JPH031531B2 - - Google Patents

Info

Publication number
JPH031531B2
JPH031531B2 JP62135690A JP13569087A JPH031531B2 JP H031531 B2 JPH031531 B2 JP H031531B2 JP 62135690 A JP62135690 A JP 62135690A JP 13569087 A JP13569087 A JP 13569087A JP H031531 B2 JPH031531 B2 JP H031531B2
Authority
JP
Japan
Prior art keywords
rollers
trunnion
row
roller
end side
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
JP62135690A
Other languages
Japanese (ja)
Other versions
JPS63303227A (en
Inventor
Takayori Naganuma
Shigeru Izawa
Teruaki Ookami
Keiichiro Makase
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.)
Koyo Seiko Co Ltd
Nippon Steel Corp
Original Assignee
Koyo Seiko Co Ltd
Nippon Steel Corp
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 Koyo Seiko Co Ltd, Nippon Steel Corp filed Critical Koyo Seiko Co Ltd
Priority to JP62135690A priority Critical patent/JPS63303227A/en
Publication of JPS63303227A publication Critical patent/JPS63303227A/en
Publication of JPH031531B2 publication Critical patent/JPH031531B2/ja
Granted 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/24—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for radial load mainly
    • F16C19/28—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for radial load mainly with two or more rows of rollers
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C21/00—Combinations of sliding-contact bearings with ball or roller bearings, for exclusively rotary movement
    • F16C21/005—Combinations of sliding-contact bearings with ball or roller bearings, for exclusively rotary movement the external zone of a bearing with rolling members, e.g. needles, being cup-shaped, with or without a separate thrust-bearing disc or ring, e.g. for universal joints
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/26—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected
    • F16D3/38—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected with a single intermediate member with trunnions or bearings arranged on two axes perpendicular to one another
    • F16D3/40—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected with a single intermediate member with trunnions or bearings arranged on two axes perpendicular to one another with intermediate member provided with two pairs of outwardly-directed trunnions on intersecting axes
    • F16D3/41—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected with a single intermediate member with trunnions or bearings arranged on two axes perpendicular to one another with intermediate member provided with two pairs of outwardly-directed trunnions on intersecting axes with ball or roller bearings
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/41—Couplings

Landscapes

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

Description

【発明の詳細な説明】 〈産業上の利用分野〉 本発明は、ユニバーサルジヨイントにおける十
字軸のトラニオンに装着される軸受装置であつ
て、２列以上のころを備えるものに関する。DETAILED DESCRIPTION OF THE INVENTION <Industrial Application Field> The present invention relates to a bearing device mounted on a trunnion of a cross shaft in a universal joint, which is provided with two or more rows of rollers.

〈従来の技術〉 従来のこの種の軸受装置の１列を第５図ないし
第８図に示して説明する。なお、第７図および第
８図においてトラニオンの傾きは説明の都合上極
端に大きく示している。<Prior Art> One row of conventional bearing devices of this type will be described with reference to FIGS. 5 to 8. Note that in FIGS. 7 and 8, the inclination of the trunnion is shown extremely large for convenience of explanation.

図において、符号１０は第１回転軸１１の軸端
に形成された第１ヨーク、符号２０は第２回転軸
（図示省略）の軸端に連結される第２ヨーク、符
号３０は十字軸、符号４０は軸受装置、符号５０
は密封装置、符号６０は軸受装置４０へのグリー
スの供給口としてのグリースニツプルをそれぞれ
示している。 In the figure, numeral 10 is a first yoke formed at the shaft end of the first rotating shaft 11, numeral 20 is a second yoke connected to the axial end of a second rotating shaft (not shown), numeral 30 is a cross shaft, Reference numeral 40 is a bearing device, reference numeral 50
Reference numeral 60 indicates a sealing device, and reference numeral 60 indicates a grease nipple serving as a grease supply port to the bearing device 40.

十字軸３０の各トラニオン３１に軸受装置４０
が装着されて、この軸受装置４０の軸受ケース４
１が第１ヨーク１０や第２ヨーク２０に係合され
てボルト７０などで連結されるようになつてい
る。 A bearing device 40 is attached to each trunnion 31 of the cross shaft 30.
is installed, and the bearing case 4 of this bearing device 40
1 is engaged with the first yoke 10 and the second yoke 20 and connected with bolts 70 or the like.

軸受装置４０は、軸受ケース４１、スラストワ
ツシヤ４２、複数のころ４３ａ〜４３ｃで構成さ
れており、ころ４３ａ〜４３ｃはトラニオン３１
の軸心方向に沿つて３列に配列されている。な
お、図では、トラニオン３１の基端側に配されて
いるころを４３ａ、中間に配されているころを４
３ｂ、トラニオン３１の先端側に配されているこ
ろを４３ｃとしている。 The bearing device 40 includes a bearing case 41, a thrust washer 42, and a plurality of rollers 43a to 43c.
They are arranged in three rows along the axial direction. In addition, in the figure, the roller arranged on the base end side of the trunnion 31 is called 43a, and the roller arranged in the middle is called 43a.
3b, and the roller disposed on the tip side of the trunnion 31 is designated 43c.

密封装置５０は、オイルシール５１、スリンガ
ー５２、ウオーターシール５３で構成されてお
り、トラニオン３１の基端側に装着されている。 The sealing device 50 includes an oil seal 51, a slinger 52, and a water seal 53, and is attached to the proximal end of the trunnion 31.

通常、上記のようなユニバーサルジヨイント
は、例えば圧延機の駆動軸のように非常に大きな
トルクが負荷されるところに使用されるのである
が、軸受装置の負荷容量を増すため、ころ４３ａ
〜４３ｃと軸受ケース４１およびトラニオン３１
とのころの有効接触長さを長くする際に、単一の
ころではころの全長を長くすることに加工精度上
困難さが伴うという問題、およびころがあまりに
も長くなると負荷がかかつた時にころに曲がりが
生じ、そのためころが折れるというような問題が
生ずるのを未然に防止する目的で、単一のころを
軸方向に２つ以上に分割して上記のような２列以
上のころを備えた軸受装置の形式としている。 Generally, the above-mentioned universal joint is used where a very large torque is applied, such as the drive shaft of a rolling mill, but in order to increase the load capacity of the bearing device, the roller 43a is used.
~43c and bearing case 41 and trunnion 31
When increasing the effective contact length of the roller, there are problems with machining accuracy difficulties in increasing the total length of the roller with a single roller, and when the roller is too long, it becomes difficult to In order to prevent problems such as roller bending and roller breakage, a single roller is divided into two or more in the axial direction and two or more rows of rollers as described above are created. It is a type of bearing device equipped with

しかしながら、上記のような軸受装置にあつて
も、各列のころ４３ａ〜４３ｃと軸受ケース４１
およびトラニオン３１との間には軸受として機能
するために内部隙間というものがμｍの単位では
あるがどうしても必要であり、そのため例えば第
１ヨーク１０（または第２ヨーク２０）から第２
ヨーク２０（または第１ヨーク１０）に動力を伝
達しようとして、第１ヨーク１０から軸受ケース
４１を介して十字軸３０の２つのトラニオン３１
に力が働き、また残りの他の２つのトラニオン３
１から軸受ケース４１を介して第２ヨーク２０に
力が働き、軸受ケース４１とトラニオン３１との
間に介在されているころ４３ａ〜４３ｃに対して
ラジアル方向の荷重が作用したときに、各列のこ
ろ４３ａ〜４３ｃとトラニオン３１との当接情態
が第７図に示すように変化することになる。 However, even in the bearing device as described above, each row of rollers 43a to 43c and the bearing case 41
In order to function as a bearing, an internal gap is necessary between the first yoke 10 (or second yoke 20) and the trunnion 31, although it is in the μm unit.
In an attempt to transmit power to the yoke 20 (or the first yoke 10), the two trunnions 31 of the cross shaft 30 are transmitted from the first yoke 10 through the bearing case 41.
The force acts on the remaining two trunnions 3
1 to the second yoke 20 via the bearing case 41, and a radial load acts on the rollers 43a to 43c interposed between the bearing case 41 and the trunnion 31. The state of contact between the rollers 43a to 43c and the trunnion 31 changes as shown in FIG.

なお、第７図において、ころ４３ａ〜４３ｃは
それぞれ軸方向の両端にクラウニングＡ，Ｂを施
したものを示している。 In addition, in FIG. 7, the rollers 43a to 43c are shown with crownings A and B provided at both ends in the axial direction, respectively.

まず、動力を伝達し始める際において当初は、
第７図ａに示すように、トラニオン３１の軸心と
軸受ケース４１の軸心とが平行にならずに微小な
がら前記軸受内部隙間分だけ傾き、トラニオン３
１の先端側に配されるころ４３ｃにのみ当接し、
次第に第７図ｂおよびｃに示すように、トラニオ
ン３１がしなるとともにころ４３ａ〜４３ｃも若
干ながら弾性変形してトラニオン３１の外周面が
ころ４３ａ〜４３ｃの外周面にほぼ全体に当接す
る。 First, when starting to transmit power, initially,
As shown in FIG. 7a, the axial center of the trunnion 31 and the axial center of the bearing case 41 are not parallel to each other, but are slightly tilted by the internal clearance of the bearing, and the trunnion 31
It contacts only the roller 43c arranged on the tip side of 1,
Gradually, as shown in FIGS. 7b and 7c, as the trunnion 31 bends, the rollers 43a to 43c are also slightly elastically deformed, so that the outer circumferential surface of the trunnion 31 almost entirely contacts the outer circumferential surfaces of the rollers 43a to 43c.

このために、トラニオン３１の先端側に配され
るころ４３ｃに作用する荷重と基端側に配される
ころ４３ａに作用する荷重とでは差が生ずる。 For this reason, a difference occurs between the load acting on the roller 43c disposed on the distal end side of the trunnion 31 and the load acting on the roller 43a disposed on the proximal end side.

具体的に、各列のころ４３ａ〜４３ｃに作用す
る荷重分布を第８図を参照して説明する。 Specifically, the load distribution acting on the rollers 43a to 43c in each row will be explained with reference to FIG.

図に示すように、トラニオン３１の先端側に配
されているころ４３ｃに作用する荷重分布は、ト
ラニオン３１の基端側に配されているころ４３ａ
のそれよりも大きくなる。条件に応じて若干異な
るがころ４３ｃにかかる荷重はころ４３ａにかか
る荷重よりも約３倍も大きいことが判つており、
トラニオン３１の先端側に配されているころ４３
ｃに対して荷重が集中して働く。 As shown in the figure, the load distribution acting on the roller 43c disposed on the distal end side of the trunnion 31 is different from the load distribution acting on the roller 43c disposed on the proximal end side of the trunnion 31.
be larger than that of Although it varies slightly depending on the conditions, it is known that the load applied to roller 43c is about three times greater than the load applied to roller 43a.
Roller 43 arranged on the tip side of trunnion 31
The load acts concentratedly on c.

このために、前記先端側のころ４３ｃの剥離つ
まりフレーキング現象が生じ、結果的に軸受寿命
が短くなつていた。 For this reason, the roller 43c on the tip end side peels off, that is, flaking phenomenon occurs, resulting in a shortened bearing life.

なお、２列以上のころを備えた軸受装置を有す
るユニバーサルジヨイントであつて、軸受の寿命
を向上させることを目的とするものとして特公昭
56−21935号公報に記載のものが知られている。 In addition, it is a universal joint that has a bearing device equipped with two or more rows of rollers, and is designed to improve the life of the bearing.
The one described in Japanese Patent No. 56-21935 is known.

この特公昭56−21935号公報に記載のユニバー
サルジヨイントは十字軸のトラニオンを段状に先
端側にいくほど細く形成して、トラニオンの全長
をできるだけ長くすることにより、ころの有効接
触長さを長くして軸受の寿命を向上させようとし
たものである。 In the universal joint described in Japanese Patent Publication No. 56-21935, the trunnion of the cross shaft is formed in a stepped manner so that it becomes thinner toward the tip, and by making the total length of the trunnion as long as possible, the effective contact length of the rollers can be increased. This is an attempt to extend the life of the bearing by making it longer.

〈発明が解決しようとする問題点〉 特公昭56−21935号公報のようなユニバーサル
ジヨイントの構成であつても、第７図で示した従
来技術と同様にトラニオンの先端側のころから順
にトラニオンのしなりとともに基端側のころへと
荷重が加わるという現象が生じ、結果的には先に
説明した第７図の従来技術のものと同様、先端側
のころのみに過大な荷重が負荷されて各列のころ
に均等な荷重を負荷させるということができな
い。<Problems to be Solved by the Invention> Even with the configuration of the universal joint as disclosed in Japanese Patent Publication No. 56-21935, the trunnion is moved in order from the roller on the tip side of the trunnion, as in the prior art shown in FIG. As the roller bends, a phenomenon occurs in which a load is applied to the rollers on the proximal end side, and as a result, an excessive load is applied only to the rollers on the distal end side, similar to the prior art shown in Fig. 7 explained earlier. Therefore, it is not possible to apply an equal load to each row of rollers.

本発明は、このトラニオンの先端側のころのみ
に過大な荷重が負荷されるという現象を防止し、
各列のころが均等に荷重を負荷して、結果的に各
列のころに加わる荷重を小さくして軸受の寿命を
向上させることを目的としている。 The present invention prevents the phenomenon that an excessive load is applied only to the roller on the tip side of the trunnion,
The purpose is to apply loads evenly to each row of rollers, thereby reducing the load applied to each row of rollers and improving the life of the bearing.

〈問題点を解決するための手段〉 本発明はこのような目的を達成するために、次
のような構成をとる。<Means for Solving the Problems> In order to achieve the above object, the present invention has the following configuration.

即ち、本発明にかかるユニバーサルジヨイント
の軸受装置は、ユニバーサルジヨイントにおける
十字軸のトラニオンに装着されるとともに、この
トラニオンの軸心方向に沿つてトラニオンに直接
配列され両端角部にクラウニングが形成された２
列以上のころを備えたものであつて、 前記トラニオンの基端側から先端側に配列され
る前記各列のころの直径を先端側の列のころほど
小径にすることにより、前記先端側に配列される
ころ列における軸受内部隙間が、前記基端側に配
列されるころ列の軸受内部隙間よりも大きく設定
されているとともに、前記各列のころの両端角部
のクラウニング量を異ならせ、かつ前記各列のこ
ろが大クラウニング側を前記トラニオンの先端側
に向けて配列されてなることに特徴を有するもの
である。 That is, the universal joint bearing device according to the present invention is mounted on the trunnion of the cross shaft in the universal joint, and is directly arranged on the trunnion along the axial direction of the trunnion, with crowning formed at both end corners. Ta2
It is provided with more than one row of rollers, and the diameter of the rollers in each row arranged from the base end side to the distal end side of the trunnion is made smaller as the rollers in the row on the distal end side, so that the diameter of the rollers on the distal end side is reduced. The bearing internal clearance in the arranged roller rows is set to be larger than the bearing internal clearance in the roller row arranged on the base end side, and the amount of crowning of both end corners of the rollers in each row is different, Further, the rollers in each row are arranged with the large crowning side facing the tip side of the trunnion.

〈作用〉 本発明の構成による作用は次のとおりである。<Effect> The effects of the configuration of the present invention are as follows.

動力伝達時において、トラニオンの軸心と軸受
ケースの軸心とは軸受内部隙間の量だけ傾く。 During power transmission, the axis of the trunnion and the axis of the bearing case are tilted by the amount of the bearing internal clearance.

この軸受内部隙間は、トラニオンの基端側から
先端側に配列される前記各列のころの直径を先端
側の列のころほど小径にすることにより、前記先
端側に配されるころ列における軸受内部隙間が、
前記基端側に配されるころ列の軸受内部隙間より
も大きく設定されているので、トラニオンが傾い
たときに、トラニオンの外周面と各列の総てのこ
ろとがほぼ同時に当接する。そして、負荷が加わ
りトラニオンがしなるとともに前記各ころが若干
ながら弾性変形して総てのころの外周面とトラニ
オンの外周面とが全面的にほぼ均一に当接するこ
ととなる。 This bearing internal gap is created by making the diameters of the rollers in each row arranged from the base end side to the distal end side of the trunnion smaller as the rollers in the row on the distal end side. The internal gap is
Since the clearance is set larger than the bearing internal clearance of the roller row arranged on the base end side, when the trunnion is tilted, the outer circumferential surface of the trunnion and all the rollers of each row come into contact almost simultaneously. Then, as a load is applied and the trunnion bends, each of the rollers is slightly elastically deformed, and the outer circumferential surfaces of all the rollers and the outer circumferential surface of the trunnion come into contact substantially uniformly over the entire surface.

このために、従来のようにトラニオンの先端側
に配されるころに対して荷重が集中することを防
げて、前記先端側に配れるころが受ける荷重と前
記基端側に配されるころが受ける荷重との差が従
来に比べて大幅に小さくなる。 For this reason, it is possible to prevent the load from concentrating on the rollers disposed at the distal end of the trunnion as in the past, and the load received by the rollers disposed at the distal end is borne by the rollers disposed at the proximal end. The difference in load is significantly smaller than before.

換言すれば、各列ごとのころに作用する荷重が
ほぼ均等になる。 In other words, the loads acting on the rollers in each row are approximately equal.

また、各ころの軸方向両端にクラウニング量の
異なるクラウニングを形成して、かつ各列のころ
における大クラウニング側をトラニオン先端側へ
向けるよう各ころを配列させているので、各列の
ころにおけるトラニオン基端側の角部（小クラウ
ニング部分）に対する荷重の立とち下がり部分が
無くなり、各ころ列に作用する荷重がより一層均
等になりやすくなる。 In addition, crowning with different amounts of crowning is formed on both ends of each roller in the axial direction, and the rollers are arranged so that the large crowning side of each row of rollers faces toward the tip of the trunnion. There is no falling part of the load on the base end side corner (small crowning part), making it easier for the load acting on each roller row to be more even.

〈実施例〉 以下、本発明の実施例を図面に基づいて詳細に
説明する。<Example> Hereinafter, an example of the present invention will be described in detail based on the drawings.

第１図ないし第４図に本発明の一実施例を示し
ている。これらの図において、第５図ないし第８
図に付してある符号と同一の符号は同一部品もし
くは対応する部分を指す。なお、本実施例にかか
る第１図ないし第４図においても説明の都合上ト
ラニオンの傾きや各ころの径差を極端に大きく示
している。 An embodiment of the present invention is shown in FIGS. 1 to 4. In these figures, figures 5 to 8
The same reference numerals as in the figures refer to the same parts or corresponding parts. Note that in FIGS. 1 to 4 according to this embodiment, the inclination of the trunnion and the difference in diameter of each roller are shown to be extremely large for convenience of explanation.

本実施例において従来例を同様の構成について
はその説明を省略し、異なる構成について詳細に
説明する。 In this embodiment, a description of structures similar to those of the conventional example will be omitted, and a different structure will be described in detail.

第１図に示すように、十字軸３０のトラニオン
３１の基端側に配されるころ４３ａの直径C1を、
トラニオン３１の中間位置に配されるころ４３ｂ
の直径C2およびトラニオン３１の先端側に配さ
れるころ４３ｃの直径C3よりも大きく設定して
あり、また、前記中間位置に配されるころ４３ｂ
の直径C2も前記先端側に配されるころ４３ｃの
直径C3より大きく設定されている。 As shown in FIG. 1, the diameter C 1 of the roller 43a disposed on the base end side of the trunnion 31 of the cross shaft 30 is
Roller 43b arranged at an intermediate position of trunnion 31
The diameter C 2 of the trunnion 31 is set larger than the diameter C 3 of the roller 43c disposed at the tip side of the trunnion 31, and the roller 43b disposed at the intermediate position
The diameter C 2 of the roller 43c is also set larger than the diameter C 3 of the roller 43c disposed on the tip side.

つまり、直径に関して、C1＞C2＞C3の関係に
なつている。 In other words, regarding the diameter, the relationship is C 1 > C 2 > C 3 .

具体的に例えば、これらころ４３ａ〜４３ｃの
軸方向長さを72mmと一定にし、ころ４３ｃの直径
C3を36mm、ころ４３ｂの直径C2を36mm＋25μｍ、
ころ４３ａの直径C1を36mm＋35μｍにそれぞれ設
定する。 Specifically, for example, the axial length of these rollers 43a to 43c is constant at 72 mm, and the diameter of roller 43c is
C 3 is 36 mm, diameter C 2 of roller 43b is 36 mm + 25 μm,
The diameter C 1 of the roller 43a is set to 36 mm + 35 μm.

このように、ころ４３ａ〜４３ｃの直径C1〜
C3をそれぞれ例えばμｍ単位で変えることによ
り、前記先端側のころ４３ｃでの軸受内部隙間
を、前記基端側のころ４３ａでの軸受内部隙間よ
りも例えばμｍ単位で大きくしてある。 In this way, the diameters C 1 to 43c of the rollers 43a to 43c
By varying C 3 by, for example, μm, the bearing internal clearance at the tip end roller 43c is made larger, for example, by μm, from the bearing internal clearance at the proximal roller 43a.

なお、第１図及び第２図においては、単に各列
のころ４３ａ〜４３ｃの直径を変えただけとし、
各ころ４３ａ〜４３ｃの軸方向両端のクラウニン
グＡ，Ｂを施している。 In addition, in FIGS. 1 and 2, it is assumed that the diameters of the rollers 43a to 43c in each row are simply changed,
Crownings A and B are provided at both axial ends of each of the rollers 43a to 43c.

次に、第１図に示した構造における動作を第２
図ａないしｃを参照して説明する。 Next, we will explain the operation of the structure shown in Figure 1 in the second example.
This will be explained with reference to figures a to c.

動力伝達時において、トラニオン３１が軸受内
部隙間の量だけ傾いたときに、第２図ａに示すよ
うに、トラニオン３１の外周面と各列の総てのこ
ろ４３ａ〜４３ｃの外周面とが初めて部分的に当
接し、次第に第２図ｂおよびｃに示すように前記
トラニオン３１がしなるとともにころ４３ａ〜４
３ｃも若干ながら弾性変形して、前記総てのころ
４３ａ〜４３ｃの外周面と前記トラニオン３１の
外周面とが全面的にほぼ均一に当接することとな
る。 During power transmission, when the trunnion 31 is tilted by the amount of the bearing internal clearance, as shown in FIG. The rollers 43a to 4 partially abut, and as the trunnion 31 gradually bends as shown in FIGS. 2b and 2c,
3c is also slightly elastically deformed, and the outer circumferential surfaces of all the rollers 43a to 43c and the outer circumferential surface of the trunnion 31 come into contact substantially uniformly over the entire surface.

このために、従来のようにトラニオン３１の先
端側に配されるころ４３ｃに対して荷重が集中す
ることを防ぐことができ、第３図に示すように、
前記先端側に配されるころ４３ｃが受ける荷重と
前記基端側に配されるころ４３ａが受ける荷重と
の差を従来に比べて大幅に小さくすることができ
る。 For this reason, it is possible to prevent the load from concentrating on the roller 43c disposed on the tip side of the trunnion 31 as in the conventional case, and as shown in FIG.
The difference between the load received by the roller 43c disposed on the distal end side and the load received on the roller 43a disposed on the proximal end side can be significantly reduced compared to the prior art.

換言すれば、各列ごとのころ４３ａ〜４３ｃに
作用する荷重をほぼ均等にすることができる。 In other words, the loads acting on the rollers 43a to 43c in each row can be made almost equal.

このように、各列のころ４３ａ〜４３ｃの直径
を変えると、各ころ４３ａ〜４３ｃに作用する荷
重をほぼ均等にできるが、ただ第３図に示すよう
に各列のころ４３ａ〜４３ｃの軸方向両端のクラ
ウニングＡ，Ｂのクラウニング量を同一にしたま
まにしていると、各列のころ４３ａ〜４３ｃのト
ラニオン基端側の角部での荷重の立ち下がり部分
が大きくなる。 In this way, by changing the diameters of the rollers 43a to 43c in each row, the loads acting on each roller 43a to 43c can be made almost equal, but as shown in FIG. If the crowning amounts of the crownings A and B at both ends in the direction are kept the same, the falling portion of the load at the corner of the trunnion proximal end of each row of rollers 43a to 43c becomes large.

そこで、本発明では第４図に示すように、各列
のころ４３ａ〜４３ｃの直径を変えるとともに、
各列のころ４３ａ〜４３におけるトラニオン３１
の基端側の角部のクラウニングＢの量を、各列の
ころ４３ａ〜４３ｃにおけるトラニオン３１の先
端側の角部に形成してあるクラウニングＡの量よ
りも小さくしてある。つまり、各ころ４３ａ〜４
３ｃを、それらの大クラウニングＡ側をトラニオ
ン３１の先端側へ向けるように配列させている。
なお、クラウニングＡ，Ｂの傾斜角度は総てのこ
ろ４３ａ〜４３ｃについて同一にして、その一方
のクラウニングＢの軸方向幅B1〜B3を他方のク
ラウニングＡの軸方向幅A1〜A3よりも小さくす
ることで、クラウニングＡ，Ｂのクラウニング量
を設定してある。 Therefore, in the present invention, as shown in FIG. 4, while changing the diameters of the rollers 43a to 43c in each row,
Trunnions 31 in each row of rollers 43a to 43
The amount of crowning B at the corner on the proximal end side is made smaller than the amount of crowning A formed at the corner on the tip side of the trunnion 31 in each row of rollers 43a to 43c. In other words, each roller 43a to 4
3c are arranged so that their large crowning A side faces toward the tip side of the trunnion 31.
Note that the inclination angles of the crownings A and B are the same for all rollers 43a to 43c, and the axial width B 1 to B 3 of one crowning B is the same as the axial width A 1 to A 3 of the other crowning A. The crowning amount of crowning A and crowning B is set by making it smaller than .

このように各列のころ４３ａ〜４３ｃの軸方向
両端の各クラウニングＡ，Ｂの量を変えて、各列
のころ４３ａ〜４３ｃのクラウニングＡ，Ｂの配
向方向を特定すると、第４図から判るように、第
３図に示す各ころ４３ａ〜４３ｃにおけるトラニ
オン３１の基端側の角部に対応する荷重の立ち下
がり部分を無くすことができ、各列のころ４３ａ
〜４３ｃに作用する荷重をより一層均等にするこ
とができる。 In this way, by changing the amounts of the crownings A and B at both axial ends of the rollers 43a to 43c in each row and specifying the orientation direction of the crownings A and B of the rollers 43a to 43c in each row, it can be seen from FIG. As shown in FIG. 3, it is possible to eliminate the falling portion of the load corresponding to the proximal corner of the trunnion 31 in each of the rollers 43a to 43c shown in FIG.
The load acting on ~43c can be made even more uniform.

このようなクラウニングＡ，Ｂの量は、前述の
ようにころ４３ａ〜４３ｃの角部の傾斜角度を一
定にして軸方向幅A1〜A3，B1〜B3を変化させて
設定する以外に、例えば軸方向幅A1〜A3，B1〜
B3を一定として傾斜角度を変化させることでも
設定することができる。 The amounts of crowning A and B can be set by changing the axial widths A 1 to A 3 and B 1 to B 3 while keeping the angle of inclination of the corners of the rollers 43a to 43c constant as described above. For example, the axial widths A 1 ~ A 3 , B 1 ~
It can also be set by changing the inclination angle while keeping B 3 constant.

なお、上記実施例においては３列のころ４３ａ
〜４３ｃを有する軸受装置４０を例示してある
が、本発明はこれに限定されず、例えば２列や３
列以上のものも含む。 In addition, in the above embodiment, three rows of rollers 43a
Although the bearing device 40 having the bearing device 43c is illustrated, the present invention is not limited thereto, and for example
Including more than columns.

〈発明の効果〉 本発明によれば、次の効果を発揮する。<Effect of the invention> According to the present invention, the following effects are achieved.

動力伝達時において、軸受内部隙間の量だけト
ラニオンの軸心と軸受装置の軸受ケースの軸心と
が傾いたときに、初めてトラニオンの外周面と各
列総てのころの外周面とが部分的にそれぞれ当接
し、次第にトラニオンが若干ながらしなるととと
もにころも若干ながら弾性変形して、トラニオン
の外周面と総てのころの外周面とが全面的にほぼ
均等に当接するのである。しかも、そのときに各
列のころのトラニオン基端側の角部での荷重の立
ち下がり部分が極力発生しなくなる。 During power transmission, when the axial center of the trunnion and the axial center of the bearing case of the bearing device are tilted by the amount of the internal clearance of the bearing, the outer circumferential surface of the trunnion and the outer circumferential surfaces of all rollers in each row are partially aligned. The trunnion gradually bends slightly and the rollers are also slightly elastically deformed, so that the outer circumferential surface of the trunnion and the outer circumferential surfaces of all the rollers come into almost equal contact over the entire surface. Moreover, at this time, the falling portion of the load at the corner of each row of rollers on the proximal end of the trunnion is minimized.

即ち、軸受内部隙間ところの非対称クラウニン
グのそれぞれの方向性を特定したことによる相乗
効果によつて、従来のようにトラニオンの先端側
に配されるころに対して荷重が集中するのを防ぐ
ことができるから、前記先端側に配されるころに
作用する荷重と前記基端側に配されるころに作用
する荷重との差を従来に比べて大幅に小さくする
ことができる。 In other words, the synergistic effect of identifying the directions of the bearing internal gap and the asymmetric crowning makes it possible to prevent the load from concentrating on the rollers placed at the tip of the trunnion as in the past. Therefore, the difference between the load acting on the rollers disposed on the distal end side and the load acting on the rollers disposed on the proximal end side can be made significantly smaller than in the past.

したがつて、各列ごとのころに作用する荷重を
ほぼ均等にすることができるので、一部のころに
従来のようなフレーキング現象が生ずるのを阻止
することができて、軸受寿命を延ばすのに貢献で
きる。 Therefore, the load acting on the rollers in each row can be made almost equal, which prevents the conventional flaking phenomenon from occurring on some rollers, extending the life of the bearing. can contribute to

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

第１図ないし第４図は本発明の一実施例にかか
り、第１図は十字軸に装着した状態の軸受装置の
要部を示す縦断側面図、第２図ａないしｃは動作
を説明するための軸受装置の部分断面図、第３図
は各列のころの直径を変えただけの構造における
荷重分布を示す説明図、第４図は第３図に対応す
る本発明の荷重分布図である。 また、第５図ないし第８図は従来例にかかり、
第５図はユニバーサルジヨイントを示す分解斜視
図、第６図は十字軸および軸受装置を示す要部縦
断側面図、第７図ａないしｃは動作を説明するた
めの軸受装置の部分断面図、第８図は第７図ｃの
状態における荷重分布を示す説明図である。 ３０……十字軸、３１……トラニオン、４０…
…軸受装置、４１……軸受ケース、４３ａ〜４３
ｃ……ころ、C1〜C3……ころの直径。 Figures 1 to 4 show an embodiment of the present invention, with Figure 1 being a vertical sectional side view showing the main parts of the bearing device installed on the cross shaft, and Figures 2 a to c explaining the operation. Figure 3 is an explanatory diagram showing the load distribution in a structure in which the diameters of the rollers in each row are simply changed, and Figure 4 is a load distribution diagram of the present invention corresponding to Figure 3. be. Moreover, FIGS. 5 to 8 relate to the conventional example,
FIG. 5 is an exploded perspective view showing the universal joint, FIG. 6 is a longitudinal sectional side view of main parts showing the cross shaft and the bearing device, and FIGS. 7 a to c are partial sectional views of the bearing device to explain the operation. FIG. 8 is an explanatory diagram showing the load distribution in the state shown in FIG. 7c. 30...cross shaft, 31...trunnion, 40...
...Bearing device, 41...Bearing case, 43a-43
c... Roller, C 1 to C 3 ... Diameter of the roller.

Claims (1)

【特許請求の範囲】 １ ユニバーサルジヨイントにおける十字軸のト
ラニオンに装着されるとともに、このトラニオン
の軸心方向に沿つてトラニオンに直接配列され両
端角部にクラウニングが形成された２列以上のこ
ろを備えた軸受装置において、 前記トラニオンの基端側から先端側に配列され
る前記各列のころの直径を先端側の列のころほど
小径にすることにより、前記先端側に配列される
ころ列における軸受内部隙間が、前記基端側に配
列されるころ列の軸受内部隙間よりも大きく設定
されているとともに、前記各列のころの両端角部
のクラウニング量を異ならせ、かつ前記各例のこ
ろが大クラウニング側を前記トラニオンの先端側
に向けて配列されてなることを特徴とするユニバ
ーサルジヨイントの軸受装置。[Scope of Claims] 1. Two or more rows of rollers mounted on a trunnion of a cross shaft in a universal joint, arranged directly on the trunnion along the axial direction of the trunnion, and having crowning formed at both end corners. In the bearing device, the diameters of the rollers in each row arranged from the proximal end side to the distal end side of the trunnion are made smaller as the rollers in the row on the distal end side, so that the diameter of the rollers in the row of rollers arranged on the distal end side is reduced. The bearing internal clearance is set to be larger than the bearing internal clearance of the roller row arranged on the base end side, and the amount of crowning of both end corners of the rollers of each row is different, and the rollers of each of the above examples A universal joint bearing device characterized in that the large crowning side is arranged toward the tip side of the trunnion.
JP62135690A 1987-05-30 1987-05-30 Bearing device for universal joint Granted JPS63303227A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP62135690A JPS63303227A (en) 1987-05-30 1987-05-30 Bearing device for universal joint

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP62135690A JPS63303227A (en) 1987-05-30 1987-05-30 Bearing device for universal joint

Publications (2)

Publication Number Publication Date
JPS63303227A JPS63303227A (en) 1988-12-09
JPH031531B2 true JPH031531B2 (en) 1991-01-10

Family

ID=15157635

Family Applications (1)

Application Number Title Priority Date Filing Date
JP62135690A Granted JPS63303227A (en) 1987-05-30 1987-05-30 Bearing device for universal joint

Country Status (1)

Country Link
JP (1) JPS63303227A (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2016109253A (en) * 2014-12-09 2016-06-20 日本精工株式会社 Rolling bearing

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0312656U (en) * 1989-06-16 1991-02-08
EP1925680A3 (en) 2001-09-26 2008-06-11 NTN Corporation Multi-row thrust roller bearing
JP4121403B2 (en) 2003-03-17 2008-07-23 株式会社ジェイテクト Cross shaft coupling
JP2005180506A (en) * 2003-12-17 2005-07-07 Nsk Ltd Needle bearing and planetary gear mechanism

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS521946U (en) * 1975-06-24 1977-01-08

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4988177U (en) * 1972-11-21 1974-07-31
JPS6193632U (en) * 1984-11-26 1986-06-17

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS521946U (en) * 1975-06-24 1977-01-08

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2016109253A (en) * 2014-12-09 2016-06-20 日本精工株式会社 Rolling bearing

Also Published As

Publication number Publication date
JPS63303227A (en) 1988-12-09

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