JPS58134222A - One row or four row tapered roller bearing - Google Patents

One row or four row tapered roller bearing

Info

Publication number
JPS58134222A
JPS58134222A JP57187651A JP18765182A JPS58134222A JP S58134222 A JPS58134222 A JP S58134222A JP 57187651 A JP57187651 A JP 57187651A JP 18765182 A JP18765182 A JP 18765182A JP S58134222 A JPS58134222 A JP S58134222A
Authority
JP
Japan
Prior art keywords
row
roller
rollers
tapered roller
bearing
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.)
Pending
Application number
JP57187651A
Other languages
Japanese (ja)
Inventor
ハインリヒ・ホ−フマン
ギユンテル・マルクフエルデル
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.)
IHO Holding GmbH and Co KG
Original Assignee
Kugelfischer Georg Schaefer and Co
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 Kugelfischer Georg Schaefer and Co filed Critical Kugelfischer Georg Schaefer and Co
Publication of JPS58134222A publication Critical patent/JPS58134222A/en
Pending legal-status Critical Current

Links

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30Parts of ball or roller bearings
    • F16C33/34Rollers; Needles
    • F16C33/36Rollers; Needles with bearing-surfaces other than cylindrical, e.g. tapered; with grooves in the bearing surfaces
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22Bearings 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
    • F16C19/34Bearings 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 both radial and axial load
    • F16C19/36Bearings 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 both radial and axial load with a single row of rollers
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22Bearings 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
    • F16C19/34Bearings 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 both radial and axial load
    • F16C19/38Bearings 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 both radial and axial load with two or more rows of rollers
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C23/00Bearings for exclusively rotary movement adjustable for aligning or positioning
    • F16C23/06Ball or roller bearings
    • F16C23/08Ball or roller bearings self-adjusting
    • F16C23/082Ball or roller bearings self-adjusting by means of at least one substantially spherical surface
    • F16C23/086Ball or roller bearings self-adjusting by means of at least one substantially spherical surface forming a track for rolling elements
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30Parts of ball or roller bearings
    • F16C33/46Cages for rollers or needles
    • F16C33/4605Details of interaction of cage and race, e.g. retention or centring
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30Parts of ball or roller bearings
    • F16C33/46Cages for rollers or needles
    • F16C33/4617Massive or moulded cages having cage pockets surrounding the rollers, e.g. machined window cages
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2240/00Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40Linear dimensions, e.g. length, radius, thickness, gap
    • F16C2240/50Crowning, e.g. crowning height or crowning radius

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)
  • Spinning Or Twisting Of Yarns (AREA)
  • Massaging Devices (AREA)

Abstract

(57)【要約】本公報は電子出願前の出願データであるた
め要約のデータは記録されません。
(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

【発明の詳細な説明】 本発明は、内レース、外レース、ころおよび保持器から
成り、レースが案内縁を持たない、1列あるいは4列テ
ーパころ軸受に関する。
DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a single-row or four-row tapered roller bearing consisting of an inner race, an outer race, rollers and a cage, the races having no guiding edges.

テーパ円筒ころ軸受は既に一般に知られている。しかし
このテーパ円筒ころ軸受は、ころに作用する軸線方向の
力のために常に案内縁を設けなければならず、この案内
縁が製造および使用の際に最適な解決策にならないとい
う欠点を持っている。すなわち一方ではレースの研削が
困難にされ、他方ではころ端面と縁との間の滑動面にお
いて摩擦が増大して軸受の付加的な温度上昇を起こす。
Tapered cylindrical roller bearings are already generally known. However, these tapered cylindrical roller bearings have the disadvantage that guide edges must always be provided due to the axial forces acting on the rollers, which do not provide an optimal solution during manufacture and use. There is. This means, on the one hand, that the grinding of the races is made more difficult, and on the other hand, the friction increases on the sliding surfaces between the roller end faces and the edges, leading to an additional temperature rise in the bearing.

さて、この軸受を例えば米国特許第1869890号明
細書に示されているような軸受に替えることは容易に推
考し得ることである。球面たる形ころを球面ころ軸受に
使用することにより、縁を設けることはもはや必要でな
いが、シかし走行面のうちの滑動部分が増大する。それ
に加えて、大きく曲げられたころの製造に時間および費
用がかかる。なぜならばいわゆる送り込み研削法で個々
のころしか製造することができないからである。
Now, it is easily conceivable to replace this bearing with a bearing as shown in, for example, US Pat. No. 1,869,890. By using spherical barrel rollers in spherical roller bearings, it is no longer necessary to provide edges, but the sliding portion of the slanted running surface is increased. In addition, manufacturing highly curved rollers is time consuming and expensive. This is because only individual rollers can be manufactured using the so-called infeed grinding method.

したがって本発明の課題は、冒頭に挙げた種類の軸受を
改良して、最も簡単な構成および任意の軸受寸法におい
てできるだけ高い半径方向および軸線方向の荷重負担能
力が小さい滑り摩擦で得られ、個々の部分および特にこ
ろが簡単に製造され得るようにするととである。
It is therefore an object of the present invention to improve bearings of the type mentioned at the outset so that in the simplest construction and in any given bearing size, as high as possible radial and axial load-bearing capacities are obtained with low sliding friction, the individual This allows the parts and especially the rollers to be easily manufactured.

この課題の解決策が特許請求の範囲第1項の+1゜ 特徴部分に記載されている。特許請求の範囲第2項ない
し第5項には特別の構成が示されている。
A solution to this problem is described in the +1° characteristic part of claim 1. Special features are indicated in claims 2 to 5.

ころの直径が少なくとも端面範囲および適当に構成され
た走行面部分において少し小さくなることによって、内
レースの走行面と外レースの走行面との間隔が狭(なる
。それによって転勤方向に対して直角方向−にころの動
きが固定される。ころ軸線方向においてころに作用する
、例えばころの遠心力およびレースの傾斜から成る力成
分が、走行面により吸収される。不利な案内縁はもはや
必要でない。意外なことに、直径が少し小さくなる際一
般に恐れられる、ころが狭(なる走行面間隙にころがり
込むことはない。ころ半径の縮小は、この新しいころを
通常の円筒ころから区別することが殆んどできないほど
僅かでよい。したがってこの新しいころは、例えば通し
送り研削法による簡単な製造に関して利点を持つが、し
かし案内縁が必要でありかつころ端面が研、削されなけ
ればならないことにぴ) よる欠点を持だ女い。任意の大きさの軸受において多く
の細いころを難なく軸受に入れることができるので、テ
ーパころ軸受の高い半径方向および軸線方向の荷重負担
能力が得られる。転動の際の滑り部分は通常のたる形こ
ろの場合より少ない。
Due to the slightly smaller diameter of the rollers, at least in the end face region and in the area of suitably designed running surfaces, the distance between the running surfaces of the inner race and the outer race becomes narrower. The movement of the rollers in the - direction is fixed. Force components acting on the rollers in the direction of the roller axis, consisting, for example, of the centrifugal force of the rollers and of the inclination of the races, are absorbed by the running surfaces. Unfavorable guide edges are no longer necessary. Surprisingly, the rollers do not roll into the narrow running surface gap, which is generally feared when the diameter is slightly reduced.The reduction in roller radius distinguishes this new roller from regular cylindrical rollers. The new rollers therefore have the advantage of being simple to manufacture, for example by through-feed grinding, but they require guide edges and the roller end faces have to be ground and ground. The high radial and axial load-bearing capacity of tapered roller bearings is obtained because many narrow rollers can be fitted into the bearing without difficulty in bearings of any size. The sliding area during movement is smaller than with normal barrel rollers.

好ましい実施例によれば、ころ半径が次第に小さくなる
。この場合、例えば縦断面が少なくともころ端面範囲に
おいて円弧状に曲げられたころ周面を持つころが得られ
る。通し送り研削′法で最も簡単に製造できるのは、全
長にわたって同じ半径で凸面状に曲げられているころで
ある。利点が完全に認められるのは、曲率半径がころの
長さの10倍よ゛り大きいころの場合である。
According to a preferred embodiment, the roller radius becomes progressively smaller. In this case, for example, a roller having a roller circumferential surface whose longitudinal section is curved in an arc at least in the roller end face region is obtained. The rollers that can be most easily manufactured using the through-feed grinding method are rollers that are curved convexly with the same radius over their entire length. The advantages are fully realized for rollers whose radius of curvature is more than ten times the length of the roller.

このようなころを持つ軸受をテーノ(円筒ころ軸受から
区別ヂることは殆んどできない。
Bearings with such rollers can hardly be distinguished from Teno (cylindrical roller bearings).

最大のころ数を持つ軸受の組付けが常に確実に行なうこ
とができるようにするために、特許請求の範囲第5項に
よれば、軸受軸線上に垂直に立つ外レース走行面の半径
が取付は側にお〜・て再び小さくなってはならない。
In order to ensure that a bearing with the maximum number of rollers can always be assembled, according to claim 5, the radius of the outer race running surface that stands perpendicular to the bearing axis is should not become smaller again on the side.

本発明によるテーパころ軸受を1列に構成することがで
きる。しかし同じ利点をもって、Xあるいは0配置によ
る2列の構成も可能である。
Tapered roller bearings according to the invention can be arranged in one row. However, a two-column configuration with an X or zero arrangement is also possible with the same advantages.

この構成では、最大数のころを詰め込もうとす゛る場合
は、組付は上の理由から少な(とも1つのレースだけを
分割すればよい。
With this configuration, if the maximum number of rollers is to be packed, the number of assemblies (at least one race only needs to be divided) for the above reasons.

本発明を図面により以下に詳細に説明する。The invention will be explained in detail below with reference to the drawings.

1列テーパころ軸受は、外レース1、内レース2、保持
器3およびころ4から成る。゛この場合ころ4は、円筒
状の中間部分4′と、両端面部分において直径5が次第
に小さくなる部分4“とを持っている。外レース1およ
び内レース20走行面1/、 2/も対応するように構
成されている。
The single-row tapered roller bearing consists of an outer race 1, an inner race 2, a cage 3, and rollers 4.゛In this case, the rollers 4 have a cylindrical intermediate portion 4' and portions 4'' where the diameter 5 gradually decreases at both end face portions.The outer race 1 and the inner race 20 running surfaces 1/, 2/ also have configured to correspond.

第1図に誇張して示した直径5の縮小の場合は、両方の
軸線方向において外レース1と内レース2との間隔が狭
(なるので、案内縁がないにもかかわらすころ4が軸線
方向にずれるのが防止される。
In the case of a reduction in the diameter 5, which is exaggerated in FIG. This prevents it from shifting in the direction.

第2図による実施例も同じような構成を持っている。こ
の図においては外レース7と内レース8との間に、縮”
小する直径5を持つころ9が設けられており、この直径
の曲率中心11が軸受軸線10をかなり越えた所にあり
、半径12がころ長さ13の10倍より大きい。誇張し
て示した半径12のころの曲線が、対応して曲げられた
走行面と共にころ9の軸線方向の動きを固定する。
The embodiment according to FIG. 2 has a similar construction. In this figure, there is a contraction between the outer race 7 and the inner race 8.
A roller 9 with a decreasing diameter 5 is provided, the center of curvature 11 of which lies well beyond the bearing axis 10, and the radius 12 is greater than ten times the roller length 13. The exaggerated curve of the roller with radius 12, together with the correspondingly curved running surface, fixes the axial movement of the roller 9.

第3図かられかるように、2列軸受も本発明により構成
することができる。“この図においては、第2図による
2つの軸受が0配置で組み立てられている。主要部分は
、両方の内側レース14、形状が第2図のころ9と一致
する両方のころ列15および一体形成の外レース16で
ある。このような構成は、製造上および機能上、例えば
2列円錐ころ軸受にはるかに優る。
As can be seen from FIG. 3, a double row bearing can also be constructed according to the present invention. “In this figure, two bearings according to FIG. 2 are assembled in the 0 configuration. The outer race 16 of the configuration is superior in manufacturing and functionality to, for example, double-row tapered roller bearings.

既に上に述べたように、ころ直径の縮小が誇張して示さ
れているから、第4a図、第4b図および第4c図が追
加されている。第4a図は通常の円筒ころを示し、第4
b図は大きな曲率半径を持つ本発明によるころを示し、
第4C図は通常のたる形ころを示している。比較する。
Figures 4a, 4b and 4c have been added because, as already mentioned above, the reduction in roller diameter is shown in an exaggerated manner. Figure 4a shows a normal cylindrical roller;
Figure b shows a roller according to the invention with a large radius of curvature,
FIG. 4C shows a conventional barrel roller. compare.

と、第4b図によるころが第4C図によるころより第4
a図によるころにはるかに似ていることがわかる。した
がって適当な走行面断面を持つ軸受に第4b図によるこ
ろを組み込むことは、案内縁の欠点なしにテーバ円筒こ
ろ軸受の利点をもたらす。第4C図によるたる形ころに
比べて、第4b図によるころは、一層長く構成できる可
能性は別として、通し送り研削法によりはるかに安価な
製造をもたらす。
and the roller according to Figure 4b is the fourth roller than the roller according to Figure 4C.
It can be seen that it is much more similar to the one shown in Figure a. The incorporation of the roller according to FIG. 4b in a bearing with a suitable running surface section therefore provides the advantages of a Taber cylindrical roller bearing without the disadvantages of a guide edge. Compared to the barrel roller according to FIG. 4C, the roller according to FIG. 4B, apart from the possibility of a longer construction, results in a much cheaper manufacture due to the through-feed grinding method.

それに対してたる形ころはその大きな曲がりのために送
り込み研削法でころを個々賢舊造することができない。
On the other hand, barrel-shaped rollers cannot be individually machined by the infeed grinding method because of their large bends.

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

第1図は、本発明による1列テーパころ軸受の部分横断
面図、第2図は、球面状に曲げられたころを持つ第1図
の変形例の部分横断面図、第3図は、第2図による構成
に似ている軸受の2列軸受の部分横断面図、第4a図な
いし第・4c図は、比較するための公知のころおよび本
発明による第2図のころを示す図である。 1.7−−−外ツー□、2.8−−−内ッーユ、4.9
・・・ころ、5・・・直径、6・・・端面用 第3図
FIG. 1 is a partial cross-sectional view of a single-row tapered roller bearing according to the present invention, FIG. 2 is a partial cross-sectional view of a modification of FIG. 1 with spherically bent rollers, and FIG. Figures 4a to 4c are partial cross-sectional views of a two-row bearing of a bearing similar to the configuration according to Figure 2, showing the known roller and the roller of Figure 2 according to the invention for comparison; be. 1.7---outside □, 2.8---inside u, 4.9
...Roller, 5...Diameter, 6...Fig. 3 for end face

Claims (1)

【特許請求の範囲】 1、内レース、外レース、ころおよび保持器から成り、
レースが案内縁を持たない、1列あるいは4列テーパこ
ろ軸受において、ころ(4゜9)の直径(5)が少なく
ともころ(4,9)・の両端面(6)の範囲でころ中央
より少し小さくなり、外レース(1,7)および内レー
ス(2,8)の走行面がほぼ同じ形状を持っていること
を特徴とする、1列あるいは4列テーパころ軸受。 2、 直径が次第に小さくなることを特徴とする特許請
求の範囲第1項に記載のテーパころ軸受。 3、 直径が、ころ縦断面が円形になるように、小さく
なることを特徴とする特許請求の範囲第1項に記載のテ
ーパころ軸受。 4゜ 円形が、ころ長さく13)の10倍より大きい半
径(12)を持つことを特徴とする特許請求の範囲第3
項に記載のテーパころ軸受。 5、 外レース(1,7)の走行面曲線に接し得るすべ
その接線が一方の側において軸受軸線(10)を切りか
つ極端な場合にこの軸受軸線と平行していることを特徴
とする特許請求の範囲第1項ないし第4項のうち1つに
記載のテーパころ軸受。
[Claims] 1. Consisting of an inner race, an outer race, rollers and a cage,
In single-row or four-row tapered roller bearings in which the race does not have a guide edge, the diameter (5) of the rollers (4°9) is at least within the range of both end faces (6) of the rollers (4, 9) from the center of the roller. A single-row or four-row tapered roller bearing, which is slightly smaller and is characterized in that the running surfaces of the outer races (1, 7) and inner races (2, 8) have approximately the same shape. 2. The tapered roller bearing according to claim 1, wherein the diameter is gradually reduced. 3. The tapered roller bearing according to claim 1, wherein the diameter is reduced so that the longitudinal cross section of the roller is circular. Claim 3, characterized in that the circular shape has a radius (12) greater than 10 times the roller length 13).
Tapered roller bearings described in section. 5. A patent characterized in that all tangents that can touch the running surface curves of the outer races (1, 7) cut the bearing axis (10) on one side and in the extreme case are parallel to this bearing axis. A tapered roller bearing according to any one of claims 1 to 4.
JP57187651A 1981-12-21 1982-10-27 One row or four row tapered roller bearing Pending JPS58134222A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE31506054 1981-12-21
DE3150605A DE3150605C2 (en) 1981-12-21 1981-12-21 Single or double row tapered roller bearing

Publications (1)

Publication Number Publication Date
JPS58134222A true JPS58134222A (en) 1983-08-10

Family

ID=6149310

Family Applications (1)

Application Number Title Priority Date Filing Date
JP57187651A Pending JPS58134222A (en) 1981-12-21 1982-10-27 One row or four row tapered roller bearing

Country Status (6)

Country Link
JP (1) JPS58134222A (en)
DE (1) DE3150605C2 (en)
FR (1) FR2518675A1 (en)
GB (1) GB2112085A (en)
IT (1) IT1153360B (en)
SE (1) SE8206995L (en)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2004092603A1 (en) * 2003-04-16 2004-10-28 Nsk Ltd. Roller bearing for belt-type stepless speed changer
JP2007144434A (en) * 2005-11-24 2007-06-14 Shiroki Corp Punching device
JP2010519473A (en) * 2007-02-23 2010-06-03 ヤコブ、ヴェルナー Roller bearing
JP2015514949A (en) * 2012-04-23 2015-05-21 アクティエボラゲット・エスコーエッフ Toroidal roller bearing
CN106415062A (en) * 2014-01-22 2017-02-15 纳博特斯克有限公司 Gear power transmission device

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DE3524063A1 (en) * 1985-07-05 1987-01-08 Kugelfischer G Schaefer & Co Taper roller bearing with apertured cage
IT1182697B (en) * 1985-11-22 1987-10-05 Riv Officine Di Villar Perosa TAPER ROLLER BEARING PARTICULARLY FOR RAILWAY USE
DE3841629C2 (en) * 1988-12-10 1996-07-11 Skf Gmbh Roller bearings
DE19612589B4 (en) * 1996-03-29 2005-12-22 Skf Gmbh storage
US5850800A (en) * 1997-01-17 1998-12-22 Ihc Gusto Engineering B.V. Bogie wheels with curved contact surfaces
DE19749638A1 (en) * 1997-09-17 1999-04-01 Fag Oem & Handel Ag Roller bearings
IT1308406B1 (en) * 1999-03-04 2001-12-17 Skf Ind Spa CONICAL ROLLER BEARING.
GB2362928C (en) * 2000-05-30 2005-10-21 Nsk Rhp Europe Technology Co Ltd Bearing assemblies incorporating roller bearings
DE102005058152A1 (en) * 2005-12-06 2007-07-05 Schaeffler Kg Cage for roller bearing
DE102005058149A1 (en) * 2005-12-06 2007-07-05 Schaeffler Kg Tapered roller bearings with curved raceways
DE102005058150A1 (en) * 2005-12-06 2007-07-05 Schaeffler Kg Tapered roller bearings
DE102006050940A1 (en) * 2006-10-28 2008-04-30 Schaeffler Kg Roller bearing for use in wheel bearing of motor vehicle, has outer ring defining outer path, and inner and outer paths formed and arranged such that ling body axis is bent towards bearing axis under angle of incidence
DE102011007635B4 (en) * 2011-04-19 2013-05-29 Aktiebolaget Skf Safety concept for a rolling bearing
WO2013162436A1 (en) * 2012-04-23 2013-10-31 Aktiebolaget Skf Bearing arrangement
EP2938879B1 (en) * 2012-08-21 2019-10-23 Aktiebolaget SKF Wind turbine rotor shaft arrangement
CN104565021B (en) * 2013-10-11 2018-04-17 株式会社捷太格特 Taper roll bearing
BR102014026410A2 (en) 2013-11-07 2016-10-04 Skf Ab bearing arrangement for fluid machinery application
EP2871377B1 (en) * 2013-11-07 2017-01-25 Aktiebolaget SKF Bearing unit for fluid machinery application
JP2016095026A (en) 2014-11-13 2016-05-26 アクティエボラゲット・エスコーエッフ Inclination contact type self axis alignment toroidal rolling bearing
CN104565022A (en) * 2014-12-31 2015-04-29 浙江大学 Variable-contact angle tapered roller bearing

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2004092603A1 (en) * 2003-04-16 2004-10-28 Nsk Ltd. Roller bearing for belt-type stepless speed changer
JP2007144434A (en) * 2005-11-24 2007-06-14 Shiroki Corp Punching device
JP2010519473A (en) * 2007-02-23 2010-06-03 ヤコブ、ヴェルナー Roller bearing
JP2015514949A (en) * 2012-04-23 2015-05-21 アクティエボラゲット・エスコーエッフ Toroidal roller bearing
CN106415062A (en) * 2014-01-22 2017-02-15 纳博特斯克有限公司 Gear power transmission device

Also Published As

Publication number Publication date
FR2518675A1 (en) 1983-06-24
SE8206995D0 (en) 1982-12-08
GB2112085A (en) 1983-07-13
IT1153360B (en) 1987-01-14
DE3150605A1 (en) 1983-07-14
IT8224604A1 (en) 1984-06-03
FR2518675B3 (en) 1985-01-25
IT8224604A0 (en) 1982-12-03
SE8206995L (en) 1983-06-22
DE3150605C2 (en) 1985-01-24

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