JPS6410691B2 - - Google Patents

Info

Publication number
JPS6410691B2
JPS6410691B2 JP57141566A JP14156682A JPS6410691B2 JP S6410691 B2 JPS6410691 B2 JP S6410691B2 JP 57141566 A JP57141566 A JP 57141566A JP 14156682 A JP14156682 A JP 14156682A JP S6410691 B2 JPS6410691 B2 JP S6410691B2
Authority
JP
Japan
Prior art keywords
inner ring
tapered roller
bearing
outer ring
generatrix
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
Application number
JP57141566A
Other languages
Japanese (ja)
Other versions
JPS5934019A (en
Inventor
Koichi Baba
Ichita Horiuchi
Yukio Sato
Katsuzo Sudo
Tetsuo Kajiwara
Hiroshi Araya
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.)
NSK Ltd
Mitsubishi Heavy Industries Ltd
Original Assignee
NSK Ltd
Mitsubishi Heavy Industries Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by NSK Ltd, Mitsubishi Heavy Industries Ltd filed Critical NSK Ltd
Priority to JP57141566A priority Critical patent/JPS5934019A/en
Publication of JPS5934019A publication Critical patent/JPS5934019A/en
Publication of JPS6410691B2 publication Critical patent/JPS6410691B2/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
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • F16C19/545—Systems comprising at least one rolling bearing for radial load in combination with at least one rolling bearing for axial load
    • 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
    • F16C13/00—Rolls, drums, discs, or the like; Bearings or mountings therefor
    • F16C13/02—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
    • 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
    • F16C19/30—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 axial load mainly
    • 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
    • F16C2322/00—Apparatus used in shaping articles
    • F16C2322/12—Rolling apparatus, e.g. rolling stands, rolls

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】 この発明は、複列スラスト円すいころ軸受に関
し、とくに、軸受の内輪の端面がカラーを介して
軸に固定されているスラスト円すいころ軸受にお
いて、内輪および外輪の軌道面の母線の交点と円
すいころのコーンセンターとのうち、少なくとも
軌道面の母線の交点を、軸受の中心軸線からずら
したオフセツト構成とし、さらに円すいころの転
動面と内輪および外輪の軌道面との少なくとも一
方の面の全長にわたり所定の曲率半径をもつクラ
ウニングを施すことにより、内輪の軸方向たわみ
に起因する円すいころの転動接触面におけるエツ
ジロードの発生と発熱とを軽減して、スラスト負
荷能力を大幅に増大させるようにしたものであ
る。Detailed Description of the Invention The present invention relates to a double-row thrust tapered roller bearing, and particularly to a thrust tapered roller bearing in which the end face of the inner ring of the bearing is fixed to the shaft via a collar. Among the intersection points of the generatrix lines and the cone centers of the tapered rollers, at least the intersection point of the generatrix line of the raceway surface is offset from the center axis of the bearing, and at least the intersection point of the raceway surface of the tapered rollers and the raceway surfaces of the inner ring and the outer ring is By applying crowning with a predetermined radius of curvature over the entire length of one surface, the generation of edge load and heat generation on the rolling contact surface of the tapered roller caused by the axial deflection of the inner ring is reduced, and the thrust load capacity is greatly increased. It was designed to increase the number of people.

たとえば、圧延機のロールネツク用のスラスト
軸受としては、小さな容積でスラスト負荷能力が
大きい複列スラスト円すいころ軸受が適している
が、最近の高荷重圧下においては、ロールに発生
するスラスト荷重がきわめて大きくなる。従来の
複列スラスト円すいころ軸受では、このように大
きなスラスト荷重が負荷されると、円すいころの
尾部側の転動面と軌道面との負荷分布が高くなつ
てエツジロードが発生するだけでなく、異常な高
熱が発生して焼付事故が生ずるなど、長期間の使
用に耐えないという欠点があつた。 For example, double-row thrust tapered roller bearings, which have a small volume and large thrust load capacity, are suitable as thrust bearings for roll necks in rolling mills, but in recent high-load rolling operations, the thrust loads generated on the rolls are extremely large. Become. In conventional double-row thrust tapered roller bearings, when such a large thrust load is applied, the load distribution between the raceway surface and the raceway surface on the tail side of the tapered roller becomes high, which not only causes edge load. It had the disadvantage that it could not withstand long-term use, such as the generation of abnormally high heat and seizure accidents.

このような現象が発生する原因を究明するた
め、種々の実験を繰返して調査したところ、内輪
の軸方向のたわみによるものであることが判明し
た。すなわち、エツジロードについては、内輪の
たわみによつて円すいころの尾部側が強く軌道面
と接触するためであり、とくに円すいころのクラ
ウニングの形状が適切でない場合に発生し易いこ
と、発熱については、内輪のたわみによつて内輪
軌道面と外輪軌道面との母線の交点が、軸受の中
心軸線（回転中心）からずれるために、軌道面に
接触する円すいころも変位してそのコーンセンタ
ーが中心軸線からずれて転動することになり、接
触面において回転差によるすべりが発生すること
によるものである。 In order to investigate the cause of this phenomenon, various experiments were repeated and it was found that it was caused by the axial deflection of the inner ring. In other words, edge load is caused by the tail side of the tapered roller coming into strong contact with the raceway surface due to the deflection of the inner ring, and it is particularly likely to occur when the crowning shape of the tapered roller is not appropriate. Due to deflection, the intersection of the generatrix lines of the inner ring raceway surface and the outer ring raceway surface deviates from the center axis (rotation center) of the bearing, which causes the tapered rollers in contact with the raceway surface to also shift, causing their cone centers to deviate from the center axis. This is due to the rotation difference that causes slippage on the contact surfaces.

さらに、内輪の軸方向たわみの原因について検
討したところ、従来の内輪は肉厚が薄く、しかも
内輪の位置決め用のカラーの端面高さが低いため
に、内輪の固定力が不十分となつて自由支持に近
い状態になつていることによるものであるとの結
論に達した。ちなみに、従来の内輪とカラーとの
端面における面圧は30Kg／mm2以上となり、この場
合の内輪の最大たわみ量を、内輪が自由支持され
ているものとして計算した結果、固定支持の場合
の15〜40倍の大きさとなる。 Furthermore, we investigated the causes of axial deflection of the inner ring, and found that because the conventional inner ring has a thin wall thickness and the end face height of the collar for positioning the inner ring is low, the fixing force of the inner ring is insufficient, causing it to flex. We came to the conclusion that this is due to the fact that the situation is close to support. By the way, the conventional surface pressure at the end face of the inner ring and collar is 30Kg/ mm2 or more, and the maximum deflection of the inner ring in this case is calculated assuming that the inner ring is freely supported. ~40 times larger.

この発明は、上記の観点に鑑みてなされたもの
であり、この発明の目的は、内輪の軸方向のたわ
みが生じた場合でも、円すいころと軌道面との転
動接触面におけるエツジロードの発生と発熱とが
抑制されるスラスト円すいころ軸受を提供するこ
とにあり、また、この発明の目的は、大きな負荷
能力を有する複列スラスト円すいころ軸受を提供
することにある。 This invention has been made in view of the above points, and an object of the invention is to prevent the occurrence of edge load on the rolling contact surface between the tapered rollers and the raceway surface even when the inner ring is deflected in the axial direction. It is an object of the present invention to provide a thrust tapered roller bearing that suppresses heat generation, and also to provide a double-row thrust tapered roller bearing that has a large load capacity.

すなわち、この発明は、たとえば図示する圧延
機ロールネツクにおける実施例のように、軸（ロ
ールネツク）１２の肩部１３とカラー４３との
間、もしくはカラー４２，４３相互間に挾んで位
置決め固定され、かつその全体がほぼ均一な肉厚
を有する内輪４１と、該内輪４１を挟むようにし
てハウジング１４，１５に嵌着される２個の外輪
４４との間に、円すいころ４８が保持器を介して
複列に配設され、円すいころ４８の転動面と内輪
４１および外輪４４の軌道面４１ａ，４５との少
なくとも一方にクラウニングが施されているスラ
スト円すいころ軸受４０において、前記内輪４１
および外輪４４の軌道面４１ａ，４５の母線の交
点P2と円すいころ４８のコーンセンターP1との
うち、少なくとも軌道面４１ａ，４５の母線の交
点P2が軸受の中心軸線Ｏ−Ｏからずれており、
しかも前記円すいころ４８の転動面と内輪および
外輪の軌道面との少なくとも一方の面の中間部４
８ｃと頭部側および尾部側の両端部４８ａ，４８
ｂとに、母線が共通の接線を有する曲率半径の異
なるクラウニングが施されている。ことを特徴す
る複列スラスト円すいころ軸受に係る。 That is, the present invention, as in the embodiment of the rolling mill roll neck shown in the figure, is positioned and fixed between the shoulder 13 of the shaft (roll neck) 12 and the collar 43, or between the collars 42 and 43, and Tapered rollers 48 are arranged in double rows through a cage between an inner ring 41 that has a substantially uniform wall thickness throughout, and two outer rings 44 that are fitted into the housings 14 and 15 so as to sandwich the inner ring 41 therebetween. In the thrust tapered roller bearing 40, which is arranged in
Of the intersection P 2 of the generatrix of the raceway surfaces 41a and 45 of the outer ring 44 and the cone center P 1 of the tapered roller 48, at least the intersection P 2 of the generatrix of the raceway surfaces 41a and 45 deviates from the center axis O-O of the bearing. and
Moreover, the intermediate portion 4 of at least one surface between the rolling surface of the tapered roller 48 and the raceway surfaces of the inner ring and the outer ring.
8c and both ends 48a, 48 on the head side and tail side
b are crowned with different radii of curvature, and the generatrix has a common tangent. This invention relates to a double-row thrust tapered roller bearing characterized by:

以下、この発明の実施例について、図面を参照
して説明する。 Embodiments of the present invention will be described below with reference to the drawings.

第１図は、この発明の実施例であり、同図にお
いて、符号１０は圧延機のロール、１２はロール
ネツク、１４，１５はハウジングをそれぞれ示
し、ハウジング１４内においてロールネツク１２
の大径部１２ａがラジアル円すいころ軸受１６に
よつて半径方向に支持されている。ラジアル円す
いころ軸受１６は、２個の複列内輪１７，２個の
単列外輪１８，１個の複列外輪１９，４列の円す
いころ２０とから成る。２１は保持器、２２は外
輪間座、２３は内輪間座である。単列外輪１８は
ハウジング１４に嵌合された押え部材２５と押え
リング２６とによつて軸方向の位置決めがなされ
ている。押え部材２５には２個のシール２８が間
座２９を介して嵌着され、ロール１０の肩部とロ
ールネツク１２の大径部１２ａとに嵌合したフイ
レツトリング３０の外周面にシール２８のリツプ
を摺接させている。また、押え部材２５の軸方向
端部にはシール３１をシール押え３２により嵌着
してフイレツトリング３０に摺接させ、シール押
え３２とロール１０との間にはシール３３が設け
てある。３４は給油穴であり、この給油穴３４か
ら潤滑油を強制循環させる。 FIG. 1 shows an embodiment of the present invention, in which reference numeral 10 indicates a roll of a rolling mill, 12 indicates a roll neck, and 14 and 15 indicate a housing.
The large-diameter portion 12a of is supported in the radial direction by a radial tapered roller bearing 16. The radial tapered roller bearing 16 includes two double-row inner rings 17, two single-row outer rings 18, one double-row outer ring 19, and four rows of tapered rollers 20. 21 is a retainer, 22 is an outer ring spacer, and 23 is an inner ring spacer. The single-row outer ring 18 is positioned in the axial direction by a presser member 25 and a presser ring 26 fitted into the housing 14. Two seals 28 are fitted to the presser member 25 via spacers 29, and the seals 28 are fitted on the outer peripheral surface of a fillet ring 30 fitted to the shoulder of the roll 10 and the large diameter portion 12a of the roll neck 12. The lip is in sliding contact. Further, a seal 31 is fitted onto the axial end of the presser member 25 by a seal presser 32 and slidably contacts the fillet ring 30, and a seal 33 is provided between the seal presser 32 and the roll 10. Reference numeral 34 denotes an oil supply hole through which lubricating oil is forced to circulate.

ロールネツク１２の小径部１２ｂには、この発
明のスラスト円すいころ軸受４０が設けてある。
この軸受は、中間輪４１をロールネツク１２の小
径部１２ｂに嵌合し、その両側端面にカラー４
２，４３を当接させて位置決め固定して内輪と
し、ハウジング１４，１５には、それぞれつば付
外輪４４を嵌合して、外輪４４の軌道面４５と前
記内輪４１の両側端面との間に円すいころ４８を
転動自在に接触させて、ロールネツク１２を軸方
向に支持する複列のスラスト軸受として構成され
ている。５１は円すいころ４８を保持案内する保
持器、５２は外輪４４の位置決め用の間座であ
り、間座５２には通油穴５３を設け、ハウジング
１４の下部には、間座５２の通油穴５３に連通す
る排油穴５５が複数個設けてある。 The small diameter portion 12b of the roll neck 12 is provided with a thrust tapered roller bearing 40 of the present invention.
In this bearing, an intermediate ring 41 is fitted into a small diameter portion 12b of a roll neck 12, and collars 4 are attached to both end surfaces of the intermediate ring 41.
2 and 43 are brought into contact and positioned and fixed to form an inner ring, and outer rings 44 with flanges are fitted into the housings 14 and 15, respectively, so that there is a gap between the raceway surface 45 of the outer ring 44 and both end surfaces of the inner ring 41. It is configured as a double-row thrust bearing that supports the roll neck 12 in the axial direction by bringing the tapered rollers 48 into rolling contact with each other. 51 is a cage that holds and guides the tapered rollers 48; 52 is a spacer for positioning the outer ring 44; the spacer 52 is provided with an oil passage hole 53; A plurality of oil drain holes 55 communicating with the hole 53 are provided.

上記の円すいころ４８の大端面４９と摺接する
外輪４４のつば４６の案内面（つば面）４７は、
球面形状に成形され、円すいころ４８の大端面４
９の曲率半径を外輪４４のつば面４７の曲率半径
に対して70〜85％の範囲に設定して、円すいころ
４８の大端面４９と外輪４４のつば面４７との間
の接触状態が良好になるようにしている。 The guide surface (flange surface) 47 of the collar 46 of the outer ring 44 that comes into sliding contact with the large end surface 49 of the tapered roller 48 is as follows:
The large end surface 4 of the tapered roller 48 is formed into a spherical shape.
The radius of curvature of No. 9 is set in the range of 70% to 85% of the radius of curvature of the flange surface 47 of the outer ring 44, so that the contact state between the large end surface 49 of the tapered roller 48 and the flange surface 47 of the outer ring 44 is good. I'm trying to make it happen.

また、外輪４４には、軌道面４５とつば面４７
との境界部（研削にげ部）に開口する給油穴６０
と尾部側の軌道面４５に開口する給油穴６２と
を、それぞれ背面側から複数個穿設して、これら
の給油穴６０，６２をハウジング１４，１５に設
けた油通路６４にそれぞれ連通させてある。 The outer ring 44 also includes a raceway surface 45 and a collar surface 47.
Oil supply hole 60 that opens at the boundary part (grinding part) with
and a plurality of oil supply holes 62 that open in the raceway surface 45 on the tail side are drilled from the rear side, and these oil supply holes 60, 62 are communicated with oil passages 64 provided in the housings 14, 15, respectively. be.

さらに、ハウジング１５とカラー４３との間に
は、間座６５を介して両側に２個のシール６５を
配設して密封している。 Furthermore, two seals 65 are disposed on both sides with a spacer 65 interposed between the housing 15 and the collar 43 for sealing.

上記のスラスト軸受４０の潤滑は、潤滑油をオ
イルジエツトにしてハウジング１４，１５の油通
路６４を経て外輪４４の給油穴６０，６２から噴
射し、給油穴６０により円すいころ４８の大端面
４９と外輪４４のつば面４７との間のすべり面を
潤滑し、給油穴６２により内輪４１と外輪４４と
の軌道面と円すいころ４８の転動面との間の接触
面を潤滑して軸受内部を循環したのち、間座５２
の通油穴５３を通つてハウジング１４の排油穴５
５から外部に排出される。 The thrust bearing 40 is lubricated by using lubricating oil as an oil jet, which is injected from the oil supply holes 60 and 62 of the outer ring 44 through the oil passages 64 of the housings 14 and 15. It lubricates the sliding surface between the flange surface 47 of 44 and the contact surface between the raceway surfaces of the inner ring 41 and outer ring 44 and the rolling surface of the tapered rollers 48 through the oil supply hole 62, and circulates inside the bearing. After that, Maza 52
The oil drain hole 5 of the housing 14 passes through the oil passage hole 53 of the housing 14.
5 and is discharged to the outside.

而して、上記スラスト軸受４０の内輪４１と外
輪４４との軌道面４１ａ，４５の母線の交点と円
すいころ４８のコーンセンターとには、いわゆる
オフセツト構成が設けてある。すなわち、従来の
軸受においては、第２図ａに示すように、軸受が
無負荷時の状態では、円すいころ４８のコーンセ
ンターP1と内輪４１と外輪４４との軌道面４１
ａ，４５の母線の交点P2とが軸受の中心軸線Ｏ
−Ｏに一致しているが、いま内輪４１が軸方向に
たわんで破線で示す位置に角度θだけ傾き、円す
いころ４８の転動面の母線が外輪４４の軌道面４
５の母線と一致しているものとすると、P2は中
心軸線Ｏ−Ｏから距離ｘだけずれたP′2の位置と
なる。 A so-called offset configuration is provided between the intersection of the generating lines of the raceway surfaces 41a and 45 of the inner ring 41 and outer ring 44 of the thrust bearing 40 and the cone center of the tapered rollers 48. That is, in the conventional bearing, as shown in FIG .
The intersection point P 2 of the generatrix lines a and 45 is the central axis O of the bearing.
-O, but now the inner ring 41 is bent in the axial direction and tilted at an angle θ to the position shown by the broken line, and the generatrix of the rolling surface of the tapered rollers 48 is aligned with the raceway surface 4 of the outer ring 44.
If it is assumed that P 2 coincides with the generatrix of 5, then P 2 will be a position P' 2 shifted by a distance x from the central axis OO.

ｘ＝Ra−lγ／cosβ・tanθ／tan2β＋tanθ ここに、Ra＝円すいころの大端面とコーンセ
ンター間の長さ（P1P3） lγ＝円すいころの転動面の母線長（P3P4） 2β＝円すいころの円すい角度 このようにして、コーンセンターP1と軌道面
母線の交点P2とが中心軸線Ｏ−Ｏからずれる結
果、円すいころ４８の転動面と軌道面との間で差
動すべりが生ずることになる。 x=Ra−lγ/cosβ・tanθ/tan2β+tanθ Where, Ra=Length between the large end face of the tapered roller and the cone center (P 1 P 3 ) lγ=Length of generatrix of the rolling surface of the tapered roller (P 3 P 4 ) 2β = conical angle of tapered rollers In this way, as a result of the intersection point P 2 of the cone center P 1 and the raceway surface generatrix deviating from the central axis O-O, there is a gap between the rolling surface of the tapered rollers 48 and the raceway surface. Differential slip will occur.

そこで、同図ｂに示すように、内輪４１と外輪
４４との軌道面４１ａ，４５の母線の交点P2を
中心軸線Ｏ−Ｏの左側、円すいころ４８のコーン
センターP1を中心軸線Ｏ−Ｏの右側の位置とな
るようにして、内輪４１と外輪４４との軌道面４
１ａ，４５の母線のなす角度ηを円すいころ４８
の円すい角度2βより内輪４１の傾き角度θだけ
小さくして、η＝2β−θとする。 Therefore, as shown in Figure b, the intersection P 2 of the generatrix of the raceway surfaces 41 a and 45 of the inner ring 41 and the outer ring 44 is placed to the left of the center axis O-O, and the cone center P 1 of the tapered roller 48 is placed on the center axis O- The raceway surface 4 of the inner ring 41 and the outer ring 44 is positioned on the right side of O.
The angle η formed by the generating lines of 1a and 45 is the tapered roller 48
The inclination angle θ of the inner ring 41 is made smaller than the cone angle 2β, so that η=2β−θ.

コーンセンターP1と軌道面母線の交点P2との
中心軸線Ｏ−Ｏからの距離をそれぞれS1，S2とす
ると、 S1＝Ra・θ・sin2β S2＝Ra・θ〔cosec(2β-θ)-sin2β〕 ここに、Ra＝P1P3＝P0P3 したがつて、このように設定された軸受の内輪
４１がスラスト荷重を受けて軸方向にたわみ、破
線で示すように角度θだけ傾くと、円すいころ４
８もこれと同一角度だけ傾いて、コーンセンター
P1と軌道面母線の交点P2とは、ともに中心軸線
Ｏ−Ｏ上の点P0に一致するから、荷重時におけ
る内輪４１と外輪４４との軌道面の母線のなす角
度η0は、円すいころ４８の円すい角度2βと等しく
なる。この結果、円すいころ４８の転動面と軌道
面との間に差動すべりが生じないことになる。 Let S 1 and S 2 be the distances between the cone center P 1 and the intersection point P 2 of the raceway surface generatrix from the central axis O- O , respectively, then S 1 = Ra・θ・sin2β S 2 = Ra・θ [cosec(2β -θ)-sin2β] Here, Ra=P 1 P 3 = P 0 P 3 Therefore, the inner ring 41 of the bearing set in this way is subjected to a thrust load and deflects in the axial direction, as shown by the broken line. When tilted by angle θ, tapered roller 4
8 is also tilted by the same angle as this, and the cone center
Since P 1 and the intersection point P 2 of the raceway surface generatrix both coincide with the point P 0 on the central axis O-O, the angle η 0 formed by the raceway surface generatrix of the inner ring 41 and the outer ring 44 under load is: It is equal to the cone angle 2β of the tapered roller 48. As a result, no differential slip occurs between the rolling surface and the raceway surface of the tapered rollers 48.

上記実施例のオフセツトは、軌道面の母線交点
と円すいころのコーンセンターとの双方に設けて
あるが、少なくとも軌道面の母線交点をオフセツ
ト構成とすればよい。 Although the offset in the above embodiment is provided at both the intersection of the generatrix of the raceway surface and the cone center of the tapered roller, it is sufficient that at least the intersection of the generatrix of the raceway surface be offset.

また、上記軸受の円すいころ４８の転動面に
は、第３図に示すようなクラウニングが施されて
いる。円すいころ４８の全有効長をlγ、頭部４８
ａと尾部４８ｂとの長さをそれぞれl1、中間部４
８ｃの長さをl2とすると、中間部４８ｃには曲率
半径R2のクラウニング、頭部４８ａおよび尾部
４８ｂには曲率半径R1のクラウニングをそれぞ
れ施し、中間部４８ｃの母線と頭部４８ａおよび
尾部４８ｂの母線とが、その交点Ａ，Ｂにおいて
共通の接線を有する円弧とする。そして、中間部
４８ｂの長さl2は全有効長lγに対して、l2＝0.7lγ
であり、中間部４８ｃの曲率半径R2は、頭部４
８ａおよび尾部４８ｂの曲率半径R1に対して、
R2≧30R1であるようにする。このように円すい
ころ４８の転動面の全部にクラウニングを施し、
しかも頭部４８ａおよび尾部４８ｂの両端部の曲
率半径R1を中間部４８ｃの曲率半径R2よりも著
しく小さくすることにより、円すいころ４８の転
動面におけるエツジロードの発生を抑制すること
ができる。 Further, the rolling surface of the tapered rollers 48 of the bearing is crowned as shown in FIG. 3. The total effective length of the tapered roller 48 is lγ, and the head 48
The length of a and the tail part 48b is l 1 respectively, and the length of the middle part 4 is
Assuming that the length of 8c is l2 , the intermediate portion 48c is crowned with a radius of curvature R2 , the head 48a and the tail 48b are crowned with a radius of curvature R1 , and the generatrix of the intermediate portion 48c and the head 48a and The generating line of the tail portion 48b is a circular arc having a common tangent at its intersections A and B. The length l 2 of the intermediate portion 48b is l 2 =0.7lγ with respect to the total effective length lγ.
The radius of curvature R 2 of the intermediate portion 48c is
8a and the radius of curvature R 1 of the tail portion 48b,
Ensure that R 2 ≧30R 1 . In this way, the entire rolling surface of the tapered rollers 48 is crowned,
Furthermore, by making the radius of curvature R 1 of both ends of the head portion 48a and the tail portion 48b significantly smaller than the radius of curvature R 2 of the intermediate portion 48c, the occurrence of edge load on the rolling surface of the tapered roller 48 can be suppressed.

上記のクラウニングは、内輪および外輪の軌道
面に施してもよく、また円すいころと内輪および
外輪との双方に施してもよい。 The above crowning may be applied to the raceway surfaces of the inner ring and the outer ring, or may be applied to both the tapered rollers and the inner ring and the outer ring.

さらに、上記軸受においては、内輪４１の軸方
向たわみを抑制するため、内輪４１の肉厚を次の
ように設定している。第４図において、内輪４１
の肉厚をＷ、内輪４１の内周縁から内輪４１の軌
道面４１ａとこれに接触する円すいころ４８の大
端面４９の母線の延長線との交点Ｃに至る半径方
向の長さ（接触上限高さ）をＨとすると、 Ｗ／Ｈ≧0.8 となるようにして、肉厚Ｗを増大させる。Ｗ／Ｈ
の上限値は、軸受部分の組付スペースの許容範囲
によつて制約されるが、1.1程度までとすること
ができる。 Furthermore, in the above bearing, in order to suppress the axial deflection of the inner ring 41, the wall thickness of the inner ring 41 is set as follows. In FIG. 4, the inner ring 41
W is the wall thickness of the inner ring 41, and the radial length from the inner peripheral edge of the inner ring 41 to the intersection C between the raceway surface 41a of the inner ring 41 and the extension line of the generatrix of the large end surface 49 of the tapered roller 48 that contacts this (maximum contact height) Letting H) be H, the wall thickness W is increased so that W/H≧0.8. W/H
The upper limit of is limited by the allowable range of the assembly space of the bearing part, but can be up to about 1.1.

また、内輪４１の内周縁と保持器５１の内周縁
との間の半径方向すき間Hcと前記内輪４１の接
触上限高さＨとの比Hc／Ｈを、 Hc／Ｈ≧0.26 となるようにする。Hc／Ｈの上限値については、
Hcを過度に大きくすると、与えられた接触上限
高さＨに対して円すいころ４８の長さが減少し、
軸受定格荷重の低下を招くことになるので、組付
スペースの許容範囲内で適宜選定する必要がある
が、0.35程度までとすることができる。このよう
にして半径方向すき間Hcを大きくすることによ
り、内輪４１の位置決め用のカラー４２，４３の
端面高さの寸法を大きくして内輪４１の両側端面
に当接させることができる。 Further, the ratio Hc/H of the radial clearance Hc between the inner peripheral edge of the inner ring 41 and the inner peripheral edge of the cage 51 to the upper limit contact height H of the inner ring 41 is set such that Hc/H≧0.26. . Regarding the upper limit of Hc/H,
If Hc is excessively increased, the length of the tapered roller 48 will decrease with respect to the given upper limit contact height H.
Since this will result in a decrease in the bearing load rating, it is necessary to select it appropriately within the allowable range of the assembly space, but it can be up to about 0.35. By increasing the radial clearance Hc in this way, the height of the end surfaces of the collars 42 and 43 for positioning the inner ring 41 can be increased and brought into contact with both end surfaces of the inner ring 41.

上記のように内輪４１とカラー４２，４３との
寸法を設定すると、内輪４１自体の曲げ剛性が増
大するとともに、内輪４１のロールネツク１２ｂ
に対する支持を強固な固定支持とすることができ
るから、内輪４１に大きなスラスト荷重が作用し
ても内輪４１の軸方向たわみを減少させることが
可能となる。ただし、上記の内輪の肉厚を規制す
る構成とカラーの端面高さを規制する構成とは、
必要に応じ省略することができる。 By setting the dimensions of the inner ring 41 and the collars 42, 43 as described above, the bending rigidity of the inner ring 41 itself increases, and the roll neck 12b of the inner ring 41 increases.
Since the support for the inner ring 41 can be a strong fixed support, even if a large thrust load is applied to the inner ring 41, the axial deflection of the inner ring 41 can be reduced. However, the configuration that restricts the wall thickness of the inner ring and the configuration that restricts the end surface height of the collar are as follows.
It can be omitted if necessary.

上記実施例では、内輪４１の両側端面にカラー
４２，４３を当接させて位置決め固定している
が、一方のカラー４２を省略して内輪４１のロー
ルネツク１２ａ側の端面をロールネツク１２ａの
肩部１３に当接させて固定するようにした軸受に
ついても同様に適用することができる。 In the embodiment described above, the collars 42 and 43 are brought into contact with both end surfaces of the inner ring 41 for positioning and fixing, but one collar 42 is omitted and the end surface of the inner ring 41 on the roll neck 12a side is attached to the shoulder 13 of the roll neck 12a. The same can be applied to a bearing that is fixed by being brought into contact with the bearing.

以上、説明したように、この発明のスラスト円
すいころ軸受は、軌道面の母線交点と円すいころ
のコーンセンターとのうち、少なくとも軌道面の
母線交点を軸受の中心軸線からずらしたオフセツ
ト構成としている。したがつて、この発明によれ
ば、内輪が大きなスラスト荷重を受けて軸方向に
たわんだ場合に、軌道面の母線交点と円すいころ
のコーンセンターとが軸受の中心軸線上で一致す
るから、円すいころの差動すべりを回避すること
ができ、円すいころと軌道面との転動接触面にお
けるすべり摩擦による発熱を効果的に抑制するこ
とが可能となる。 As described above, the thrust tapered roller bearing of the present invention has an offset configuration in which at least the intersection of the generatrix of the raceway surface and the cone center of the tapered roller is offset from the central axis of the bearing. Therefore, according to the present invention, when the inner ring receives a large thrust load and bends in the axial direction, the intersection point of the generatrix of the raceway surface and the cone center of the tapered rollers coincide on the central axis of the bearing, so that the inner ring is bent in the axial direction. Differential sliding of the rollers can be avoided, and heat generation due to sliding friction on the rolling contact surface between the tapered roller and the raceway surface can be effectively suppressed.

また、この発明のスラスト円すいころ軸受の円
すいころの転動面と内輪および外輪の軌道面との
少なくとも一方の面に施されるクラウニングは、
従来の２つの曲率半径の異なる面のつながり部分
を別途加工によつてなめらかに接合したものとは
異なり、円すいころの軌道面と内輪および外輪の
軌道面との少なくとも一方の面の中間部と両端部
とは、母線が共通の接線を有する曲率半径の異な
るクラウニングであるから、曲率半径の異なる面
が極めてなめらかなつながりとなり、つながり部
分の局部当たりもなく、クラウニング効果が十二
分に発揮されるとともに、クラウニング加工にお
いてもつながり部分に特別の加工を付加する必要
がなくなる。 Further, the crowning applied to at least one of the rolling surface of the tapered rollers and the raceway surfaces of the inner ring and outer ring of the thrust tapered roller bearing of the present invention,
Unlike the conventional method in which two surfaces with different radii of curvature are connected smoothly by separate processing, the tapered roller raceway surface and the raceway surfaces of the inner ring and outer ring are connected at the middle and both ends of at least one surface. The crowning is a crowning with different radii of curvature where the generatrix has a common tangent line, so the surfaces with different radii of curvature form an extremely smooth connection, and there is no local contact at the connected part, and the crowning effect is fully exerted. At the same time, there is no need to add special processing to the connecting portions in the crowning process.

したがつて、この発明のスラスト円すいころ軸
受は、上記の効果が相まつてスラスト負荷能力が
大幅に増大するから、大きなスラスト荷重が発生
する圧延機のロールネツクに最も好適な軸受とし
て使用することができる。 Therefore, the thrust tapered roller bearing of the present invention can be used as the most suitable bearing for the roll neck of a rolling mill where a large thrust load is generated, since the above-mentioned effects are combined and the thrust load capacity is greatly increased. .

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

第１図は、この発明の実施例を示す縦断側面
図、第２図は、円すいころのコーンセンターと軌
道輪の軌道面母線の交点との位置関係を示し、同
図ａはオフセツトを設けない軸受、同図ｂはオフ
セツトを設けた軸受の断面図、第３図は、この発
明の円すいころの転動面の母線図、第４図は、内
輪とカラーとの関係寸法を示す断面図である。 図中、１２はロールネツク（軸）、１３はロー
ルネツクの肩部、１４，１５はハウジング、４０
はスラスト軸受、４１は内輪、４１ａは内輪の軌
道面、４２，４３はカラー、４４は外輪、４５は
外輪の軌道面、４８は円すいころ、P1は円すい
ころのコーンセンター、P2は内輪と外輪との軌
道面の母線の交点、Ｏ−Ｏは軸受の中心軸線であ
る。 Fig. 1 is a longitudinal sectional side view showing an embodiment of the present invention, Fig. 2 shows the positional relationship between the cone center of the tapered roller and the intersection of the raceway surface generatrix of the raceway ring, and Fig. a shows the case where no offset is provided. Fig. 3 is a generatrix diagram of the rolling surface of the tapered roller of the present invention, and Fig. 4 is a sectional view showing the relative dimensions between the inner ring and the collar. be. In the figure, 12 is the roll neck (shaft), 13 is the shoulder of the roll neck, 14 and 15 are the housing, and 40
is the thrust bearing, 41 is the inner ring, 41a is the raceway surface of the inner ring, 42, 43 are the collars, 44 is the outer ring, 45 is the raceway surface of the outer ring, 48 is the tapered roller, P 1 is the cone center of the tapered roller, P 2 is the inner ring The intersection of the generatrix of the raceway surface with the outer ring, O-O, is the central axis of the bearing.

Claims (1)

【特許請求の範囲】 １ 軸の肩部とカラーとの間、もしくはカラー相
互間に挟んで位置決め固定され、かつその全体が
ほぼ均一な肉厚を有する内輪と、該内輪を挟むよ
うにしてハウジングに嵌着される２個の外輪との
間に、円すいころが保持器を介して複列に配設さ
れ、円すいころの転動面と内輪および外輪の軌道
面との少なくとも一方にクラウニングが施されて
いるスラスト円すいころ軸受において、前記内輪
および外輪の軌道面の母線の交点と円すいころの
コーンセンターとのうち、少なくとも軌道面の母
線の交点が軸受の中心軸線からずれており、しか
も前記円すいころの転動面と内輪および外輪の軌
道面との少なくとも一方の面の中間部と頭部側お
よび尾部側の両端部とに、母線が共通の接線を有
する曲率半径の異なるクラウニングが施されてい
ることを特徴とする複列スラスト円すいころ軸
受。 ２ 円すいころの転動面と内輪および外輪の軌道
面との少なくとも一方の面の中間部の長さが、円
すいころの全有効長の70％であつて、中間部の曲
率半径が両端部の曲率半径の30倍以上である特許
請求の範囲第１項記載の複列スラスト円すいころ
軸受。[Scope of Claims] 1. An inner ring that is positioned and fixed between the shoulder of the shaft and the collar or between the collars and has a substantially uniform wall thickness throughout, and that is fitted into the housing so as to sandwich the inner ring. Tapered rollers are arranged in double rows between the two outer rings to be mounted, via a cage, and crowning is applied to at least one of the rolling surface of the tapered rollers and the raceway surfaces of the inner ring and the outer ring. In a thrust tapered roller bearing, at least the intersection of the generatrix of the raceway surfaces of the inner ring and the outer ring and the cone center of the tapered roller is offset from the central axis of the bearing, and The intermediate portion of at least one surface of the rolling surface and the raceway surfaces of the inner ring and the outer ring, and both ends of the head side and the tail side, are crowned with different radii of curvature and whose generatrix lines have a common tangent line. A double-row thrust tapered roller bearing featuring: 2. The length of the intermediate portion of at least one of the rolling surface of the tapered roller and the raceway surfaces of the inner ring and outer ring is 70% of the total effective length of the tapered roller, and the radius of curvature of the intermediate portion is equal to or greater than that of both ends. The double-row thrust tapered roller bearing according to claim 1, wherein the double-row thrust tapered roller bearing has a radius of curvature 30 times or more.
JP57141566A 1982-08-14 1982-08-14 Multiple-row thrust conical roller bearing Granted JPS5934019A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP57141566A JPS5934019A (en) 1982-08-14 1982-08-14 Multiple-row thrust conical roller bearing

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP57141566A JPS5934019A (en) 1982-08-14 1982-08-14 Multiple-row thrust conical roller bearing

Publications (2)

Publication Number Publication Date
JPS5934019A JPS5934019A (en) 1984-02-24
JPS6410691B2 true JPS6410691B2 (en) 1989-02-22

Family

ID=15294950

Family Applications (1)

Application Number Title Priority Date Filing Date
JP57141566A Granted JPS5934019A (en) 1982-08-14 1982-08-14 Multiple-row thrust conical roller bearing

Country Status (1)

Country Link
JP (1) JPS5934019A (en)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004039845B4 (en) * 2004-08-18 2013-04-11 Schaeffler Technologies AG & Co. KG Tapered roller bearings
JP5040552B2 (en) * 2007-09-21 2012-10-03 株式会社ジェイテクト Rolling bearing device
JP6991823B2 (en) * 2016-12-26 2022-01-13 Ntn株式会社 Track wheels for thrust roller bearings and thrust roller bearings
WO2018123397A1 (en) * 2016-12-26 2018-07-05 Ntn株式会社 Thrust roller bearing and raceway rings for thrust roller bearing
CN106678175A (en) * 2017-03-06 2017-05-17 常熟长城轴承有限公司 Rotary and vertical reciprocating motion integrated composite bearing

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5120347Y2 (en) * 1971-08-02 1976-05-27
JPS528897Y2 (en) * 1972-10-07 1977-02-24

Also Published As

Publication number Publication date
JPS5934019A (en) 1984-02-24

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