JPH09317783A - Fixed type constant velocity universal joint for automobile - Google Patents

Fixed type constant velocity universal joint for automobile

Info

Publication number
JPH09317783A
JPH09317783A JP13399896A JP13399896A JPH09317783A JP H09317783 A JPH09317783 A JP H09317783A JP 13399896 A JP13399896 A JP 13399896A JP 13399896 A JP13399896 A JP 13399896A JP H09317783 A JPH09317783 A JP H09317783A
Authority
JP
Japan
Prior art keywords
ball
joint member
center
guide groove
diameter surface
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.)
Granted
Application number
JP13399896A
Other languages
Japanese (ja)
Other versions
JP3859264B2 (en
Inventor
Keisuke Sone
啓助 曽根
Kazuhiko Hozumi
和彦 穂積
Yoshihisa Kaneko
佳久 兼子
Tatsuro Sugiyama
達朗 杉山
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
NTN Corp
Original Assignee
NTN Corp
NTN Toyo Bearing 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
Priority to JP13399896A priority Critical patent/JP3859264B2/en
Application filed by NTN Corp, NTN Toyo Bearing Co Ltd filed Critical NTN Corp
Priority to DE69636726T priority patent/DE69636726T2/en
Priority to DE69636727T priority patent/DE69636727T2/en
Priority to EP02003007A priority patent/EP1209373B1/en
Priority to US08/860,719 priority patent/US6120382A/en
Priority to KR1019970705290A priority patent/KR100472985B1/en
Priority to EP02003004A priority patent/EP1209372B1/en
Priority to EP96942575A priority patent/EP0802341B2/en
Priority to PCT/JP1996/003702 priority patent/WO1997024538A1/en
Priority to CN96192137A priority patent/CN1087817C/en
Priority to AU11711/97A priority patent/AU714553B2/en
Priority to DE69623439T priority patent/DE69623439T3/en
Priority to TW086104441A priority patent/TW368566B/en
Publication of JPH09317783A publication Critical patent/JPH09317783A/en
Priority to US09/500,532 priority patent/US6386983B1/en
Priority to US09/500,649 priority patent/US6267682B1/en
Priority to CNB021015333A priority patent/CN1260487C/en
Application granted granted Critical
Publication of JP3859264B2 publication Critical patent/JP3859264B2/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
    • F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
    • F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
    • F16D3/224—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts the groove centre-lines in each coupling part lying on a sphere
    • F16D3/2245—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts the groove centre-lines in each coupling part lying on a sphere where the groove centres are offset from the joint centre
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
    • F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
    • F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
    • F16D2003/22303—Details of ball cages

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

PROBLEM TO BE SOLVED: To simplify a universal joint and secure its strength, load capacity, and durability by providing an outer joint member having 8 curved guide grooves formed in its inner diameter face, an inner joint member having 8 curved guide grooves and a shaft part connected tooth formed in the outer diameter face and an inner diameter face respectively, 8 balls in both guide grooves, and their cage. SOLUTION: A fixed type constant velocity universal joint is constituted of an outer race 1 as an outer joint member having 8 curved guide grooves 1b formed axially in an inner diameter face 1a, an inner race 2 as an inner joint member having 8 curved guide grooves 2b formed axially in the outer diameter face 2a and a serration 2c for connecting a shaft part 5 formed in the inner diameter face, 8 balls 3 arranged in a ball track which is formed from guide grooves 1b, 2b, and a cage 4 for holding them. The ratio r1 of pitch circle diameter of the ball 3 to the diameter is set to 3.3<=r1<=5.0 and the ratio r2 of the outer diameter of the outer race 1 to the pitch circle diameter of the serration 2c of the inner race 2 is set to 2.5<=r2<=3.5. This constitution can secure the strength, load capacity, and durability and simplify the universal joint.

Description

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

【０００１】[0001]

【発明の属する技術分野】本発明は、８個のボールを備
えた自動車用固定型等速自在継手に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a fixed type constant velocity universal joint for automobiles having eight balls.

【０００２】[0002]

【発明が解決しようとする課題】等速自在継手には、大
別して、２軸間の角度変位のみを許容する固定型と、角
度変位および軸方向変位を許容する摺動型とがある。自
動車のドライブシャフトやプロペラシャフトの連結に
は、通常、固定型と摺動型の等速自在継手を一対として
用いる。The constant velocity universal joints are roughly classified into a fixed type that allows only angular displacement between two axes and a sliding type that allows angular displacement and axial displacement. A fixed type and a sliding type constant velocity universal joint are usually used as a pair for connecting a drive shaft and a propeller shaft of an automobile.

【０００３】例えば、自動車のエンジンの動力を車輪に
伝達する動力伝達装置は、エンジンと車輪との相対的位
置関係の変化による角度変位と軸方向変位に対応する必
要があるため、図１４に示すように、エンジン側と車輪
側との間に介装されるドライブシャフト１０の一端を摺
動型等速自在継手１１を介してディファレンシャル１２
に連結し、他端を固定型等速自在継手１３を介して車輪
１４に連結している。For example, a power transmission device for transmitting the power of an automobile engine to a wheel needs to cope with an angular displacement and an axial displacement due to a change in a relative positional relationship between the engine and the wheel, and therefore is shown in FIG. As described above, one end of the drive shaft 10 interposed between the engine side and the wheel side is connected to the differential 12 through the sliding type constant velocity universal joint 11.
, And the other end is connected to a wheel 14 via a fixed type constant velocity universal joint 13.

【０００４】摺動型と比較した場合の、固定型等速自在
継手の特徴の一つは、高作動角をとれることである。上
記のような自動車のドライブシャフト用固定型等速自在
継手では、最大作動角４５°以上が必要とされる。一
方、固定型等速自在継手は、摺動型に比べ、内部構造が
やや複雑にならざるをえない。One of the features of the fixed type constant velocity universal joint as compared with the sliding type is that a high working angle can be obtained. A fixed type constant velocity universal joint for a drive shaft of an automobile as described above requires a maximum operating angle of 45 ° or more. On the other hand, the fixed type constant velocity universal joint has a slightly complicated internal structure as compared with the sliding type.

【０００５】図１５に示すのは、固定型等速自在継手と
して代表的なツェパー型等速自在継手である。この等速
自在継手は、内径面１１ａに６本の曲線状の案内溝１１
ｂを軸方向に形成した外側継手部材としての外輪１１
と、外径面１２ａに６本の曲線状の案内溝１２ｂを軸方
向に形成し、内径面に軸部を連結するためのセレーショ
ン（又はスプライン）１２ｃを形成した内側継手部材と
しての内輪１２と、外輪１１の案内溝１１ｂと内輪１２
の案内溝１２ｂとが協働して形成されるボールトラック
に配された６個のボール１３と、ボール１３を保持する
保持器１４とで構成される。FIG. 15 shows a Zepper type constant velocity universal joint, which is a typical fixed type constant velocity universal joint. This constant velocity universal joint has six curved guide grooves 11 on the inner diameter surface 11a.
Outer ring 11 as an outer joint member in which b is formed in the axial direction
And an inner ring 12 as an inner joint member in which six curved guide grooves 12b are formed in the outer diameter surface 12a in the axial direction and serrations (or splines) 12c for connecting the shaft portion are formed in the inner diameter surface. , The guide groove 11b of the outer ring 11 and the inner ring 12
6 balls 13 arranged on a ball track formed in cooperation with the guide groove 12b of the above, and a cage 14 for holding the balls 13.

【０００６】外輪１１の案内溝１１ｂの中心Ａは内径面
１１ａの球面中心に対して、内輪１２の案内溝１２ｂの
中心Ｂは外径面１２ａの球面中心に対して、それぞれ、
軸方向に等距離だけ反対側に（球面中心Ａは継手の開口
側、球面中心Ｂは継手の奥部側に）オフセットされてい
る。保持器１４の案内面となる外輪１１の内径面１１ａ
および内輪１２の外径面１２ａの球面中心は、いずれも
継手中心面Ｏ内にある。The center A of the guide groove 11b of the outer ring 11 is with respect to the spherical center of the inner diameter surface 11a, and the center B of the guide groove 12b of the inner ring 12 is with respect to the spherical center of the outer diameter surface 12a.
It is offset by an equal distance in the axial direction on the opposite side (the spherical center A is on the opening side of the joint, and the spherical center B is on the rear side of the joint). Inner diameter surface 11a of the outer ring 11 serving as a guide surface of the cage 14.
The spherical center of the outer diameter surface 12a of the inner ring 12 is located within the joint center plane O.

【０００７】外輪１１と内輪１２とが角度θだけ角度変
位すると、保持器１４に案内されたボール１３は常にど
の作動角θにおいても、角度θの２等分面（θ／２）内
に維持され、そのため継手の等速性が確保される。When the outer ring 11 and the inner ring 12 are angularly displaced by the angle θ, the ball 13 guided by the retainer 14 is always maintained within the bisecting plane (θ / 2) of the angle θ at any operating angle θ. Therefore, the uniform speed of the joint is ensured.

【０００８】本発明は、固定型等速自在継手において、
より一層のコンパクト化を図り、また、比較品（上述し
たような６個ボールの固定型等速自在継手）と同等以上
の強度、負荷容量および耐久性を確保し、特に自動車の
動力伝達装置用として好適な固定型等速自在継手を提供
しようとするものである。The present invention relates to a fixed type constant velocity universal joint,
Further compactness is achieved, and strength, load capacity and durability equivalent to or better than those of the comparative product (fixed type constant velocity universal joint with 6 balls as described above) are secured, especially for power transmission devices of automobiles. The present invention aims to provide a fixed type constant velocity universal joint suitable as

【０００９】[0009]

【課題を解決するための手段】上記課題を解決するた
め、本発明は、内径面に８本の曲線状の案内溝を形成し
た外側継手部材と、外径面に８本の曲線状の案内溝を形
成し、内径面に軸部を連結するための歯型を形成した内
側継手部材と、外側継手部材の案内溝と内側継手部材の
案内溝とが協働して形成されるボールトラックに配され
た８個のボールと、ボールを保持する保持器とを備え、
自動車の動力伝達装置に用いられる構成を提供する（請
求項１）。In order to solve the above-mentioned problems, the present invention provides an outer joint member having eight curved guide grooves formed on the inner diameter surface and eight curved guide members on the outer diameter surface. A ball track in which a groove is formed and an inner joint member having an inner diameter surface formed with a tooth profile for connecting a shaft portion, and a guide groove of the outer joint member and a guide groove of the inner joint member are formed in cooperation with each other. Equipped with eight balls arranged and a retainer for holding the balls,
A structure used for a power transmission device of an automobile is provided (Claim 1).

【００１０】上記構成に加え、ボールのピッチ円径（Ｐ
ＣＤBALL）と直径（ＤBALL）との比ｒ１（＝ＰＣＤBALL
／ＤBALL）を３．３≦ｒ１≦５．０の範囲内とすると良
い（請求項２）。ここで、ボールのピッチ円径（ＰＣＤ
BALL）は、外側継手部材の案内溝の中心又は内側継手部
材の案内溝の中心とボールの中心とを結ぶ線分の長さ
｛外側継手部材の案内溝の中心とボールの中心とを結ぶ
線分の長さと、内側継手部材の案内溝の中心とボールの
中心とを結ぶ線分の長さとは等しい。これにより、継手
の等速性が確保される。以下、この寸法を（ＰＣＲ）と
いう。｝の２倍（ＰＣＤBALL＝２×ＰＣＲ）である。In addition to the above structure, the pitch circle diameter of the ball (P
Ratio r1 (= PCD BALL ) between CD BALL ) and diameter (D BALL )
/ D BALL ) is preferably in the range of 3.3 ≦ r1 ≦ 5.0 (claim 2). Here, the pitch circle diameter of the ball (PCD
BALL ) is the length of the line segment that connects the center of the guide groove of the outer joint member or the center of the guide groove of the inner joint member and the center of the ball (the line that connects the center of the guide groove of the outer joint member and the center of the ball). The length of the minute portion is equal to the length of a line segment connecting the center of the guide groove of the inner joint member and the center of the ball. This ensures the uniform speed of the joint. Hereinafter, this dimension is referred to as (PCR). } Twice (PCD BALL = 2 × PCR).

【００１１】３．３≦ｒ１≦５．０とした理由は、外輪
等の強度、継手の負荷容量および耐久性を比較品（６個
ボールの固定型等速自在継手）と同等以上に確保するた
めである。すなわち、等速自在継手においては、限られ
たスペースの範囲で、ボールのピッチ円径（ＰＣ
ＤBALL）を大幅に変更することは困難である。そのた
め、ｒ１の値は、主にボールの直径（ＤBALL）に依存す
ることになる。ｒ１〈３．３であると（主に直径ＤBALL
が大きい場合）、他の部品（外輪、内輪等）の肉厚が薄
くなりすぎて、強度の点で懸念が生じる。逆に、ｒ１〉
５．０であると（主に直径ＤBALLが小さい場合）、負荷
容量が小さくなり、耐久性の点で懸念が生じる。３．３
≦ｒ１≦５．０とすることにより、外輪等の強度、継手
の負荷容量および耐久性を比較品（６個ボール）と同等
以上に確保することができる。このことは、試験によ
り、ある程度裏付けされている。The reason for 3.3 ≦ r1 ≦ 5.0 is that the strength of the outer ring, the load capacity and the durability of the joint are ensured to be equal to or higher than those of the comparative product (fixed type constant velocity universal joint with 6 balls). This is because. That is, in a constant velocity universal joint, the pitch circle diameter of the ball (PC
It is difficult to change D BALL ) drastically. Therefore, the value of r1 mainly depends on the diameter of the ball (D BALL ). r1 <3.3 (mainly diameter D BALL
Is large), the wall thickness of other parts (outer ring, inner ring, etc.) becomes too thin, and there is concern about strength. Conversely, r1>
When it is 5.0 (mainly when the diameter D BALL is small), the load capacity becomes small and there is a concern in terms of durability. 3.3
By setting ≦ r1 ≦ 5.0, the strength of the outer ring and the like, the load capacity and the durability of the joint can be secured to be equal to or higher than that of the comparative product (6 balls). This has been confirmed to some extent by tests.

【００１２】[0012]

【表２】 [Table 2]

【００１３】表２に示すように（表２は比較試験に基づ
く評価を示している。）、ｒ１＝３．２とした場合で
は、外輪、内輪、保持器の強度が十分に確保されず、好
ましくない結果が得られた。ｒ１＝３．３、３．４とし
た場合では、強度面でもまずまず良好な結果が得られ
た。特に、ｒ１≧３．５とした場合では、外輪、内輪、
保持器の強度および継手の耐久性が十分に確保され、好
ましい結果が得られた。尚、ｒ１〉３．９の範囲内につ
いては、まだ試験は行なっていないが、上記と同様に好
ましい結果が得られるものと推測される。ただし、ｒ
１〉５．０になると、耐久性の点が問題になると考えら
れるので、ｒ１≦５．０とするのが良い。As shown in Table 2 (Table 2 shows the evaluation based on the comparative test), when r1 = 3.2, the strengths of the outer ring, the inner ring and the cage were not sufficiently secured, Poor results were obtained. In the case of r1 = 3.3, 3.4, good results were obtained in terms of strength. In particular, when r1 ≧ 3.5, the outer ring, the inner ring,
The strength of the cage and the durability of the joint were sufficiently ensured, and favorable results were obtained. Although the test has not been carried out for the range of r1> 3.9, it is presumed that preferable results are obtained in the same manner as described above. Where r
When 1> 5.0, durability is considered to be a problem, so r1 ≦ 5.0 is preferable.

【００１４】以上により、ｒ１は、３．３≦ｒ１≦５．
０の範囲内、好ましくは、３．５≦ｒ１≦５．０の範囲
内に設定するのが良い。From the above, r1 is 3.3 ≦ r1 ≦ 5.
It is preferable to set it within the range of 0, preferably within the range of 3.5 ≦ r1 ≦ 5.0.

【００１５】また、上記構成に加え、さらに、外側継手
部材の外径（ＤOUTER）と内側継手部材の歯型のピッチ
円径（ＰＣＤSERR）との比ｒ２（＝ＤOUTER／ＰＣＤ
SERR）を２．５≦ｒ２≦３．５の範囲内とすると良い
（請求項３）。In addition to the above structure, the ratio r2 (= D OUTER / PCD) of the outer diameter (D OUTER ) of the outer joint member and the pitch circle diameter (PCD SERR ) of the tooth mold of the inner joint member.
It is preferable that SERR ) is within the range of 2.5 ≦ r2 ≦ 3.5 (claim 3).

【００１６】２．５≦ｒ２≦３．５とした理由は次にあ
る。すなわち、内側継手部材の歯型のピッチ円径（ＰＣ
ＤSERR）は、相手軸の強度等との関係で大幅に変更する
ことはできない。そのため、ｒ２の値は、主に外側継手
部材の外径（ＤOUTER）に依存することになる。ｒ２
〈２．５であると（主に外径ＤOUTERが小さい場合）、
各部品（外輪、内輪等）の肉厚が薄くなりすぎて、強度
の点で懸念が生じる。一方、ｒ２〉３．５であると（主
に外径ＤOUTERが大きい場合）、寸法的な面等から実用
上の問題が生じる場合があり、また、コンパクト化とい
う目的も達成できない。２．５≦ｒ２≦３．５とするこ
とにより、外輪等の強度および継手の耐久性を比較品
（６個ボール）と同等以上に確保することができ、か
つ、実用上の要請も満足できる。特に、２．５≦ｒ２
〈３．２とすることにより、同じ呼び形式の比較品（６
個ボール）に対して、外径寸法をコンパクト化できると
いうメリットがある。The reason for setting 2.5 ≦ r2 ≦ 3.5 is as follows. That is, the pitch circle diameter (PC
D SERR ) cannot be changed significantly due to the strength of the mating shaft. Therefore, the value of r2 mainly depends on the outer diameter (D OUTER ) of the outer joint member. r2
<2.5 (mainly when the outer diameter D OUTER is small)
The thickness of each component (outer ring, inner ring, etc.) becomes too thin, which causes concern about strength. On the other hand, if r2> 3.5 (mainly when the outer diameter D OUTER is large), there may be a practical problem in terms of dimension and the like, and the object of downsizing cannot be achieved. By setting 2.5 ≦ r2 ≦ 3.5, the strength of the outer ring and the durability of the joint can be secured to be equal to or higher than that of the comparative product (6 balls), and the requirements for practical use can be satisfied. . In particular, 2.5 ≦ r2
<By setting 3.2, a comparison product (6
The advantage is that the outer diameter can be made smaller than the individual balls.

【００１７】以上により、ｒ２は、２．５≦ｒ２≦３．
５の範囲内、好ましくは、２．５≦ｒ２〈３．２の範囲
内に設定するのが良い。From the above, r2 is 2.5 ≦ r2 ≦ 3.
It is preferable to set it within the range of 5, preferably within the range of 2.5 ≦ r2 <3.2.

【００１８】また、本発明は、内径面に８本の曲線状の
案内溝を形成した外側継手部材と、外径面に８本の曲線
状の案内溝を形成し、内径面に軸部を連結するための歯
型を形成した内側継手部材と、外側継手部材の案内溝と
内側継手部材の案内溝とが協働して形成されるボールト
ラックに配された８個のボールと、ボールを保持する保
持器とを備え、自動車の動力伝達装置に用いられるもの
であって、外側継手部材の案内溝の中心が内径面の球面
中心に対して、内側継手部材の案内溝の中心が外径面の
球面中心に対して、それぞれ、軸方向に等距離（Ｆ）だ
け反対側にオフセットされ、前記オフセット量（Ｆ）
と、前記（ＰＣＲ）との比Ｒ１（＝Ｆ／ＰＣＲ）が、
０．０６９≦Ｒ１≦０．１２１の範囲内である構成を提
供する（請求項４）。Further, according to the present invention, an outer joint member having eight curved guide grooves formed on the inner diameter surface and eight curved guide grooves formed on the outer diameter surface, and the shaft portion is provided on the inner diameter surface. Eight balls arranged on a ball track formed by cooperation of an inner joint member having a tooth profile for connection, a guide groove of the outer joint member and a guide groove of the inner joint member, and a ball. A retainer for holding is used for a power transmission device of an automobile, wherein the center of the guide groove of the outer joint member is the spherical center of the inner diameter surface, and the center of the guide groove of the inner joint member is the outer diameter. Each of them is offset to the opposite side by an equal distance (F) in the axial direction with respect to the spherical center of the surface, and the offset amount (F)
And the ratio R1 (= F / PCR) with the above (PCR) is
A configuration is provided within the range of 0.069 ≦ R1 ≦ 0.121 (claim 4).

【００１９】０．０６９≦Ｒ１≦０．１２１とした理由
は次にある。ＰＣＲを固定して考えた場合、一般に、作
動角付与時、オフセット量（Ｆ）が大きいほどトラック
荷重（案内溝とボールとの接触部分に加わる荷重）は減
少するので、トラック荷重の点では、オフセット量
（Ｆ）が大きい方が有利であると言える。The reason for setting 0.069≤R1≤0.121 is as follows. When the PCR is fixed, generally, when the operating angle is applied, the larger the offset amount (F) is, the smaller the track load (the load applied to the contact portion between the guide groove and the ball) is. Therefore, in terms of the track load, It can be said that it is advantageous that the offset amount (F) is large.

【００２０】しかし、オフセット量（Ｆ）が大きすぎる
と： （I）高作動角域でトラックが浅くなり、許容負荷トル
クの低下を招く； （II）保持器のポケット内での、ボールの径方向移動量
が大きくなるので、ボールの脱落を防止するため、保持
器の肉厚（径方向寸法）を大きくする必要が生じる。そ
のため、トラックが浅くなり、許容負荷トルクの低下を
招く； （III）保持器のポケット内での、ボールの周方向移動
量が大きくなるので、ボールの適正な運動を確保するた
め、保持器のポケットの周方向寸法を大きくする必要が
生じる。そのため、保持器の柱部が細くなり、強度面が
問題となる。However, if the offset amount (F) is too large: (I) The track becomes shallow in a high operating angle range, and the allowable load torque is reduced; (II) The diameter of the ball in the cage pocket. Since the amount of directional movement increases, it becomes necessary to increase the wall thickness (radial dimension) of the cage in order to prevent the balls from falling off. Therefore, the track becomes shallow and the allowable load torque is reduced. (III) The amount of movement of the ball in the circumferential direction of the cage in the pocket increases, so that the proper movement of the ball is ensured in the cage. It becomes necessary to increase the circumferential size of the pocket. Therefore, the pillar portion of the cage becomes thin, and the strength is a problem.

【００２１】一方、オフセット量（Ｆ）が小さすぎる
と： （IV）作動角付与時、負荷側のトラック荷重（Ｐ１）、
非負荷側のトラック荷重（Ｐ２：１回転中に、非負荷側
トラックに荷重が働く位相が生じる。）のピーク値が増
大し（Ｐ１、Ｐ２は所定の位相角でピーク値を示
す。）、耐久性低下を招く； （V）最大作動角が減少する。On the other hand, if the offset amount (F) is too small: (IV) When the working angle is applied, the track load (P1) on the load side,
The peak value of the track load on the non-loaded side (P2: The phase in which the load acts on the non-loaded side occurs during one rotation) increases (P1 and P2 show the peak value at a predetermined phase angle), Durability is reduced; (V) Maximum operating angle is reduced.

【００２２】以上より、オフセット量（Ｆ）は、過大・
過小いずれも好ましくなく、上記（I）（II）（III）の
問題と上記（IV）（V）の問題との均衡を図り得る最適
範囲が存在する。ただ、オフセット量（Ｆ）の最適範囲
は継手の大きさによって変わるので、継手の大きさを表
す基本寸法との関係において求める必要がある。比Ｒ１
（＝Ｆ／ＰＣＲ）を用いているのはそのためである。Ｒ
１〉０．１２１であると上記（I）（II）（III）が問題
となり、Ｒ１〈０．０６９であると上記（IV）（V）が
問題となる。許容負荷トルクの確保、保持器強度の確
保、トラック荷重の低減、耐久性の確保、最大作動角の
確保の点から、０．０６９≦Ｒ１≦０．１２１がオフセ
ット量（Ｆ）の最適範囲である。ここで、上記Ｒ１の上
限値（０．１２１）は比較品（６個ボールの固定型等速
自在継手）におけるＲ１の一般的な値（通常、０．１４
である。）よりもかなり小さい。Ｒ１が小さい分、本発
明品は比較品に比べ、許容負荷トルクの向上、保持器強
度の確保に関して、より一層の配慮が払われているとい
うことができる。Ｒ１を上記範囲に設定することができ
たのは、本発明品が８個のボールを備えており、トラッ
ク荷重の点で比較品よりも有利であること（理論解析に
より確認されている。）、温度上昇が比較品に比べて低
減されること（実験により確認されている。図８、図９
参照）による。比較品（６個ボール）において、Ｒ１を
上記範囲に設定すると、トラック荷重が過大となって、
耐久性低下につながると考えられる。From the above, the offset amount (F) is excessive.
Neither is preferable, and there is an optimum range in which the problems (I), (II) and (III) and the problems (IV) and (V) can be balanced. However, since the optimum range of the offset amount (F) varies depending on the size of the joint, it is necessary to find it in relation to the basic dimension representing the size of the joint. Ratio R1
That is why (= F / PCR) is used. R
When 1> 0.121, the above (I) (II) (III) becomes a problem, and when R1 <0.069, the above (IV) (V) becomes a problem. From the viewpoint of ensuring the allowable load torque, securing the cage strength, reducing the truck load, ensuring durability, and ensuring the maximum working angle, 0.069 ≦ R1 ≦ 0.121 is the optimum range of the offset amount (F). is there. Here, the upper limit value (0.121) of R1 is the general value of R1 in a comparative product (fixed type constant velocity universal joint with 6 balls) (usually 0.14).
It is. ) Is much smaller than. Since R1 is smaller, it can be said that the product of the present invention is given more consideration as to the improvement of the allowable load torque and the securing of the cage strength as compared with the comparative product. The reason why R1 could be set in the above range is that the product of the present invention is provided with eight balls, and is advantageous over the comparative product in terms of track load (confirmed by theoretical analysis). , The temperature rise is reduced compared to the comparative product (confirmed by experiments. FIG. 8 and FIG. 9)
See). In the comparative product (6 balls), if R1 is set in the above range, the track load becomes excessive,
It is thought to lead to a decrease in durability.

【００２３】上記構成に加え、さらに、保持器の外径面
の球面中心と内径面の球面中心とを、ボールの中心を含
む継手中心面に対して軸方向に等距離（ｆ）だけ反対側
にオフセットさせ、前記オフセット量（ｆ）と、前記
（ＰＣＲ）との比Ｒ２（＝ｆ／ＰＣＲ）を、０〈Ｒ２≦
０．０５２の範囲内とした構成を採用することもできる
（請求項５）。In addition to the above configuration, the spherical center of the outer diameter surface and the spherical center of the inner diameter surface of the cage are opposite to each other by an equal distance (f) in the axial direction with respect to the central surface of the joint including the center of the ball. And the ratio R2 (= f / PCR) between the offset amount (f) and the (PCR) is 0 <R2 ≦
It is also possible to adopt a configuration in which the range is within 0.052 (Claim 5).

【００２４】０〈Ｒ２≦０．０５２とした理由は次にあ
る。一般に、オフセット量（ｆ）を設けることにより、
保持器の内径面の面積を増大させ、発熱減少により、耐
久性向上を図ることができ、また、内輪を組入れる保持
器の入口部の肉厚を増大させ、強度向上を図ることがで
きるという利点がある。The reason for setting 0 <R2 ≦ 0.052 is as follows. Generally, by providing the offset amount (f),
Advantages of increasing the area of the inner diameter surface of the cage and reducing heat generation to improve durability, and also to increase the wall thickness of the inlet part of the cage that incorporates the inner ring to improve strength There is.

【００２５】しかし、オフセット量（ｆ）が大きすぎる
と： （I）保持器のポケット内におけるボールの周方向移動
量が大きくなるので、ボールの適正な運動を確保するた
め、保持器のポケットの周方向寸法を大きくする必要が
生じる。そのため、保持器の柱部が細くなり、強度面が
問題となる； （II）保持器の入口部と反対側の部分の肉厚が小さくな
り、強度面が問題となる。However, if the offset amount (f) is too large: (I) The amount of movement of the ball in the pocket of the cage in the circumferential direction becomes large, so that in order to ensure proper movement of the ball, It becomes necessary to increase the circumferential dimension. Therefore, the cage column becomes thin and the strength becomes a problem; (II) The thickness of the portion of the cage on the side opposite to the inlet becomes small and the strength becomes a problem.

【００２６】以上より、オフセット量（ｆ）が過大であ
るのは好ましくなく、オフセット量（ｆ）を設ける意義
と上記（I）（II）の問題との均衡を図り得る最適範囲
が存在する。ただ、オフセット量（ｆ）の最適範囲は継
手の大きさによって変わるので、継手の大きさを表す基
本寸法との関係において求める必要がある。比Ｒ２（＝
ｆ／ＰＣＲ）を用いているのはそのためである。Ｒ１〉
０．０５２であると上記（I）（II）が問題となる。保
持器強度の確保、耐久性の確保の点から、０〈Ｒ２≦
０．０５２がオフセット量（ｆ）の最適範囲である。From the above, it is not preferable that the offset amount (f) is excessively large, and there is an optimum range in which the significance of providing the offset amount (f) and the problems (I) and (II) can be balanced. However, since the optimum range of the offset amount (f) changes depending on the size of the joint, it is necessary to find it in relation to the basic dimension representing the size of the joint. Ratio R2 (=
That is why f / PCR) is used. R1>
If it is 0.052, the above (I) and (II) become problems. From the viewpoint of securing cage strength and durability, 0 <R2 ≦
0.052 is the optimum range of the offset amount (f).

【００２７】[0027]

【発明の実施の形態】以下、本発明の実施形態を図面に
従って説明する。Embodiments of the present invention will be described below with reference to the drawings.

【００２８】図１に示すように、この実施形態の固定型
等速自在継手は、内径面１ａに８本の曲線状の案内溝１
ｂを軸方向に形成した外側継手部材としての外輪１と、
外径面２ａに８本の曲線状の案内溝２ｂを軸方向に形成
し、内径面に軸部５を連結するためのセレーション（又
はスプライン）２ｃを形成した内側継手部材としての内
輪２と、外輪１の案内溝１ｂと内輪２の案内溝２ｂとが
協働して形成されるボールトラックに配された８個のボ
ール３と、ボール３を保持する保持器４とで構成され
る。As shown in FIG. 1, the fixed type constant velocity universal joint of this embodiment has eight curved guide grooves 1 on the inner diameter surface 1a.
an outer ring 1 as an outer joint member in which b is formed in the axial direction,
An inner ring 2 as an inner joint member in which eight curved guide grooves 2b are formed in the outer diameter surface 2a in the axial direction and serrations (or splines) 2c for connecting the shaft portion 5 to the inner diameter surface are formed; The guide groove 1b of the outer ring 1 and the guide groove 2b of the inner ring 2 are formed in cooperation with each other, and are composed of eight balls 3 arranged on a ball track and a cage 4 for holding the balls 3.

【００２９】この実施形態において、外輪１の案内溝１
ｂの中心Ｏ１は内径面１ａの球面中心に対して、内輪２
の案内溝２ｂの中心Ｏ２は外径面２ａの球面中心に対し
て、それぞれ、軸方向に等距離（Ｆ）だけ反対側にオフ
セットされている。保持器４の外径面４ａの球面中心、
および、保持器４の外径面４ａの案内面となる外輪１の
内径面１ａの球面中心は、いずれも、ボール３の中心Ｏ
３を含む継手中心面Ｏ内にある。また、保持器４の内径
面４ｂの球面中心、および、保持器４の内径面４ｂの案
内面となる内輪２の外径面２ａの球面中心は、いずれ
も、継手中心面Ｏ内にある。それ故、外輪１の上記オフ
セット量（Ｆ）は、案内溝１ｂの中心Ｏ１と継手中心面
Ｏとの間の軸方向距離、内輪２の上記オフセット量
（Ｆ）は、案内溝２ｂの中心Ｏ２と継手中心面Ｏとの間
の軸方向距離になり、両者は等しい。外輪１の案内溝１
ｂの中心Ｏ１と内輪２の案内溝２ｂの中心Ｏ２とは、継
手中心面Ｏに対して軸方向に等距離（Ｆ）だけ反対側
（案内溝１ｂの中心Ｏ１は継手の開口側、案内溝２ｂの
中心Ｏ２は継手の奥部側）にずれた位置にある。外輪１
の案内溝１ｂの中心Ｏ１とボール３の中心Ｏ３を結ぶ線
分の長さ、内輪２の案内溝２ｂの中心Ｏ２とボール３の
中心Ｏ３を結ぶ線分の長さが、それぞれＰＣＲであり、
両者は等しい。In this embodiment, the guide groove 1 of the outer ring 1
the center O1 of the inner ring 2 with respect to the center of the spherical surface of the inner surface 1a.
The center O2 of the guide groove 2b is offset by an equal distance (F) in the axial direction from the spherical center of the outer diameter surface 2a on the opposite side. The spherical center of the outer diameter surface 4a of the cage 4,
Also, the spherical center of the inner diameter surface 1a of the outer ring 1 which serves as a guide surface for the outer diameter surface 4a of the cage 4 is the center O of the ball 3.
It is in the joint center plane O including 3. Further, the spherical center of the inner diameter surface 4b of the cage 4 and the spherical center of the outer diameter surface 2a of the inner ring 2 that serves as a guide surface for the inner diameter surface 4b of the cage 4 are both within the joint center plane O. Therefore, the offset amount (F) of the outer ring 1 is the axial distance between the center O1 of the guide groove 1b and the joint center plane O, and the offset amount (F) of the inner ring 2 is the center O2 of the guide groove 2b. And the joint center plane O, which are equal. Guide groove 1 of outer ring 1
The center O1 of the guide groove 1b and the center O2 of the guide groove 2b of the inner ring 2 are opposite to each other by an equal distance (F) in the axial direction with respect to the joint center plane O (the center O1 of the guide groove 1b is the opening side of the joint, the guide groove The center O2 of 2b is located at a position shifted toward the inner side of the joint). Outer ring 1
The length of the line segment connecting the center O1 of the guide groove 1b and the center O3 of the ball 3 and the length of the line segment connecting the center O2 of the guide groove 2b of the inner ring 2 and the center O3 of the ball 3 are PCR, respectively.
Both are equal.

【００３０】外輪１と内輪２とが角度θだけ角度変位す
ると、保持器４に案内されたボール３は常にどの作動角
θにおいても、角度θの２等分面（θ／２）内に維持さ
れ、継手の等速性が確保される。When the outer ring 1 and the inner ring 2 are angularly displaced by the angle θ, the ball 3 guided by the cage 4 is always maintained within the bisecting plane (θ / 2) of the angle θ at any operating angle θ. The constant velocity of the joint is secured.

【００３１】この実施形態では、上記構成に加え、継手
の主要寸法を次のような値に設定している。前述したよ
うに、 ボール３のピッチ円径ＰＣＤBALL（ＰＣＤBALL＝２×
ＰＣＲ）と直径ＤBALLとの比ｒ１（＝ＰＣＤBALL／Ｄ
BALL）は、３．３≦ｒ１≦５．０の範囲、好ましくは、
３．５≦ｒ１≦５．０の範囲内の値に設定するのが、外
輪等の強度確保、負荷容量の確保、耐久性の確保の点か
ら好ましいが、この実施形態では、ｒ１＝３．８３に設
定してある。また、 外輪１の外径ＤOUTERと内輪２のセレーション（又は
スプライン）２ｃのピッチ円径ＰＣＤSERRとの比ｒ２
（＝ＤOUTER／ＰＣＤSERR）を２．５≦ｒ２≦３．５、
例えば、２．５≦ｒ２〈３．２の範囲内の値に設定して
ある。尚、上記の構成は単独で採用しても良い。In this embodiment, in addition to the above structure, the main dimensions of the joint are set to the following values. As mentioned above, the pitch circle diameter of the ball 3 PCD BALL (PCD BALL = 2 ×
Ratio of PCR) and diameter D BALL r1 (= PCD BALL / D
BALL ) is in the range 3.3 ≦ r1 ≦ 5.0, preferably
It is preferable to set the value within the range of 3.5 ≦ r1 ≦ 5.0 from the viewpoint of securing the strength of the outer ring and the like, securing the load capacity, and securing the durability. In this embodiment, r1 = 3. It is set to 83. The ratio r2 between the outer diameter D OUTER of the outer ring 1 and the pitch circle diameter PCD SERR of the serration (or spline) 2c of the inner ring 2
(= D OUTER / PCD SERR ) 2.5 ≦ r2 ≦ 3.5,
For example, it is set to a value within the range of 2.5 ≦ r2 <3.2. Note that the above configuration may be employed alone.

【００３２】上記の構成について、同じ呼び形式の
比較品（図１５に示すような６個ボールの固定型等速自
在継手）と比較すると表１のようになる。Table 1 shows a comparison of the above construction with a comparative product of the same nominal type (fixed type constant velocity universal joint with 6 balls as shown in FIG. 15).

【００３３】[0033]

【表１】 [Table 1]

【００３４】この実施形態の固定型等速自在継手は、ボ
ール３の個数が８個であり、比較品（６個ボール）に比
べ、継手の全負荷容量に占めるボール１個当りの負荷割
合が少ないので、同じ呼び形式の比較品（６個ボール）
に対して、ボール３の直径ＤBALLを小さくし、外輪１の
肉厚および内輪２の肉厚を比較品（６個ボール）と同程
度に確保することが可能である。In the fixed type constant velocity universal joint of this embodiment, the number of balls 3 is 8, and the load ratio per ball in the total load capacity of the joint is higher than that of the comparative product (6 balls). Since there are few, comparative products with the same nominal format (6 balls)
On the other hand, it is possible to reduce the diameter D BALL of the ball 3 and secure the wall thickness of the outer ring 1 and the wall thickness of the inner ring 2 to the same extent as the comparative product (6 balls).

【００３５】また、同じ呼び形式の比較品（６個ボー
ル）に対して、比ｒ２（＝ＤOUTER／ＰＣＤSERR）を小
さくし（２．５≦ｒ２〈３．２）、比較品（６個ボー
ル）と同等以上の強度、負荷容量および耐久性を確保し
つつ、より一層のコンパクト化を図ることができる。Further, the ratio r2 (= D OUTER / PCD SERR ) is made smaller (2.5 ≦ r2 <3.2) than the comparative product (6 balls) of the same nominal type, and the comparative product (6 balls). The strength, load capacity and durability equal to or higher than that of a ball) can be secured, and further compactification can be achieved.

【００３６】案内溝１ｂ、２ｂのオフセット量（Ｆ）は
次のような値に設定すると良い。前述したように、 案内溝１ｂ、２ｂのオフセット量（Ｆ）は、比Ｒ１
（＝Ｆ／ＰＣＲ）が、０．０６９≦Ｒ１≦０．１２１の
範囲内になるように設定するのが、許容負荷トルクの確
保、保持器強度の確保、トラック荷重の低減、耐久性の
確保、最大作動角の確保の点から好ましいが、この実施
形態では、Ｒ１＝０．１０４（又は０．１０３８）に設
定してある。比較品（６個ボール）におけるＲ１の一般
的な値は０．１４であり、この実施形態品のＲ１は比較
品よりもかなり小さい。The offset amount (F) of the guide grooves 1b, 2b may be set to the following value. As described above, the offset amount (F) between the guide grooves 1b and 2b is the ratio R1.
It is necessary to set (= F / PCR) within the range of 0.069 ≦ R1 ≦ 0.121 to ensure the allowable load torque, the cage strength, the track load, and the durability. , Is preferable from the viewpoint of ensuring the maximum operating angle, but in this embodiment, R1 = 0.104 (or 0.1038) is set. A typical value of R1 in the comparative product (6 balls) is 0.14, and R1 of this embodiment product is considerably smaller than that of the comparative product.

【００３７】図２は、外輪１を示している。外輪１の内
径面１ａの開口側領域には、保持器４を内径面１ａに組
込むための円筒状カット部１ａ１が設けられている。保
持器４の組込みに際しては、図２（ａ）に示すように、
軸線を互いに直交させた状態で、保持器４のポケット４
ｃを円筒状カット部１ａ１に入れる。この態様で、保持
器４を、その外径面４ａの球面中心が外輪１の内径面１
ａの球面中心に一致するまで挿入する。この状態から、
保持器４を９０度回転させ、保持器４の軸線と外輪１の
軸線とを一致させる。これにより、保持器４が外輪１の
内径面１ａに完全に組込まれる。FIG. 2 shows the outer ring 1. A cylindrical cut portion 1a1 for incorporating the retainer 4 into the inner diameter surface 1a is provided in the opening side region of the inner diameter surface 1a of the outer ring 1. When assembling the retainer 4, as shown in FIG.
With the axes perpendicular to each other, the pocket 4
c is put into the cylindrical cut portion 1a1. In this manner, the retainer 4 is arranged such that the center of the spherical surface of the outer diameter surface 4 a is the inner diameter surface 1 of the outer ring 1.
Insert until it coincides with the spherical center of a. From this state,
The retainer 4 is rotated by 90 degrees so that the axis of the retainer 4 and the axis of the outer ring 1 match. Thereby, the retainer 4 is completely assembled on the inner diameter surface 1a of the outer race 1.

【００３８】また、図２（ｃ）（ｄ）に拡大して示すよ
うに、外輪１の案内溝１ｂの開口側領域には、チャンフ
ァ１ｂ１が設けられている。チャンファ１ｂ１は、案内
溝１ｂを熱処理する際｛図２（ｄ）における領域Ｗに熱
処理を施す。｝の焼抜けを防止する役割をもつ（外輪１
の開口端面に焼きが入らないようにする）と同時に、ボ
ール３を保持器４のポケット４ｃに組込む際の案内部と
して利用することができる。As enlargedly shown in FIGS. 2 (c) and 2 (d), a chamfer 1b1 is provided in the opening side region of the guide groove 1b of the outer ring 1. When heat-treating the guide groove 1b, the chamfer 1b1 heat-treats the region W in FIG. 2D.役 割 has the role of preventing burn-through (outer ring 1
At the same time, it is possible to use the ball 3 as a guide portion when the ball 3 is incorporated into the pocket 4c of the retainer 4.

【００３９】図３は、内輪２を示している。内輪２の外
径面２ａの直径はＡ、１８０度対向した２つの案内溝１
ｂの溝底を含む平面Ｓと平行な縦断面における、外径面
２ａ間の最大間隔はＣである。FIG. 3 shows the inner ring 2. The diameter of the outer diameter surface 2a of the inner ring 2 is A, and the two guide grooves 1 facing each other by 180 degrees.
The maximum distance between the outer diameter surfaces 2a in a vertical section parallel to the plane S including the groove bottom b is C.

【００４０】図４は、保持器４を示している。保持器４
には、ボール３を収容保持する８つの窓状のポケット４
ｃが円周等間隔に設けられている。８つのポケット４ｃ
のうち４つは円周方向寸法の大きな長ポケット４ｃ１、
残りの４つは円周方向の小さな短ポケット４ｃ２で、長
ポケット４ｃ１と短ポケット４ｃ２とは交互に配列され
ている。また、内輪２を組入れる保持器４の入口部４ｄ
の径（Ｂ）は、図３に示す内輪２の外径（Ａ）と、最大
間隔（Ｃ）に対して、Ｃ≦Ｂ〈Ａの関係になるように設
定されている。入口部４ｄの奥側（内径面４ｂと入口部
４ｄとの境界部分）は段差４ｅになっている。FIG. 4 shows the cage 4. Cage 4
Eight window-shaped pockets 4 for accommodating and holding balls 3
c are provided at equal intervals on the circumference. 8 pockets 4c
Four of them are long pockets 4c1 with a large circumferential dimension,
The remaining four are small circumferential short pockets 4c2, and long pockets 4c1 and short pockets 4c2 are arranged alternately. Further, the inlet portion 4d of the cage 4 incorporating the inner ring 2
The diameter (B) of the inner ring 2 is set to have a relationship of C ≦ B <A with respect to the outer diameter (A) of the inner ring 2 shown in FIG. 3 and the maximum distance (C). A step 4e is formed on the inner side of the entrance 4d (the boundary between the inner diameter surface 4b and the entrance 4d).

【００４１】入口部４ｄの径（Ｂ）をＣ≦Ｂ〈Ａの関係
になるように設定したのは、保持器４の内径面４ｂに内
輪２を組込む際の組込み性に配慮したためである。内輪
２の組込みに際しては、互いの軸線を直交させた状態
で、内輪２の１つの案内溝２ｂを保持器４の入口部４ｄ
にあてがいながら、内輪２を保持器４の内径面４ｂに挿
入する。この態様で、内輪２をある程度挿入すると、内
輪２の外径面２ａの最大間隔（Ｃ）が段差４ｅに引っ掛
かり、その以上内輪２を挿入することができなくなる
（図５に示す状態）。この状態から、内輪２を９０度回
転させ、内輪２の軸線と保持器４の軸線とを一致させ
る。これにより、内輪２が保持器４の内径面４ｂに完全
に組込まれる。The reason that the diameter (B) of the inlet portion 4d is set to satisfy the relationship of C≤B <A is to consider the assembling property when the inner ring 2 is mounted on the inner diameter surface 4b of the cage 4. When assembling the inner ring 2, one guide groove 2 b of the inner ring 2 is inserted into the entrance 4 d of the retainer 4 in a state where the axes are orthogonal to each other.
, The inner ring 2 is inserted into the inner surface 4 b of the retainer 4. When the inner race 2 is inserted to some extent in this manner, the maximum interval (C) between the outer diameter surfaces 2a of the inner race 2 is caught by the step 4e, and the inner race 2 cannot be inserted any more (the state shown in FIG. 5). From this state, the inner ring 2 is rotated by 90 degrees, and the axis of the inner ring 2 and the axis of the retainer 4 are aligned. Thereby, the inner race 2 is completely assembled on the inner diameter surface 4b of the retainer 4.

【００４２】４つの長ポケット４ｃ１と４つの短ポケッ
ト４ｃ２とを交互に配列したのは、ボール３を保持器４
のポケット４ｃに組込む際の組込み性に配慮したためで
ある。図６（ａ）に示すように、ボール３の組込みは、
内輪２および保持器４のアッセンブリを外輪１の内径面
１ａに組込んだ後、内輪２および保持器４を外輪１に対
して角度変位（ボール組込み角α）させた状態で行な
う。図６（ｂ）の各位相におけるボール３を、３１、３
２、・・・、３８で示す。ボール３１、３３、３５、３
７は保持器４の短ポケット４ｃ２に収容され、ボール３
２、３４、３６、３８は長ポケット４ｃ１に収容されて
いる。継手が作動角αをとった時の、ポケット４ｃ内に
おけるボール３の移動位置は図７に示すようになる。
尚、図７（ａ）は保持器オフセット（ｆ）を設けていな
い図１の構成、図７（ｂ）は保持器オフセット（ｆ）を
設けた図１１および図１２の構成にそれぞれ対応してい
る。ボール３は、まず４つの長ポケット４ｃ１にそれぞ
れ組込み、その後、４つの短ポケット４ｃ２にそれぞれ
組込む。例えばボール３１を組込む際、３３、３５、３
７の位相では、ボール３の周方向の動き量は少ない。そ
のため、ボール３１を短ポケット４ｃ２に組込むことが
できる。同様に、例えばボール３３を組込む際、３１、
３５、３７の位相では、ボール３の周方向の動き量は少
ない。そのため、ボール３３を短ポケット４ｃ２に組込
むことができる。このようにして、全ての短ポケット４
ａ２にボール３を組込むことができる。尚、ボール３を
ポケット４ｃに組込む際、外輪１のチャンファ１ｂ１が
ボール３を案内する役割をなす｛図６（ａ）参照｝。The four long pockets 4c1 and the four short pockets 4c2 are arranged alternately so that the ball 3 is retained in the cage 4.
This is because consideration was given to the assemblability when it is installed in the pocket 4c. As shown in FIG. 6A, the ball 3 is assembled in
After the assembly of the inner ring 2 and the cage 4 is assembled on the inner diameter surface 1a of the outer ring 1, the inner ring 2 and the cage 4 are angularly displaced with respect to the outer ring 1 (ball mounting angle α). The ball 3 in each phase of FIG.
2, ..., 38. Balls 31, 33, 35, 3
7 is accommodated in the short pocket 4c2 of the cage 4, and the ball 3
2, 34, 36 and 38 are accommodated in the long pocket 4c1. The movement position of the ball 3 in the pocket 4c when the joint has the operating angle α is as shown in FIG.
7A corresponds to the configuration of FIG. 1 without the cage offset (f), and FIG. 7B corresponds to the configurations of FIGS. 11 and 12 with the cage offset (f). I have. The balls 3 are first assembled in the four long pockets 4c1 and then in the four short pockets 4c2, respectively. For example, when incorporating the ball 31, 33, 35, 3
In the phase of 7, the amount of movement of the ball 3 in the circumferential direction is small. Therefore, the ball 31 can be incorporated in the short pocket 4c2. Similarly, for example, when incorporating the ball 33, 31,
In the phases of 35 and 37, the amount of movement of the ball 3 in the circumferential direction is small. Therefore, the ball 33 can be incorporated in the short pocket 4c2. In this way, all short pockets 4
The ball 3 can be incorporated in a2. When the ball 3 is assembled in the pocket 4c, the chamfer 1b1 of the outer ring 1 plays a role of guiding the ball 3 (see FIG. 6 (a)).

【００４３】上述した態様で、外輪１、内輪２、保持器
４、ボール３を組付けると、図１に示す本実施形態の固
定型等速自在継手が完成する。内輪２のセレーション
（スプラインでも良い。）２ｃには、軸部５が連結され
る。尚、この実施形態では、軸部５をボロン鋼で形成
し、軸部５の小径化を図っている（最大作動角付与時、
外輪１の開口端と干渉する部分の径を小さくしてある。
セレーションの径は比較品と同じにしてある。）。軸部
５の小径化を図ったのは、作動角増大に配慮したためで
ある。試作品では、例えば自動車のドライブシャフト用
継手として要求される最大作動角４５°以上を充分達成
できた。When the outer ring 1, the inner ring 2, the cage 4 and the balls 3 are assembled in the above-described manner, the fixed type constant velocity universal joint of this embodiment shown in FIG. 1 is completed. The shaft portion 5 is connected to the serration (or spline) 2c of the inner race 2. In this embodiment, the shaft portion 5 is formed of boron steel to reduce the diameter of the shaft portion 5 (when the maximum operating angle is given,
The diameter of the portion that interferes with the open end of the outer ring 1 is reduced.
The diameter of the serration is the same as the comparative product. ). The reason why the diameter of the shaft portion 5 is reduced is that consideration is given to an increase in the operating angle. In the prototype, for example, a maximum operating angle of 45 ° or more required for a joint for a drive shaft of an automobile could be sufficiently achieved.

【００４４】図８は、実施形態品と比較品（６個ボール
の固定型逃走自在継手）（いずれも同じ呼び形式）につ
いて、回転数（ｒｐｍ）と温度上昇量（°Ｃ）との関係
を比較試験した結果を示している。同図でＸ（点線白
○）は実施形態品、Ｙ（実線黒○）は比較品であり、温
度上昇量（°Ｃ）は、運転開始から３０分経過後に測定
したデータである。また、θは継手作動角、Ｔは入力回
転トルクである。FIG. 8 shows the relationship between the number of revolutions (rpm) and the amount of temperature rise (° C) for the embodiment product and the comparative product (fixed type escape universal joint of 6 balls) (all have the same nominal type). The result of the comparative test is shown. In this figure, X (dotted white circle) is the product of the embodiment, Y (solid black circle) is the comparative product, and the temperature rise (° C) is data measured 30 minutes after the start of operation. Θ is the joint operating angle, and T is the input rotational torque.

【００４５】同図に示す試験結果から明らかなように、
実施形態品（Ｘ）の温度上昇量は比較品（Ｙ）よりも小
さく、回転数が高くなるに従ってその差が大きくなって
いる。温度上昇の低減は、耐久性の向上につながる。ま
た、そのような温度上昇の低減は、作動角（θ）および
入力回転トルク（Ｔ）の如何を問わず得られるものと考
えられる。As is clear from the test results shown in FIG.
The temperature rise of the embodiment product (X) is smaller than that of the comparative product (Y), and the difference increases as the rotation speed increases. Reducing the temperature rise leads to improved durability. Further, it is considered that such a reduction in temperature rise can be obtained regardless of the operating angle (θ) and the input rotation torque (T).

【００４６】図９は、実施形態品と比較品（６個ボー
ル）（いずれも同じ呼び形式）について、温度上昇量
（°Ｃ）の経時変化を比較試験した結果を示している。
同図でＸ（点線白○）は実施形態品、Ｙ（実線黒○）は
比較品であり、θは継手作動角、Ｔは入力回転トルクで
ある。FIG. 9 shows the results of a comparative test of changes over time in the amount of temperature rise (° C) for the embodiment product and the comparative product (6 balls) (both have the same nominal type).
In the figure, X (dotted white circle) is the embodiment product, Y (solid line black circle) is the comparative product, θ is the joint operating angle, and T is the input rotation torque.

【００４７】同図に示す試験結果から明らかなように、
実施形態品（Ｘ）の温度上昇量は比較品（Ｙ）よりも小
さく、その差は運転時間が長くなってもあまり変化して
いない。As is clear from the test results shown in FIG.
The temperature rise amount of the embodiment product (X) is smaller than that of the comparative product (Y), and the difference does not change much even when the operation time becomes longer.

【００４８】図１０は、実施形態品と比較品（６個ボー
ル）（いずれも同じ呼び形式）について、作動角θ（ｄ
ｅｇ）とトルク損失率（％）との関係を比較試験した結
果を示している。同図でＸ（点線白○）は実施形態品、
Ｙ（実線黒○）は比較品であり、θ＝１０ｄｅｇでは入
力回転トルクＴ＝１９６Ｎ・ｍ、θ＝３０ｄｅｇではＴ
＝９８Ｎ・ｍとして、トルク損失率を測定している。FIG. 10 shows the operating angle θ (d) for the embodiment product and the comparison product (6 balls) (all have the same nominal form).
3 shows the results of a comparative test of the relationship between the torque loss rate (eg) and the torque loss rate (%). In the figure, X (dotted white circle) indicates the product of the embodiment
Y (solid black circle) is a comparative product, and the input rotation torque T = 196 N · m at θ = 10 deg and T at θ = 30 deg.
= 98 N · m, and the torque loss rate is measured.

【００４９】同図から明らかなように、実施形態品
（Ｘ）のトルク損失率は比較品（Ｙ）よりも小さく、作
動角θが大きくなるに従ってその差が大きくなってい
る。トルク損失の低減は、省燃費、省エネルギーに寄与
する他、温度上昇の低減ひいては耐久性の向上にもつな
がる。As is clear from the figure, the torque loss rate of the embodiment product (X) is smaller than that of the comparison product (Y), and the difference increases as the operating angle θ increases. Reduction of torque loss contributes to fuel saving and energy saving, and also leads to reduction of temperature rise and improvement of durability.

【００５０】以上のように、この実施形態の固定型等速
自在継手によれば、形状がコンパクトでありながら、比
較品（６個ボール）と同等またはそれ以上の負荷容量お
よび耐久性をもたせることができる。As described above, according to the fixed type constant velocity universal joint of this embodiment, it is possible to provide a load capacity and durability equal to or higher than that of the comparative product (6 balls) while having a compact shape. You can

【００５１】図１１は、本発明の他の実施形態に係わる
固定型等速自在継手を示している。外輪１の案内溝１ｂ
の中心Ｏ１は内径面１ａの球面中心Ｏ４に対して、内輪
２の案内溝２ｂの中心Ｏ２は外径面２ａの球面中心Ｏ５
に対して、それぞれ、軸方向に等距離（Ｆ）だけ反対側
にオフセットされている。さらに、この実施形態では、
保持器４の外径面４ａの球面中心（外輪１の内径面１ａ
の球面中心Ｏ４と同じ）と、保持器４の内径面４ｂの球
面中心（内輪２の外径面２ａの球面中心Ｏ５と同じ）と
を、継手中心面Ｏに対して軸方向に等距離（ｆ）だけ反
対側にオフセットさせている。外輪１の上記オフセット
量（Ｆ）は、案内溝１ｂの中心Ｏ１と内径面１ａの球面
中心Ｏ４との間の軸方向距離、内輪２の上記オフセット
量（Ｆ）は、案内溝２ｂの中心Ｏ２と外径面２ａの球面
中心Ｏ５との間の軸方向距離になり、両者は等しい。外
輪１の案内溝１ｂの中心Ｏ１と内輪２の案内溝２ｂの中
心Ｏ２とは、継手中心面Ｏに対して軸方向に等距離だけ
反対側（案内溝１ｂの中心Ｏ１は継手の開口側、案内溝
２ｂの中心Ｏ２は継手の奥部側）にずれた位置にある。
外輪１の案内溝１ｂの中心Ｏ１とボール３の中心Ｏ３を
結ぶ線分の長さ、内輪２の案内溝２ｂの中心Ｏ２とボー
ル３の中心Ｏ３を結ぶ線分の長さが、それぞれＰＣＲで
あり、両者は等しい。FIG. 11 shows a fixed type constant velocity universal joint according to another embodiment of the present invention. Guide groove 1b of outer ring 1
The center O1 of the inner diameter surface 1a is the center O4 of the spherical surface, and the center O2 of the guide groove 2b of the inner ring 2 is the center O5 of the outer surface 2a.
On the other hand, each is offset to the opposite side by an equal distance (F) in the axial direction. Further, in this embodiment,
The spherical center of the outer diameter surface 4a of the cage 4 (the inner diameter surface 1a of the outer ring 1
And the spherical center of the inner diameter surface 4b of the cage 4 (same as the spherical center O5 of the outer diameter surface 2a of the inner ring 2) are equidistant from the joint center surface O in the axial direction ( Only f) is offset to the opposite side. The offset amount (F) of the outer ring 1 is the axial distance between the center O1 of the guide groove 1b and the spherical center O4 of the inner diameter surface 1a, and the offset amount (F) of the inner ring 2 is the center O2 of the guide groove 2b. Is equal to the axial distance between the spherical center O5 of the outer diameter surface 2a and both are equal. The center O1 of the guide groove 1b of the outer ring 1 and the center O2 of the guide groove 2b of the inner ring 2 are on the opposite side by an equal distance in the axial direction with respect to the joint center plane O (the center O1 of the guide groove 1b is the opening side of the joint, The center O2 of the guide groove 2b is located at a position shifted toward the inner side of the joint).
The length of the line segment connecting the center O1 of the guide groove 1b of the outer ring 1 and the center O3 of the ball 3 and the length of the line segment connecting the center O2 of the guide groove 2b of the inner ring 2 and the center O3 of the ball 3 are respectively PCR. Yes, both are equal.

【００５２】保持器４の外径面４ａ、内径面４ｂのオフ
セット量（ｆ）は、次のような値に設定すると良い。前
述したように、 外径面４ａ、内径面４ｂのオフセット量（ｆ）は比Ｒ
２（＝ｆ／ＰＣＲ）が、０〈Ｒ２≦０．０５２の範囲内
になるように設定するのが、保持器強度の確保、耐久性
の確保の点から好ましいが、この実施形態では、Ｒ２＝
０．０３５に設定してある。上記実施形態における
の構成については同様であるので（但し、の構成に
関しては、Ｒ１＝０．１００３に設定している。）、説
明を省略する。尚、保持器４のオフセット（ｆ）の向き
は逆でも良い。すなわち、図１１における点Ｏ４を内径
面４ｂの球面中心、点Ｏ５を外径面４ａの球面中心とし
ても良い。The offset amount (f) of the outer diameter surface 4a and the inner diameter surface 4b of the cage 4 may be set to the following values. As described above, the offset amount (f) of the outer diameter surface 4a and the inner diameter surface 4b is the ratio R
It is preferable to set 2 (= f / PCR) within the range of 0 <R2 ≦ 0.052 from the viewpoint of securing the cage strength and durability, but in this embodiment, R2 =
It is set to 0.035. The configuration of the above embodiment is the same (however, the configuration of is set to R1 = 0.1003), and therefore the description thereof is omitted. The direction of the offset (f) of the cage 4 may be reversed. That is, the point O4 in FIG. 11 may be the spherical center of the inner diameter surface 4b, and the point O5 may be the spherical center of the outer diameter surface 4a.

【００５３】図１２に示す実施形態は、外輪１の案内溝
１ｂの所定領域Ｕ１、内輪２の案内溝２ｂの所定領域Ｕ
２をそれぞれストレート状にしたものである。案内溝１
ｂのＵ１以外の領域は点Ｏ１を中心とする曲線状、案内
溝２ｂのＵ２以外の領域は点Ｏ２を中心とする曲線状で
ある。その他の構成は、図１１に示す実施形態と同様で
あるので、説明を省略する。In the embodiment shown in FIG. 12, the predetermined area U1 of the guide groove 1b of the outer ring 1 and the predetermined area U of the guide groove 2b of the inner ring 2 are used.
2 is a straight shape. Guide groove 1
The area b other than U1 has a curved shape centered on the point O1, and the area other than U2 of the guide groove 2b has a curved shape centered on the point O2. The other configurations are similar to those of the embodiment shown in FIG. 11, and thus the description thereof will be omitted.

【００５４】尚、この種の固定型等速自在継手におい
て、外輪案内溝の中心、内輪案内溝の中心、外輪内径面
の球面中心、内輪外径面の球面中心の位置関係には、図
１３示すような８つのバリエーション｛図１３（ａ）〜
図１３（ｈ）｝があるが、本発明はそのいずれの構成に
も適用することができる。ちなみに、図１の構成は図１
３（ｂ）、図１１および図１２の構成は図１３（ａ）に
それぞれ対応している。In this type of fixed type constant velocity universal joint, the positional relationship among the center of the outer ring guide groove, the center of the inner ring guide groove, the spherical center of the outer ring inner diameter surface, and the spherical center of the inner ring outer diameter surface is shown in FIG. Eight variations as shown {Fig. 13 (a)-
13 (h)}, the present invention can be applied to any of the configurations. By the way, the configuration of FIG.
The configurations of FIG. 3B, FIG. 11 and FIG. 12 correspond to FIG. 13A, respectively.

【００５５】また、以上説明した実施形態における構成
は、（）、（＋）、（）、（）、
（＋）、（＋）、（＋＋）、（＋＋
）、（＋）、（＋＋）、（＋＋＋
）のように、単独で又は組み合わせて用いることがで
きる。これらの中で、（）（請求項２）、（＋）
（請求項３）、（）（請求項４）、（＋）（請求
項５）、（＋）（請求項６）、（＋＋）（請
求項６）、（＋＋）（請求項７）、（＋＋
＋）（請求項７）の構成が好ましい。Further, the configurations in the above-described embodiments are (), (+), (), (),
(+), (+), (++), (++
), (+), (++), (++++
), Alone or in combination. Among these, () (claim 2), (+)
(Claim 3), () (Claim 4), (+) (Claim 5), (+) (Claim 6), (++) (Claim 6), (++) (Claim 7), (++
+) (Claim 7) is preferable.

【００５６】この実施形態の固定型等速自在継手は、自
動車、各種産業機械等における動力伝達要素として広く
用いることができるが、特に、自動車のドライブシャフ
ト用として好適である。The fixed type constant velocity universal joint of this embodiment can be widely used as a power transmission element in automobiles, various industrial machines, etc., but is particularly suitable for drive shafts of automobiles.

【００５７】[0057]

【発明の効果】以上説明したように、本発明によれば、
固定型等速自在継手における、より一層のコンパクト化
を図ることができると同時に、比較品（６個ボール）と
同等以上の強度、負荷容量、耐久性、作動角を確保する
ことができる。As described above, according to the present invention,
The fixed type constant velocity universal joint can be made more compact, and at the same time, the strength, load capacity, durability, and working angle equivalent to or higher than those of the comparative product (6 balls) can be secured.

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

【図１】本発明の実施形態を示す縦断面図（図ａ：図ｂ
におけるａ−ａ断面）、横断面図（図ｂ：図ａにおける
ｂ−ｂ断面）である。FIG. 1 is a longitudinal sectional view showing an embodiment of the present invention (FIG. A: FIG. B)
2 is a sectional view taken along a line a-a in FIG. 2, and a cross-sectional view is shown in FIG.

【図２】外輪の正面図（図ａ）、縦部分断面図（図
ｂ）、図ａにおける案内溝部分の拡大正面図（図ｃ）、
図ｂにおける端部の拡大縦断面図（図ｄ）である。FIG. 2 is a front view of the outer race (FIG. A), a vertical sectional view (FIG. B), an enlarged front view of a guide groove portion in FIG.
It is an expanded longitudinal cross-sectional view (FIG. D) of the end part in FIG. B.

【図３】内輪の正面図（図ａ）、縦断面図（図ｂ）であ
る。FIG. 3 is a front view (FIG. A) and a longitudinal sectional view (FIG. B) of the inner race.

【図４】保持器の横断面図（図ａ）、縦断面図（図ｂ）
である。FIG. 4 is a cross-sectional view (FIG. A) and a vertical cross-sectional view (FIG. B) of the cage.
It is.

【図５】内輪を保持器に組込む際の一態様を示す正面図
である。FIG. 5 is a front view showing an embodiment when the inner ring is assembled into the retainer.

【図６】ボールを組込む際の態様を示す縦断面図（図
ａ）、横断面図（図ｂ）である。FIG. 6 is a vertical sectional view (FIG. A) and a lateral sectional view (FIG. B) showing a mode in which a ball is assembled.

【図７】作動角αの時の、ポケット内におけるボールの
移動位置を示す図である。図（ａ）は保持器オフセット
を設けていない構成、図（ｂ）は保持器オフセットを設
けた構成にそれぞれ対応している。FIG. 7 is a diagram showing a moving position of a ball in a pocket at an operating angle α. FIG. 7A corresponds to the configuration without the cage offset, and FIG. 8B corresponds to the configuration with the cage offset.

【図８】回転数と温度上昇量との関係を示す図である
（図ａ、図ｂ、図ｃ）。FIG. 8 is a diagram showing the relationship between the number of rotations and the amount of temperature rise (FIGS. A, b, and c).

【図９】温度上昇量の経時変化を示す図である。FIG. 9 is a diagram showing a change over time in the amount of temperature rise.

【図１０】作動角とトルク損失率との関係を示す図であ
る。FIG. 10 is a diagram showing a relationship between an operating angle and a torque loss rate.

【図１１】本発明の他の実施形態を示す縦断面図（図
ａ：図ｂにおけるａ−ａ断面）、横断面図（図ｂ：図ａ
におけるｂ−ｂ断面）である。FIG. 11 is a longitudinal sectional view (FIG. A: aa cross section in FIG. B) and a transverse sectional view (FIG. B: FIG. A) showing another embodiment of the present invention.
Bb section).

【図１２】本発明の他の実施形態を示す縦断面図（図
ａ：図ｂにおけるａ−ａ断面）、横断面図（図ｂ：図ａ
におけるｂ−ｂ断面）である。FIG. 12 is a longitudinal sectional view (FIG. A: a-a section in FIG. B) and a transverse sectional view (FIG. B: FIG. A) showing another embodiment of the present invention.
Bb section).

【図１３】固定型等速自在継手における、外輪案内溝の
中心、内輪案内溝の中心、外輪内径面（保持器外径面）
の中心、内輪外径面（保持器内径面）の中心の位置関係
のバリエーションを示す図である。[Fig. 13] Center of outer ring guide groove, center of inner ring guide groove, outer ring inner diameter surface (cage outer diameter surface) in a fixed type constant velocity universal joint.
It is a figure which shows the variation of the positional relationship of the center of an inner ring, and the center of an inner ring outer diameter surface (cage inner diameter surface).

【図１４】自動車の動力伝達装置の一例（ドライブシャ
フト）を示す図である。FIG. 14 is a diagram showing an example (drive shaft) of a power transmission device of an automobile.

【図１５】比較品（６個ボールの固定型等速自在継手）
を示す横断面図（図ａ）、縦断面図（図ｂ：図ａにおけ
るｂ−ｂ断面図）である。FIG. 15 Comparative product (fixed type constant velocity universal joint with 6 balls)
3 is a horizontal cross-sectional view (FIG. A) and a vertical cross-sectional view (FIG. B: bb cross-sectional view in FIG. A).

【符号の説明】[Explanation of symbols]

１ 外輪 １ａ 内径面 １ｂ 案内溝 ２ 内輪 ２ａ 外径面 ２ｂ 案内溝 ３ ボール ４ 保持器 Ｏ１ 外輪の案内溝の中心 Ｏ２ 内輪の案内溝の中心 Ｏ３ ボールの中心 Ｏ４ 保持器の外径面の球面中心 Ｏ５ 保持器の内径面の球面中心 1 outer ring 1a inner diameter surface 1b guide groove 2 inner ring 2a outer diameter surface 2b guide groove 3 ball 4 cage O1 center of guide groove of outer ring O2 center of guide groove of inner ring O3 center of ball O4 center of spherical surface of outer diameter of cage O5 Cage center of inner diameter of cage

Claims (7)

【特許請求の範囲】[Claims] 【請求項１】 内径面に８本の曲線状の案内溝を形成し
た外側継手部材と、外径面に８本の曲線状の案内溝を形
成し、内径面に軸部を連結するための歯型を形成した内
側継手部材と、外側継手部材の案内溝と内側継手部材の
案内溝とが協働して形成されるボールトラックに配され
た８個のボールと、ボールを保持する保持器とを備え、
自動車の動力伝達装置に用いられる自動車用固定型等速
自在継手。1. An outer joint member having eight curved guide grooves formed on an inner diameter surface and eight curved guide grooves formed on an outer diameter surface for connecting a shaft portion to the inner diameter surface. Eight balls arranged on a ball track formed by cooperation of the inner joint member having a tooth profile, the guide groove of the outer joint member and the guide groove of the inner joint member, and a retainer for holding the ball. With and
Fixed type constant velocity universal joint for automobiles used for power transmission of automobiles. 【請求項２】 ボールのピッチ円径（ＰＣＤBALL）とボ
ールの直径（ＤBALL）との比ｒ１（＝ＰＣＤBALL／Ｄ
BALL）が、３．３≦ｒ１≦５．０の範囲内であることを
特徴とする請求項１記載の自動車用固定型等速自在継
手。2. A ratio r1 (= PCD BALL / D) of the pitch circle diameter of the ball (PCD BALL ) and the diameter of the ball (D BALL ).
BALL ) is within a range of 3.3 ≦ r1 ≦ 5.0. The fixed type constant velocity universal joint for an automobile according to claim 1, wherein 【請求項３】 ボールのピッチ円径（ＰＣＤBALL）とボ
ールの直径（ＤBALL）との比ｒ１（＝ＰＣＤBALL／Ｄ
BALL）が、３．３≦ｒ１≦５．０の範囲内であり、か
つ、外側継手部材の外径（ＤOUTER）と内側継手部材の
歯型のピッチ円径（ＰＣＤSERR）との比ｒ２（＝Ｄ
OUTER／ＰＣＤSERR）が、２．５≦ｒ２≦３．５の範囲
内であることを特徴とする請求項１記載の自動車用固定
型等速自在継手。3. The ratio r1 (= PCD BALL / D) of the pitch circle diameter (PCD BALL ) of the ball and the diameter (D BALL ) of the ball.
BALL ) is within the range of 3.3 ≦ r1 ≦ 5.0, and the ratio r2 of the outer diameter (D OUTER ) of the outer joint member and the tooth die pitch circle diameter (PCD SERR ) of the inner joint member. (= D
OUTER / PCD SERR ) is within a range of 2.5≤r2≤3.5, wherein the fixed type constant velocity universal joint for an automobile according to claim 1. 【請求項４】 内径面に８本の曲線状の案内溝を形成し
た外側継手部材と、外径面に８本の曲線状の案内溝を形
成し、内径面に軸部を連結するための歯型を形成した内
側継手部材と、外側継手部材の案内溝と内側継手部材の
案内溝とが協働して形成されるボールトラックに配され
た８個のボールと、ボールを保持する保持器とを備え、
自動車の動力伝達装置に用いられる固定型等速自在継手
であって、 外側継手部材の案内溝の中心が内径面の球面中心に対し
て、内側継手部材の案内溝の中心が外径面の球面中心に
対して、それぞれ、軸方向に等距離（Ｆ）だけ反対側に
オフセットされ、 前記オフセット量（Ｆ）と、外側継手部材の案内溝の中
心又は内側継手部材の案内溝の中心とボールの中心とを
結ぶ線分の長さ（ＰＣＲ）との比Ｒ１（＝Ｆ／ＰＣＲ）
が、０．０６９≦Ｒ１≦０．１２１の範囲内であること
を特徴とする自動車用固定型等速自在継手。4. An outer joint member having eight curved guide grooves formed on the inner diameter surface and eight curved guide grooves formed on the outer diameter surface for connecting the shaft portion to the inner diameter surface. Eight balls arranged on a ball track formed by cooperation of the inner joint member having a tooth profile, the guide groove of the outer joint member and the guide groove of the inner joint member, and a retainer for holding the ball. With and
A fixed type constant velocity universal joint used in a power transmission device of an automobile, in which the center of the guide groove of the outer joint member is the spherical center of the inner diameter surface and the center of the guide groove of the inner joint member is the outer spherical surface. They are offset from each other by an equal distance (F) in the axial direction to the opposite side, and the offset amount (F) and the center of the guide groove of the outer joint member or the center of the guide groove of the inner joint member and the ball Ratio R1 (= F / PCR) with the length of the line segment connecting the center (PCR)
Is within a range of 0.069 ≦ R1 ≦ 0.121. A fixed type constant velocity universal joint for an automobile, characterized in that 【請求項５】 内径面に８本の曲線状の案内溝を形成し
た外側継手部材と、外径面に８本の曲線状の案内溝を形
成し、内径面に軸部を連結するための歯型を形成した内
側継手部材と、外側継手部材の案内溝と内側継手部材の
案内溝とが協働して形成されるボールトラックに配され
た８個のボールと、ボールを保持する保持器とを備え、
自動車の動力伝達装置に用いられる固定型等速自在継手
であって、 外側継手部材の案内溝の中心が内径面の球面中心に対し
て、内側継手部材の案内溝の中心が外径面の球面中心に
対して、それぞれ、軸方向に等距離（Ｆ）だけ反対側に
オフセットされ、かつ、保持器の外径面の球面中心と内
径面の球面中心とが、ボールの中心を含む継手中心面に
対して軸方向に等距離（ｆ）だけ反対側にオフセットさ
れ、 前記オフセット量（Ｆ）と、外側継手部材の案内溝の中
心又は内側継手部材の案内溝の中心とボールの中心とを
結ぶ線分の長さ（ＰＣＲ）との比Ｒ１（＝Ｆ／ＰＣＲ）
が、０．０６９≦Ｒ１≦０．１２１の範囲内であり、か
つ、前記オフセット量（ｆ）と、前記（ＰＣＲ）との比
Ｒ２（＝ｆ／ＰＣＲ）が、０〈Ｒ２≦０．０５２の範囲
内であることを特徴とする自動車用固定型等速自在継
手。5. An outer joint member having eight curved guide grooves formed on the inner diameter surface and eight curved guide grooves formed on the outer diameter surface for connecting the shaft portion to the inner diameter surface. Eight balls arranged on a ball track formed by cooperation of the inner joint member having a tooth profile, the guide groove of the outer joint member and the guide groove of the inner joint member, and a retainer for holding the ball. With and
A fixed type constant velocity universal joint used in a power transmission device of an automobile, in which the center of the guide groove of the outer joint member is the spherical center of the inner diameter surface and the center of the guide groove of the inner joint member is the outer spherical surface. A joint center plane that is offset to the opposite side by an equal distance (F) in the axial direction from the center, and in which the spherical center of the outer diameter surface and the spherical center of the inner diameter surface of the cage include the center of the ball. Is offset to the opposite side by an equal distance (f) in the axial direction, and connects the center of the guide groove of the outer joint member or the center of the guide groove of the inner joint member and the center of the ball with the offset amount (F). Ratio of line segment length (PCR) R1 (= F / PCR)
Is within the range of 0.069 ≦ R1 ≦ 0.121, and the ratio R2 (= f / PCR) between the offset amount (f) and the (PCR) is 0 <R2 ≦ 0.052. Fixed type constant velocity universal joint for automobiles, characterized in that 【請求項６】 ボールのピッチ円径（ＰＣＤBALL）とボ
ールの直径（ＤBALL）との比ｒ１（＝ＰＣＤBALL／Ｄ
BALL）が、３．３≦ｒ１≦５．０の範囲内であることを
特徴とする請求項４又は５記載の自動車用固定型等速自
在継手。6. The ratio r1 (= PCD BALL / D) of the pitch circle diameter (PCD BALL ) of the ball and the diameter (D BALL ) of the ball.
BALL ) is within the range of 3.3 ≦ r1 ≦ 5.0. The fixed type constant velocity universal joint for an automobile according to claim 4 or 5, wherein 【請求項７】 ボールのピッチ円径（ＰＣＤBALL）とボ
ールの直径（ＤBALL）との比ｒ１（＝ＰＣＤBALL／Ｄ
BALL）が、３．３≦ｒ１≦５．０の範囲内であり、か
つ、外側継手部材の外径（ＤOUTER）と内側継手部材の
歯型のピッチ円径（ＰＣＤSERR）との比ｒ２（＝Ｄ
OUTER／ＰＣＤSERR）が、２．５≦ｒ２≦３．５の範囲
内であることを特徴とする請求項４又は５記載の自動車
用固定型等速自在継手。7. The ratio r1 (= PCD BALL / D) of the pitch circle diameter of the ball (PCD BALL ) and the diameter of the ball (D BALL ).
BALL ) is within the range of 3.3 ≦ r1 ≦ 5.0, and the ratio r2 of the outer diameter (D OUTER ) of the outer joint member and the tooth die pitch circle diameter (PCD SERR ) of the inner joint member. (= D
OUTER / PCD SERR ) is in the range of 2.5 ≦ r2 ≦ 3.5, wherein the fixed type constant velocity universal joint for an automobile according to claim 4 or 5.
JP13399896A 1995-12-26 1996-05-28 Fixed constant velocity universal joint for automobiles Expired - Lifetime JP3859264B2 (en)

Priority Applications (16)

Application Number Priority Date Filing Date Title
JP13399896A JP3859264B2 (en) 1996-05-28 1996-05-28 Fixed constant velocity universal joint for automobiles
AU11711/97A AU714553B2 (en) 1995-12-26 1996-12-19 Constant velocity joint
EP02003007A EP1209373B1 (en) 1995-12-26 1996-12-19 Constant velocity joint
US08/860,719 US6120382A (en) 1995-12-26 1996-12-19 Constant velocity joint
KR1019970705290A KR100472985B1 (en) 1995-12-26 1996-12-19 Constant velocity joint
EP02003004A EP1209372B1 (en) 1995-12-26 1996-12-19 Constant velocity joint
EP96942575A EP0802341B2 (en) 1995-12-26 1996-12-19 Constant velocity universal coupling
PCT/JP1996/003702 WO1997024538A1 (en) 1995-12-26 1996-12-19 Constant velocity universal coupling
DE69636726T DE69636726T2 (en) 1995-12-26 1996-12-19 CV joints
DE69636727T DE69636727T2 (en) 1995-12-26 1996-12-19 CV joints
DE69623439T DE69623439T3 (en) 1995-12-26 1996-12-19 HOMOKINETIC CRUSH
CN96192137A CN1087817C (en) 1995-12-26 1996-12-19 Constant velocity universal coupling
TW086104441A TW368566B (en) 1996-04-26 1997-04-08 Constant velocity joint
US09/500,532 US6386983B1 (en) 1995-12-26 2000-02-09 Constant velocity joint having eight torque transmitting balls
US09/500,649 US6267682B1 (en) 1995-12-26 2000-02-09 Constant velocity joint
CNB021015333A CN1260487C (en) 1995-12-26 2002-01-04 Constant speed universal coupling assembly

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP13399896A JP3859264B2 (en) 1996-05-28 1996-05-28 Fixed constant velocity universal joint for automobiles

Publications (2)

Publication Number Publication Date
JPH09317783A true JPH09317783A (en) 1997-12-09
JP3859264B2 JP3859264B2 (en) 2006-12-20

Family

ID=15118000

Family Applications (1)

Application Number Title Priority Date Filing Date
JP13399896A Expired - Lifetime JP3859264B2 (en) 1995-12-26 1996-05-28 Fixed constant velocity universal joint for automobiles

Country Status (1)

Country Link
JP (1) JP3859264B2 (en)

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0892187A2 (en) 1997-07-16 1999-01-20 Nsk Ltd Constant velocity ratio joint
WO2005068863A1 (en) * 2004-01-15 2005-07-28 Honda Motor Co., Ltd. Constant velocity joint
WO2005078302A1 (en) * 2004-02-13 2005-08-25 Ntn Corporation Constant velocity universal joint
JP2005226778A (en) * 2004-02-13 2005-08-25 Ntn Corp Constant velocity universal joint
JP2006194268A (en) * 2005-01-11 2006-07-27 Honda Motor Co Ltd Constant velocity universal joint
JP2007010079A (en) * 2005-07-01 2007-01-18 Ntn Corp Fixed type constant velocity universal joint
JP2007211803A (en) * 2006-02-07 2007-08-23 Ntn Corp Fixed type constant velocity universal joint
WO2008072521A1 (en) 2006-12-14 2008-06-19 Ntn Corporation Constant velocity universal joint
JP2009509106A (en) * 2005-09-23 2009-03-05 ジーケイエヌ ドライヴライン インターナショナル ゲゼルシャフト ミット ベシュレンクテル ハフツング Constant velocity universal shaft joint with undercutless ball raceway
WO2009145035A1 (en) * 2008-05-30 2009-12-03 Ntn株式会社 Fixed‑type, constant‑velocity universal joint
JP2009287715A (en) * 2008-05-30 2009-12-10 Ntn Corp Fixed-type, constant-velocity universal joint
JP2009287711A (en) * 2008-05-30 2009-12-10 Ntn Corp Fixed-type, constant-velocity universal joint
WO2009150942A1 (en) 2008-06-13 2009-12-17 Ntn株式会社 Fixed uniform-motion universal joint
WO2011065400A1 (en) 2009-11-26 2011-06-03 Ntn株式会社 Stationary constant-velocity universal joint
JP2012021546A (en) * 2010-07-12 2012-02-02 Ntn Corp Fixed type constant velocity universal joint

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2149719B1 (en) 2007-03-27 2013-06-19 NTN Corporation Fixed uniform-motion universal coupling
US8292749B2 (en) 2007-09-26 2012-10-23 Ntn Corporation Fixed type constant velocity universal joint
JP5420369B2 (en) 2009-10-08 2014-02-19 Ｎｔｎ株式会社 Fixed constant velocity universal joint
JP5823127B2 (en) 2011-01-06 2015-11-25 Ntn株式会社 Fixed constant velocity universal joint
JP6328452B2 (en) 2014-03-17 2018-05-23 Ntn株式会社 Fixed constant velocity universal joint

Cited By (26)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0892187A2 (en) 1997-07-16 1999-01-20 Nsk Ltd Constant velocity ratio joint
EP1326027A1 (en) 1997-07-16 2003-07-09 Nsk Ltd Constant velocity joint for wheels
WO2005068863A1 (en) * 2004-01-15 2005-07-28 Honda Motor Co., Ltd. Constant velocity joint
US7632190B2 (en) 2004-01-15 2009-12-15 Honda Motor Co., Ltd. Constant velocity joint
JP2005226778A (en) * 2004-02-13 2005-08-25 Ntn Corp Constant velocity universal joint
US8162764B2 (en) 2004-02-13 2012-04-24 Ntn Corporation Constant velocity universal joint
WO2005078302A1 (en) * 2004-02-13 2005-08-25 Ntn Corporation Constant velocity universal joint
JP2006194268A (en) * 2005-01-11 2006-07-27 Honda Motor Co Ltd Constant velocity universal joint
JP2007010079A (en) * 2005-07-01 2007-01-18 Ntn Corp Fixed type constant velocity universal joint
JP2009509106A (en) * 2005-09-23 2009-03-05 ジーケイエヌ ドライヴライン インターナショナル ゲゼルシャフト ミット ベシュレンクテル ハフツング Constant velocity universal shaft joint with undercutless ball raceway
JP2007211803A (en) * 2006-02-07 2007-08-23 Ntn Corp Fixed type constant velocity universal joint
WO2008072521A1 (en) 2006-12-14 2008-06-19 Ntn Corporation Constant velocity universal joint
JP2008151182A (en) * 2006-12-14 2008-07-03 Ntn Corp Constant velocity universal joint
EP2101072A1 (en) * 2006-12-14 2009-09-16 NTN Corporation Constant velocity universal joint
EP2101072A4 (en) * 2006-12-14 2012-04-18 Ntn Toyo Bearing Co Ltd Constant velocity universal joint
US8162765B2 (en) 2006-12-14 2012-04-24 Ntn Corporation Constant velocity universal joint
WO2009145035A1 (en) * 2008-05-30 2009-12-03 Ntn株式会社 Fixed‑type, constant‑velocity universal joint
JP2009287711A (en) * 2008-05-30 2009-12-10 Ntn Corp Fixed-type, constant-velocity universal joint
JP2009287715A (en) * 2008-05-30 2009-12-10 Ntn Corp Fixed-type, constant-velocity universal joint
US8267802B2 (en) 2008-05-30 2012-09-18 Ntn Corporation Fixed-type, constant-velocity universal joint
JP2009299810A (en) * 2008-06-13 2009-12-24 Ntn Corp Fixed constant velocity universal joint
WO2009150942A1 (en) 2008-06-13 2009-12-17 Ntn株式会社 Fixed uniform-motion universal joint
US8545337B2 (en) 2008-06-13 2013-10-01 Ntn Corporation Fixed uniform-motion universal joint
WO2011065400A1 (en) 2009-11-26 2011-06-03 Ntn株式会社 Stationary constant-velocity universal joint
US8684849B2 (en) 2009-11-26 2014-04-01 Ntn Corporation Fixed type constant velocity universal joint
JP2012021546A (en) * 2010-07-12 2012-02-02 Ntn Corp Fixed type constant velocity universal joint

Also Published As

Publication number Publication date
JP3859264B2 (en) 2006-12-20

Similar Documents

Publication Publication Date Title
JP3859264B2 (en) Fixed constant velocity universal joint for automobiles
JP3859295B2 (en) Sliding type constant velocity universal joint
EP0802341B2 (en) Constant velocity universal coupling
CN102575720B (en) Fixed type constant velocity universal joint
JP4041657B2 (en) Constant velocity universal joint
EP2908020B1 (en) Fixed-type constant-velocity universal joint
JP2000240673A (en) Constant velocity universal joint for propeller shaft and propeller shaft
JP3859267B2 (en) Fixed type constant velocity universal joint
JP2001153149A (en) Fixed constant velocity universal joint
JP3460107B2 (en) Constant velocity universal joint
JP4262863B2 (en) Fixed type constant velocity universal joint
JP2003307235A (en) Constant velocity universal joint
JP4896662B2 (en) Fixed constant velocity universal joint
US7147565B2 (en) Fixed type constant velocity joint
CN108496019B (en) Fixed constant velocity universal joint
JP2008019961A (en) Fixed constant velocity universal joint
WO2007058201A1 (en) Fixed constant velocity universal joint
KR100472985B1 (en) Constant velocity joint
JP2001330051A (en) Constant velocity universal joint
JP5398968B2 (en) Fixed constant velocity universal joint
JP2008261390A (en) Fixed constant velocity universal joint
JP2001349333A (en) Constant velocity universal joint
JP5220480B2 (en) Fixed type constant velocity universal joint
JP2007107568A (en) Fixed constant velocity universal joint
JP2008267407A (en) Fixed type constant velocity universal joint

Legal Events

Date Code Title Description
A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20060202

A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20060403

TRDD Decision of grant or rejection written
A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

Effective date: 20060818

A61 First payment of annual fees (during grant procedure)

Free format text: JAPANESE INTERMEDIATE CODE: A61

Effective date: 20060919

R150 Certificate of patent (=grant) or registration of utility model

Free format text: JAPANESE INTERMEDIATE CODE: R150

FPAY Renewal fee payment (prs date is renewal date of database)

Free format text: PAYMENT UNTIL: 20090929

Year of fee payment: 3

FPAY Renewal fee payment (prs date is renewal date of database)

Free format text: PAYMENT UNTIL: 20100929

Year of fee payment: 4

FPAY Renewal fee payment (prs date is renewal date of database)

Free format text: PAYMENT UNTIL: 20100929

Year of fee payment: 4

FPAY Renewal fee payment (prs date is renewal date of database)

Free format text: PAYMENT UNTIL: 20110929

Year of fee payment: 5

FPAY Renewal fee payment (prs date is renewal date of database)

Free format text: PAYMENT UNTIL: 20120929

Year of fee payment: 6

FPAY Renewal fee payment (prs date is renewal date of database)

Free format text: PAYMENT UNTIL: 20130929

Year of fee payment: 7

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

EXPY Cancellation because of completion of term