small-diameter fixing portion (not shown) in which one end which is a large-diameter fixing portion 18 is fitted to an outer peripheral surface (boot mounting portion 20 described later) of the outer ring member 12. And the other end portion of the second shaft 14 fitted on the outer peripheral portion of the second shaft 14 and the large-diameter fixing portion 18 of the boot 22 to the boot mounting portion 20 of the outer ring member 12. A large-diameter boot nond 24 to be fixed and a small-diameter boot band (not shown) for fixing a small-diameter fixing portion (not shown) of the boot 22 to the outer peripheral surface of the second shaft 14 are included.
[0020] 前記外輪部材 12の内壁面には、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本の案内溝 26a〜26cが形成される(但し、案内溝 26b、 26cは図示するのを省略している)。前記案内溝 26a〜26cは、断面が曲線状に形 成された天井部と、前記天井部の両側に相互に対向し断面円弧状に形成された摺 動部とから構成される。  [0020] Three guide grooves 26a to 26c are formed on the inner wall surface of the outer ring member 12 so as to extend along the axial direction and have an interval of 120 degrees around the shaft center ( However, the guide grooves 26b and 26c are not shown). The guide grooves 26a to 26c are composed of a ceiling portion whose section is formed in a curved shape, and a sliding portion which is opposed to each other on both sides of the ceiling portion and is formed in an arc shape in section.
[0021] 第 2軸 14にはリング状部分を含むスパイダ 28がセレーシヨン嵌合され、前記スパイ ダ 28の外周面には、それぞれ案内溝 26a〜26cに向かって膨出し軸心の回りに 120 度の間隔をおいて 3本のトラ-オン 30a〜30cがー体的に形成される(但し、トラ-ォ ン 30cは、図示するのを省略している)。前記各トラ-オン 30a (30b、 30c)は、外径 が一定の円柱状に形成される。  [0021] A spider 28 including a ring-shaped portion is selectively fitted to the second shaft 14, and the outer surface of the spider 28 bulges toward the guide grooves 26a to 26c, and 120 degrees around the axis. Three traons 30a to 30c are formed in a body at intervals of the interval (however, the traon 30c is not shown). Each of the trillions 30a (30b, 30c) is formed in a columnar shape having a constant outer diameter.
[0022] 前記トラ-オン 30a (30b、 30c)の外周部には、複数本の転動体 32を介してリング 状のローラ部材 34が外嵌される。前記転動体 32は、例えば、ニードル、ころ等を含 む転がり軸受けであればよい。なお、前記転動体 32を設けることがなぐローラ部材( リング体)を前記トラ-オン 30a (30b, 30c)の外周面に対して摺動自在に直接装着 するようにしてちょい。  [0022] A ring-shaped roller member 34 is externally fitted to the outer periphery of the traon 30a (30b, 30c) via a plurality of rolling elements 32. The rolling element 32 may be a rolling bearing including a needle, a roller and the like, for example. It is to be noted that a roller member (ring body) that does not have the rolling element 32 is directly attached to the outer peripheral surface of the trolley 30a (30b, 30c) so as to be slidable.
[0023] 前記外輪部材 12は、開口部 11を有するカップ部 12aと、前記カップ部 12aと一体 的に形成された軸部 12bとから構成される。前記外輪部材 12の開口部 11側の端縁 部近傍の外周面には、ブーツ 22端部の大径な固定部 18が装着されるブーツ取付部 20が形成される。  [0023] The outer ring member 12 includes a cup portion 12a having an opening 11 and a shaft portion 12b formed integrally with the cup portion 12a. A boot mounting portion 20 to which a large-diameter fixing portion 18 at the end portion of the boot 22 is attached is formed on the outer peripheral surface in the vicinity of the edge portion on the opening 11 side of the outer ring member 12.
[0024] このブーツ取付部 20には、図 2に示されるように、開口部 11を有する外輪部材 12 の端面 35から軸部 12b側に向力つて所定幅だけ周方向に沿って切り欠いて形成さ れた断面略平坦な環状面からなる被装着面 36と、前記被装着面 36に連続する軸部 12b側に形成され、該断面略平坦な被装着面 36に対して傾斜角度 Θだけ傾斜する 環状の傾斜面 44とが設けられる。この場合、前記外輪部材 12の端面 35と前記傾斜 面 44の頂部 45との間の離間間隔であって、外輪部材 12の軸線 T1と平行な水平方 向に沿った所定距離を Lとする。 As shown in FIG. 2, the boot mounting portion 20 has an outer ring member 12 having an opening 11. A mounting surface 36 formed of an annular surface having a substantially flat cross-section formed by cutting along the circumferential direction by a predetermined width from the end surface 35 of the shaft to the shaft portion 12b side, and a shaft continuous to the mounting surface 36 An annular inclined surface 44 that is formed on the side of the portion 12b and is inclined by an inclination angle Θ with respect to the mounted surface 36 having a substantially flat cross section is provided. In this case, let L be a predetermined distance along the horizontal direction parallel to the axis T1 of the outer ring member 12, which is the spacing between the end surface 35 of the outer ring member 12 and the top 45 of the inclined surface 44.
[0025] なお、図 3に示されるように、断面略平坦に形成された被装着面 36の略中央部に 所定の溝底 42を有する係合溝 38を設けるように構成してもよい。また、図 4に示され るように、前記係合溝 38を間にしたその両側の近接した部位に、一対の環状突起部 40a、 40bを膨出形成してもよい。  In addition, as shown in FIG. 3, an engagement groove 38 having a predetermined groove bottom 42 may be provided at a substantially central portion of the mounted surface 36 having a substantially flat cross section. Further, as shown in FIG. 4, a pair of annular protrusions 40a and 40b may be formed to bulge out at adjacent portions on both sides of the engaging groove 38 therebetween.
[0026] ブーツ 22は山部と谷部とが交互に連続する断面波状に形成された蛇腹部を有し、 前記蛇腹部の一端部には、外輪部材 12のブーツ取付部 20の外径 D2に対応する内 径 D1からなる固定部 18が設けられ (図 5参照)、前記蛇腹部の他端部には、第 2軸 1 4の外径に対応して小径に形成された固定部(図示せず)が設けられる。なお、前記 ブーツ 22の固定部 18の内径 D1と前記外輪部材 12の外径 D2とは、 D1≤D2の関 係を充足するように設定される。  [0026] The boot 22 has a bellows portion having a corrugated section in which peaks and valleys are alternately continuous, and an outer diameter D2 of the boot mounting portion 20 of the outer ring member 12 is provided at one end portion of the bellows portion. (See FIG. 5), and the other end of the bellows part is provided with a fixing part (smaller diameter corresponding to the outer diameter of the second shaft 14). (Not shown). The inner diameter D1 of the fixing portion 18 of the boot 22 and the outer diameter D2 of the outer ring member 12 are set so as to satisfy the relationship of D1≤D2.
[0027] なお、図 6に示されるように、外輪部材 12のブーツ取付部 20に装着される前記固 定部 18には、外輪部材 12のブーツ取付部 20の係合溝 38 (図 3及び図 4参照)に係 合して位置決めされる環状凸部 46を膨出形成してもよい。また、図 5及び図 6におい て、 T2はブーツ 22の軸線を示している。  As shown in FIG. 6, the fixing portion 18 attached to the boot mounting portion 20 of the outer ring member 12 has an engaging groove 38 (see FIGS. 3 and 3) of the boot mounting portion 20 of the outer ring member 12. The annular protrusion 46 positioned in association with (see FIG. 4) may be bulged. In FIGS. 5 and 6, T2 represents the axis of the boot 22.
[0028] 本発明の実施の形態に係る等速ジョイント 10は、基本的には以上のように構成され るものであり、次に、外輪部材 12に対してブーツ 22の固定部 18が装着される外輪部 材 12の端部形状 (ブーツ取付部 20の形状)の設定手法について説明する。  The constant velocity joint 10 according to the embodiment of the present invention is basically configured as described above. Next, the fixing portion 18 of the boot 22 is attached to the outer ring member 12. A method for setting the end shape of the outer ring member 12 (the shape of the boot mounting portion 20) will be described.
[0029] 先ず、前述したように、前記ブーツ 22の固定部 18の内径 D1と前記外輪部材 12の ブーツ取付部 20の外径 D2とは、 D1≤D2の関係を充足するように設定されるとよい  [0029] First, as described above, the inner diameter D1 of the fixing portion 18 of the boot 22 and the outer diameter D2 of the boot mounting portion 20 of the outer ring member 12 are set so as to satisfy the relationship of D1≤D2. And good
[0030] 次に、外輪部材 12の端面 35から傾斜面 44の頂部 45までの間の離間間隔であつ て水平方向に沿って離間した所定距離 Lと、被装着面 36に対する傾斜面 44の傾斜 角度 Θとの関係が図 7に示される許容範囲 Μ内(網線部分参照)に設定されるとよい [0030] Next, a predetermined distance L between the end surface 35 of the outer ring member 12 and the top portion 45 of the inclined surface 44, which is spaced apart along the horizontal direction, and the inclination of the inclined surface 44 with respect to the mounting surface 36 The relationship with the angle Θ should be set within the allowable range shown in Fig. 7 (see the shaded area)
[0031] この許容範囲 Μは、前記 L (mm)と 0 (度)との間の下記(1)〜(5)の関係式を全て 充足する範囲であって、下記(1)〜(5)の関係式によって囲繞される領域によって設 定される。 [0031] This permissible range 範 囲 is a range that satisfies all the following relational expressions (1) to (5) between L (mm) and 0 (degrees), and includes the following (1) to (5 ) Is set by the area surrounded by the relational expression.
[0032] (l) L≤-0. 018 Θ + 15. 807  [0032] (l) L≤-0. 018 Θ + 15. 807
(2) L≤-0. 1438 θ + 21. 597  (2) L≤-0. 1438 θ + 21. 597
(3) L≥-0. 0885 θ + 16. 106  (3) L≥-0. 0885 θ + 16. 106
(4) θ≥20  (4) θ≥20
(5) θ≤60  (5) θ≤60
[0033] なお、図 7中において、直線(1)〜(5)は、それぞれ上記の関係式に対応する直線 を示している。この場合、傾斜角度 Θが 20度未満であるとブーツ 22端部の傾斜面 4 4に対する乗り上げ量が増大してシール性及び位置決め性が劣化すると共に、前記 傾斜角度 Θが 60度を超えると傾斜面 44の機械加工が困難となるからである。  In FIG. 7, straight lines (1) to (5) indicate straight lines corresponding to the above relational expressions, respectively. In this case, if the inclination angle Θ is less than 20 degrees, the amount of riding on the inclined surface 44 of the end of the boot 22 will increase and the sealing performance and positioning will deteriorate, and if the inclination angle Θ exceeds 60 degrees, the inclination will increase. This is because the machining of the surface 44 becomes difficult.
[0034] さらに、シール特性、位置決め性、及び加工性等を総合的に勘案すると最適範囲 Ν (斜線部分参照)は、前記 L (mm)と Θ (度)との下記(6)、(7)の関係式によって囲 繞される領域によって設定されるとよい。図 7中では、(6)式の内容を直線 (6A)と直 線 (6B)とに分けて示し、 (7)式の内容を直線 (7A)と直線 (7B)とに分けて示して ヽ る。  [0034] Furthermore, considering the seal characteristics, positioning properties, workability, etc., the optimum range Ν (see shaded area) is the following (6), (7) of L (mm) and Θ (degrees) ) Should be set according to the area surrounded by the relational expression. In Fig. 7, the contents of Eq. (6) are divided into straight lines (6A) and straight lines (6B), and the contents of Eq. (7) are divided into straight lines (7A) and straight lines (7B).ヽ.
[0035] (6) L= 14. 7±0. 3  [0035] (6) L = 14. 7 ± 0.3
(7) Θ =45± 1. 5  (7) Θ = 45 ± 1.5
[0036] なお、前記(1)〜(7)の関係式は、実験及びシミュレーションによって求められたも のである。  [0036] The relational expressions (1) to (7) are obtained through experiments and simulations.
[0037] 本実施の形態では、以上のように設定された許容範囲 Mに基づいて外輪部材 12 の端部形状 (ブーツ取付部 20の形状)を設定することにより、ブーツバンド 24を締め 付けたときにブーツ 22の固定部 18を外輪部材 12のブーツ取付部 20に対して確実 に位置決めすることができる。  In the present embodiment, the boot band 24 is tightened by setting the end shape of the outer ring member 12 (the shape of the boot mounting portion 20) based on the allowable range M set as described above. Sometimes, the fixing portion 18 of the boot 22 can be reliably positioned with respect to the boot mounting portion 20 of the outer ring member 12.
[0038] 換言すると、図 7に示される許容範囲 Mにおいて外輪部材 12の端面力も被装着面 36を経由し前記被装着面 36に連続する傾斜面 44の頂部 45との間で離間する所定 距離 Lの値と、被装着面 36に対する傾斜面 44の傾斜角度 Θの値とをそれぞれ設定 することにより、ブーツバンド 24を締め付けたときに、該ブーツ 22の固定部 18が軸部 12b側又は端面 35側にずれることがなくブーツ取付部 20に対して確実に位置決め され、さらに、所定のシール性を確保することができると共に、加工性をも考慮した好 適な外輪部材 12の端部形状を設定することができる。 [0038] In other words, the end surface force of the outer ring member 12 in the allowable range M shown in FIG. The value of a predetermined distance L that is separated from the top 45 of the inclined surface 44 that continues to the mounted surface 36 via 36 and the value of the inclination angle Θ of the inclined surface 44 with respect to the mounted surface 36 are set. Thus, when the boot band 24 is tightened, the fixing portion 18 of the boot 22 is securely positioned with respect to the boot mounting portion 20 without being displaced toward the shaft portion 12b side or the end surface 35 side. As a result, it is possible to set a suitable end shape of the outer ring member 12 in consideration of workability.
[0039] この場合、本実施の形態では、外輪部材 12の端面 35をその基準面として確定し、 前記外輪部材 12の端面 35から傾斜面 44の頂部 45までの所定距離を Lとする簡素( 単純)な形状によって設定されているため、外輪部材 12の端部形状の設定手法を簡 便化することができると共に、外輪部材 12の端部形状を容易に設定'変更することが できる。 [0039] In this case, in the present embodiment, the end surface 35 of the outer ring member 12 is determined as the reference surface, and a simple distance from the end surface 35 of the outer ring member 12 to the top 45 of the inclined surface 44 is L ( Since it is set by a simple shape, the method for setting the end shape of the outer ring member 12 can be simplified, and the end shape of the outer ring member 12 can be easily set and changed.
[0040] なお、本実施の形態では、市販の汎用ブーツを前提として、外輪部材 12の端部形 状 (ブーツ取付部 20の形状)を容易に設定することが可能となり、効率的に大量生産 することができてコストダウンを図ることができる。  [0040] In the present embodiment, it is possible to easily set the end shape of the outer ring member 12 (the shape of the boot mounting portion 20) on the assumption of a commercially available general-purpose boot, and mass production can be performed efficiently. This can reduce costs.
[0041] さらに、上記の実施の形態では、トリポート型等速ジョイント 10を構成する外輪部材 12の端部形状 (ブーツ取付部 20の形状)について説明しているが、これに限定され るものではなぐ図 8に示されるようなバーフィールド型の等速ジョイント 100の外輪部 材 102の端部形状に対しても適用することが可能である。なお、同一の構成要素に は同一の参照符号を付してその詳細な説明を省略する。  Furthermore, in the above embodiment, the end shape of the outer ring member 12 (the shape of the boot mounting portion 20) constituting the tripod type constant velocity joint 10 is described, but the present invention is not limited to this. The present invention can also be applied to the end shape of the outer ring member 102 of the Barfield type constant velocity joint 100 as shown in FIG. Note that the same components are denoted by the same reference numerals, and detailed description thereof is omitted.
[0042] この等速ジョイント 100は、図示しない第 1軸に連結される軸部 102bを有する外輪 部材 102と、第 2軸 104に連結されて前記外輪部材 102の開口部 106内に収容され るインナ部材 108とから構成される。  The constant velocity joint 100 is accommodated in an outer ring member 102 having a shaft portion 102b connected to a first shaft (not shown) and an opening 106 of the outer ring member 102 connected to the second shaft 104. And an inner member 108.
[0043] 前記外輪部材 102の内壁には軸方向に沿って延在し、軸心の回りにそれぞれ 60 度の間隔をおいて 6本の第 1案内溝 110が形成される。  [0043] Six first guide grooves 110 are formed on the inner wall of the outer ring member 102 so as to extend along the axial direction and are spaced by 60 degrees around the axis.
[0044] インナ部材 108は、外周面の周方向に沿って前記第 1案内溝 110に対応する複数 の第 2案内溝 112が形成されたインナリング 114と、前記外輪部材 102の内壁面に 形成された第 1案内溝 110と前記インナリング 114の外径面に形成された第 2案内溝 112との間で転動可能に配設され、回転トルク伝達機能を営む複数 (例えば、 6個) のボール 116と、前記ボール 116を保持する複数の保持窓 118が周方向に沿って形 成され外輪部材 102と前記インナリング 114との間に介装されたリテーナ 120とを備 える。 [0044] The inner member 108 is formed on the inner ring 114 formed with a plurality of second guide grooves 112 corresponding to the first guide grooves 110 along the circumferential direction of the outer peripheral surface, and on the inner wall surface of the outer ring member 102. A plurality of (for example, six) rotating torque transmitting functions disposed between the first guiding groove 110 formed on the outer ring 114 and the second guiding groove 112 formed on the outer diameter surface of the inner ring 114. And a retainer 120 formed between the outer ring member 102 and the inner ring 114. The retainer 118 is formed along the circumferential direction.
なお、外輪部材 102の端部に設けられる所定距離 L及び傾斜面 44の傾斜角度 Θ の設定等は、トリポート型の外輪部材 12と同様に設定範囲 M又は最適範囲 Nに基づ いてなされるため、その詳細な説明を省略する。  The setting of the predetermined distance L provided at the end portion of the outer ring member 102 and the inclination angle Θ of the inclined surface 44 is based on the setting range M or the optimum range N as in the case of the tripod type outer ring member 12. Detailed description thereof will be omitted.

Claims

請求の範囲 [1] 榭脂製のブーツ (22)の端部に設けられた筒状の固定部(18)を外輪部材(12)の 端部に形成されたブーツ取付部(20)に装着した後、前記ブーツ (22)の固定部(18 )をブーツバンド(24)で緊締することにより、前記ブーツ(22)の固定部(18)が前記 外輪部材(12)のブーツ取付部(20)に固定される等速ジョイントにおいて、 前記外輪部材(12)のブーツ取付部(20)には、前記ブーツ(22)の固定部(18)が 装着され該外輪部材(12)の端面 (35)力 軸方向に沿って延在する被装着面 (36) と、前記被装着面 (36)に連続し該被装着面 (36)に対して所定角度傾斜する環状の 傾斜面 (44)とが設けられ、 前記外輪部材(12)の端面(35)から前記傾斜面 (44)の頂部 (45)までの水平方向 に沿って離間する所定距離を Lとし、前記被装着面 (36)に対する前記傾斜面 (44) の傾斜角度を 0とした場合、前記 L (mm)及び 0 (度)は、下記(1)〜(5)の関係式を 充足する範囲に設定されることを特徴とする等速ジョイント。 Claims [1] A cylindrical fixing portion (18) provided at the end portion of the resin-made boot (22) is attached to the boot mounting portion (20) formed at the end portion of the outer ring member (12). After that, the fixing portion (18) of the boot (22) is fastened with the boot band (24), so that the fixing portion (18) of the boot (22) becomes the boot mounting portion (20 of the outer ring member (12)). ) Is fixed to the boot mounting portion (20) of the outer ring member (12), and the fixing portion (18) of the boot (22) is attached to the end surface (35) of the outer ring member (12). A mounting surface (36) extending along the axial direction, and an annular inclined surface (44) continuous to the mounting surface (36) and inclined at a predetermined angle with respect to the mounting surface (36). And a predetermined distance spaced apart along the horizontal direction from the end surface (35) of the outer ring member (12) to the top (45) of the inclined surface (44) is L, and is relative to the mounted surface (36). The inclination of the inclined surface (44) A constant velocity joint characterized in that when the oblique angle is 0, the L (mm) and 0 (degrees) are set within a range satisfying the following relational expressions (1) to (5).
(1) L≤-0. 018 Θ + 15. 807  (1) L≤-0. 018 Θ + 15. 807
(2) L≤-0. 1438 θ + 21. 597  (2) L≤-0. 1438 θ + 21. 597
(3) L≥-0. 0885 θ + 16. 106  (3) L≥-0. 0885 θ + 16. 106
(4) θ≥20  (4) θ≥20
(5) θ≤60  (5) θ≤60
[2] 請求項 1記載の等速ジョイントにおいて、  [2] In the constant velocity joint according to claim 1,
前記 L (mm)及び 0 (度)は、下記(6)、(7)の関係式を充足する範囲に設定される ことを特徴とする等速ジョイント。  The L (mm) and 0 (degrees) are set within a range satisfying the following relational expressions (6) and (7).
(6) L= 14. 7±0. 3  (6) L = 14. 7 ± 0.3
(7) Θ =45± 1. 5  (7) Θ = 45 ± 1.5
[3] 請求項 1記載の等速ジョイントにおいて、  [3] The constant velocity joint according to claim 1,
前記被装着面(36)は、断面略平坦な環状面からなることを特徴とする等速ジョイン  The mounted surface (36) comprises an annular surface having a substantially flat cross section.
[4] 請求項 3記載の等速ジョイントにお 、て、 [4] In the constant velocity joint according to claim 3,
前記断面略平坦な環状面の略中央部には、所定の溝底 (42)を有する係合溝 (38 )が設けられることを特徴とする等速ジョイント。 An engagement groove (38) having a predetermined groove bottom (42) is formed at a substantially central portion of the annular surface having a substantially flat cross section. ) Is provided.
[5] 請求項 4記載の等速ジョイントにお 、て、 [5] In the constant velocity joint according to claim 4,
前記係合溝(38)を間にしたその両側の近接部位には、一対の環状突起部 (40a、 40b)が膨出形成されることを特徴とする等速ジョイント。  A constant velocity joint, characterized in that a pair of annular protrusions (40a, 40b) bulge out at adjacent portions on both sides of the engagement groove (38).
[6] 請求項 4記載の等速ジョイントにお 、て、 [6] In the constant velocity joint according to claim 4,
前記ブーツ (22)の固定部(18)には、前記係合溝 (38)に係合する環状凸部 (46) が膨出形成されることを特徴とする等速ジョイント。  The constant velocity joint according to claim 1, wherein an annular convex portion (46) that engages with the engaging groove (38) is formed bulging in the fixing portion (18) of the boot (22).
PCT/JP2006/306038 2005-05-25 2006-03-24 Constant velocity joint WO2006126328A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2005-152360 2005-05-25
JP2005152360A JP2006329299A (en) 2005-05-25 2005-05-25 Uniform joint

Publications (1)

Publication Number Publication Date
WO2006126328A1 true WO2006126328A1 (en) 2006-11-30

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Application Number Title Priority Date Filing Date
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WO (1) WO2006126328A1 (en)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH01118227U (en) * 1988-02-03 1989-08-10
JPH07280094A (en) * 1994-02-24 1995-10-27 Draftex Ind Ltd Protection bellows
JPH09177993A (en) * 1995-12-27 1997-07-11 Ntn Corp Boot attaching structure
JPH11166624A (en) * 1997-09-30 1999-06-22 Ntn Corp Constant velocity universal joint

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH01118227U (en) * 1988-02-03 1989-08-10
JPH07280094A (en) * 1994-02-24 1995-10-27 Draftex Ind Ltd Protection bellows
JPH09177993A (en) * 1995-12-27 1997-07-11 Ntn Corp Boot attaching structure
JPH11166624A (en) * 1997-09-30 1999-06-22 Ntn Corp Constant velocity universal joint

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