JP3025594B2 - Four-row tapered roller bearing - Google Patents
Four-row tapered roller bearingInfo
- Publication number
- JP3025594B2 JP3025594B2 JP4354859A JP35485992A JP3025594B2 JP 3025594 B2 JP3025594 B2 JP 3025594B2 JP 4354859 A JP4354859 A JP 4354859A JP 35485992 A JP35485992 A JP 35485992A JP 3025594 B2 JP3025594 B2 JP 3025594B2
- Authority
- JP
- Japan
- Prior art keywords
- row
- outer ring
- ring
- 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.)
- Expired - Lifetime
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
- F16C19/34—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 both radial and axial load
- F16C19/38—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 both radial and axial load with two or more rows of rollers
- F16C19/383—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 both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
- F16C19/385—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 both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered 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
- 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
- F16C19/54—Systems consisting of a plurality of bearings with rolling friction
- F16C19/541—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing
-
- 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
- F16C19/541—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing
- F16C19/542—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing with two rolling bearings with angular contact
-
- 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
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/66—Special parts or details in view of lubrication
- F16C33/6603—Special parts or details in view of lubrication with grease as lubricant
- F16C33/6607—Retaining the grease in or near the bearing
- F16C33/6614—Retaining the grease in or near the bearing in recesses or cavities provided in retainers, races or rolling elements
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rolling Contact Bearings (AREA)
Description
【0001】[0001]
【産業上の利用分野】本発明は、軸方向多分割構造の内
輪と外輪および内外輪間に配置された円錐ころを有し、
特に内側ころ列がO形配列で、隣接する外側ころ列がX
形配列で内輪の案内軌道と外輪の案内軌道との間に配置
されている四列円錐ころ軸受に関する。なおここでX形
配列とは、両ころ列の円錐ころの作用線が軸受中央軸線
に対して収斂した、いわゆる正面組合せ形式の配列を意
味し、O形配列とは、両ころ列の円錐ころの作用線が軸
受中央軸線に対して離散した、いわゆる背面組合せ形式
の配列を意味する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention has a tapered roller disposed between an inner ring, an outer ring, and an inner and outer ring of an axially multi-split structure,
In particular, the inner roller row is an O-shaped array and the adjacent outer roller row is X
The present invention relates to a four-row tapered roller bearing arranged between a guideway of an inner ring and a guideway of an outer ring in a shape arrangement. Here, the X-shaped arrangement means an arrangement of a so-called front combination type in which the action lines of the tapered rollers in the double roller row converge with respect to the center axis of the bearing, and the O-shaped arrangement means the tapered rollers in the double roller row. Of the so-called back-to-back combination type, in which the action lines are discrete with respect to the center axis of the bearing.
【0002】[0002]
【従来の技術】かかる円錐ころ軸受は既に公知である。
しかし、例えばドイツ連邦共和国特許出願公開第361
5343号公報に示されているように、常に内輪同士そ
して外輪同士は環状のスペーサによって互いに分離して
配置されている。かかる構造は、ころ組立体を有する内
輪が、軸受リング(軌道輪)の整合および軸受隙間の調
整のために個々の軸受部品を損傷することなしには分解
できないために必要である。ころ組立体を有する内輪の
互いに向かい合う端面が再研磨される際、その研磨粉末
が軸受部品間に入り込み、これにより軸受は運転中に早
期に損傷してしまう。これを避けるために、公知の軸受
の場合には、軸受リングを整合する際に、環状スペーサ
の側面だけが別個に研磨される。この公知の軸受は、特
別に加工されねばならない沢山の部品から成ってしまう
という欠点、および正確に合わされた環状スペーサと軸
受リングは軸受を組み立てる際に容易に取り違えられ、
環状スペーサによって調整された軸受隙間が組立後に最
適でなくなるという欠点がある。2. Description of the Related Art Such tapered roller bearings are already known.
However, for example, German Patent Application Publication No. 361
As disclosed in Japanese Patent No. 5343, the inner rings and the outer rings are always separated from each other by annular spacers. Such a configuration is necessary because the inner race with the roller assembly cannot be disassembled without damaging the individual bearing components for alignment of the bearing rings and adjustment of the bearing clearance. As the opposing end faces of the inner race with the roller assembly are reground, the abrasive powder enters between the bearing components, causing premature damage to the bearing during operation. To avoid this, in the case of known bearings, only the side faces of the annular spacer are separately ground when the bearing rings are aligned. The disadvantage of this known bearing is that it consists of many parts that have to be specially machined, and the precisely matched annular spacers and bearing rings are easily interchanged when assembling the bearing,
The disadvantage is that the bearing clearance adjusted by the annular spacer is not optimal after assembly.
【0003】[0003]
【発明が解決しようとする課題】本発明の目的は、冒頭
に述べた形式の四列円錐ころ軸受を、公知のものよりも
少数の部品から成り、予調整された軸受隙間が軸受を組
み立てた際にほとんど変化しないように形成することに
ある。SUMMARY OF THE INVENTION It is an object of the present invention to provide a four-row tapered roller bearing of the type mentioned at the outset consisting of a smaller number of parts than is known, with a pre-adjusted bearing gap having assembled the bearing. In this case, it is formed so that it hardly changes.
【0004】[0004]
【課題を解決するための手段】本発明によればこの目的
は、各ころ列に対して別々の外輪が設けられ、互いに隣
接する外側ころ列と内側ころ列に対して共通の内輪が設
けられ、内側外輪および内輪がそれぞれ互いに向かい合
う端面で直接接触し、内側外輪の互いに反対側に位置す
る端面が外側外輪の端面に直接接触して配置されている
ことによって達成される。In accordance with the invention, it is an object of the invention to provide a separate outer race for each roller row and a common inner race for adjacent outer and inner roller rows. This is achieved by the inner outer ring and the inner ring being in direct contact with each other at the end faces facing each other, and the opposite end faces of the inner outer ring being disposed in direct contact with the end faces of the outer outer ring.
【0005】本発明に基づく形態によれば、個々の軸受
リング間に環状スペーサを入れる必要はなくなる。軸受
リングの整合前および軸受隙間の調整前に、内輪は仕上
げ研磨でき、ころ組立体と共に1つのユニットの形に結
合できる。軸受リングの整合および例えば内側ころ列と
対応した軸受リングの案内軌道との間における軸受隙間
の調整に対して、最終組立済みのころ組立体をもった内
輪が損傷されることなしに、内側外輪部分の互いに向か
い合う端面が相応して研磨できる。これによって内輪に
ついて測定した軸受の狭い幅での公差が厳守されるの
で、軸受を軸方向に固定するための高価な組立部品、例
えばねじ付きリングおよびナットは不要となる。したが
って非常に安価に製造でき困難なしに据えつけられる軸
受が作られる。[0005] According to the configuration according to the invention, it is no longer necessary to insert an annular spacer between the individual bearing rings. Before alignment of the bearing rings and adjustment of the bearing clearance, the inner race can be finished polished and combined with the roller assembly in one unit. Due to the alignment of the bearing rings and, for example, the adjustment of the bearing gap between the inner roller rows and the corresponding raceways of the bearing rings, the inner ring with the final assembled roller assembly is not damaged without the inner ring being damaged. The mutually facing end faces of the part can be polished accordingly. This eliminates the need for expensive assemblies, such as threaded rings and nuts, for axially fixing the bearing, since tight bearing tolerances, measured on the inner ring, are maintained. A bearing is thus produced which is very inexpensive to manufacture and which can be installed without difficulty.
【0006】本発明の有利な実施態様が特許請求の範囲
の各請求項に記載されている。[0006] Advantageous embodiments of the invention are specified in the claims.
【0007】[0007]
【実施例】以下図に示した実施例を参照して本発明を詳
細に説明する。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be described in detail below with reference to the embodiments shown in the drawings.
【0008】四列円錐ころ軸受は圧延機、特に冷間およ
び熱間ストリップ圧延ラインに対する転がり軸受として
適しており、2つの内輪1,2、4つの外輪3,4,
5,6および転動体(円錐ころ)から成っている。各こ
ろ列8a,8b,8c,8dの円錐ころ7は保持器9内
に保持され案内されている。内側(軸方向にて内側)こ
ろ列8b,8cは内輪1,2の案内軌道10b,10c
と内側外輪部分4,5の案内軌道11b,11cとの間
にO形配列で配置され、外側(軸方向にて外側)ころ列
8a,8dはそれぞれ隣りの内側ころ列8b,8cとX
形配列をなして、内輪1,2の案内軌道10a,10
b,10c,10dと外輪部分3,4,5,6の案内軌
道11a,11b,11c,11dとの間に配置されて
いる。それぞれの軸受部品は必要に応じて交換できるよ
うになっている。内輪1,2について測定した軸受の幅
公差は±0.25mmより小さい。内側外輪4,5は互い
に向かい合う端面12,13で互いに直接接触し、内側
外輪4,5の互いに反対側に位置する端面14,15a
は外側外輪3,6の端面14a,15に直接接触してい
る。The four-row tapered roller bearing is suitable as a rolling bearing for rolling mills, especially for cold and hot strip rolling lines, and has two inner rings 1,2 and four outer rings 3,4.
5, 6 and rolling elements (conical rollers). The tapered rollers 7 of each roller row 8a, 8b, 8c, 8d are held and guided in a holder 9. Inner (in the axial direction) roller rows 8b and 8c are guide tracks 10b and 10c of the inner rings 1 and 2, respectively.
And the guide tracks 11b and 11c of the inner outer ring portions 4 and 5 are arranged in an O-shape arrangement, and the outer (axially outer) roller rows 8a and 8d are respectively adjacent to the inner roller rows 8b and 8c and X
The guide tracks 10a, 10
b, 10c, 10d and the guide tracks 11a, 11b, 11c, 11d of the outer ring portions 3, 4, 5, 6 are arranged. Each bearing component can be replaced as needed. The width tolerance of the bearing measured for the inner rings 1 and 2 is smaller than ± 0.25 mm. The inner outer rings 4 and 5 are in direct contact with each other at end faces 12 and 13 facing each other, and end faces 14 and 15a located on the opposite sides of the inner outer rings 4 and 5.
Are in direct contact with the end surfaces 14a, 15 of the outer outer rings 3, 6.
【0009】このために内側外輪4,5および外側外輪
3,6ならびに内輪1,2は互いに向かい合う端面に、
案内軌道10b,10c,11a,11b,11c,1
1dより軸方向に突出している延長部16,16a,1
7,17aを備えている。内輪1,2は互いに向かい合
う端面18,19で同様に直接に接触している。外輪
3,4,5,6は外周面20の非荷重範囲に段差部21
を備えている。内側外輪4,5は両側端面に、軸受の通
気ないし潤滑のために使用する円周に分布して配置され
半径方向に延びる複数の切欠き22を備えている。さら
にこれらの切欠き22は互いに向かい合う側の内周面に
大きな傾斜部23を備えており、これにより軸受に補助
的なグリース貯蔵部が形成されている。For this purpose, the inner outer rings 4, 5 and the outer outer rings 3, 6 and the inner rings 1, 2 are provided with end faces facing each other.
Guide tracks 10b, 10c, 11a, 11b, 11c, 1
Extensions 16, 16a, 1 projecting axially from 1d
7, 17a. The inner rings 1, 2 are also in direct contact at the end faces 18, 19 facing each other. The outer races 3, 4, 5, and 6 have stepped portions 21 in the non-load range of the outer peripheral surface 20.
It has. The inner outer races 4, 5 are provided at their two end faces with a plurality of radially extending cutouts 22 which are arranged on the circumference used for ventilation or lubrication of the bearing. Furthermore, these cutouts 22 are provided with a large inclined part 23 on the inner peripheral surface on the side facing each other, so that an auxiliary grease storage part is formed in the bearing.
【0010】内輪1,2は内周面において端面18,1
9,25,26から発した傾斜部24を有し、これらの
傾斜部24によって、全体が閉鎖的に構成されている場
合にその構成部材を交換をするときに組立が容易にな
る。さらに内輪1,2は端面18,19,25,26に
円周に分布して配置された複数の潤滑溝27を備え、円
筒状の内周面に潤滑グリースおよび摩耗粒子を収容する
ためのスパイラル状溝29を有している。The inner rings 1 and 2 have end faces 18 and 1 on the inner peripheral surface.
It has ramps 24 emanating from 9, 25, 26, which facilitate assembly when replacing its components when the whole is constructed closed. Further, the inner rings 1 and 2 are provided with a plurality of lubrication grooves 27 distributed circumferentially on the end faces 18, 19, 25 and 26, and a spiral for accommodating lubricating grease and wear particles on a cylindrical inner peripheral face. It has a groove 29.
【0011】本発明は図示した実施例に限定されるもの
ではなく、個々の構造部品の構造は本発明の範囲内にお
いて簡単に変更できる。The invention is not limited to the embodiment shown, but the structure of the individual structural parts can easily be changed within the scope of the invention.
【0012】[0012]
【発明の効果】本発明によれば、部品点数が少なく、安
価に簡単に製造できる四列円錐ころ軸受が得られる。According to the present invention, a four-row tapered roller bearing having a small number of components, which can be easily manufactured at low cost can be obtained.
【図1】本発明に基づく四列円錐ころ軸受の断面図。FIG. 1 is a sectional view of a four-row tapered roller bearing according to the present invention.
1,2 内輪 3〜6 外輪 8a〜8d ころ列 14,14a 端面 15,15a 端面 16,16a 延長部 17,17a 延長部 18,19 端面 23,24 傾斜部 25,26 端面 1, 2 Inner ring 3-6 Outer ring 8a-8d Roller row 14, 14a End face 15, 15a End face 16, 16a Extension 17, 17a Extension 18, 18, End face 23, 24 Inclined section 25, 26 End face
───────────────────────────────────────────────────── フロントページの続き (72)発明者 ローター マイドル ドイツ連邦共和国、 8720 シュバイン フルト、 ゲルダーシャイマー シュト ラッセ 86 (56)参考文献 特開 昭61−171917(JP,A) 実開 昭63−180102(JP,U) (58)調査した分野(Int.Cl.7,DB名) F16C 19/38 F16C 33/58 ──────────────────────────────────────────────────続 き Continuation of the front page (72) Inventor Rotor Middle 8720 Schweinfurt, Gelderscheimer straße 86 (56) References JP-A-61-171917 (JP, A) Japanese Utility Model 63-180102 (JP, U) (58) Field surveyed (Int. Cl. 7 , DB name) F16C 19/38 F16C 33/58
Claims (6)
外輪間に配置された円錐ころを有し、特に内側ころ列が
O形配列で、隣接する外側ころ列がX形配列で内輪の案
内軌道と外輪の案内軌道との間に配置されている四列円
錐ころ軸受において、 各ころ列(8a,8b,8c,8d)に対して別々の外
輪(3,4,5,6)が設けられ、互いに隣接する外側
ころ列と内側ころ列に対して共通の内輪(1,2)が設
けられ、内側外輪(4,5)および内輪(1,2)がそ
れぞれ互いに向かい合う端面(12,13,18,1
9)で直接接触し、内側外輪(4,5)の互いに反対側
に位置する端面(14,15a)が外側外輪(3,6)
の端面(14a,15)に直接接触して配置されている
ことを特徴とする四列円錐ころ軸受。1. An axially multi-segmented inner ring having tapered rollers disposed between an outer ring and an inner and outer ring, particularly an inner roller row having an O-shaped arrangement, an adjacent outer roller row having an X-shaped arrangement, and an inner ring having an X-shaped arrangement. In a four-row tapered roller bearing arranged between the guide track and the outer ring guide track, a separate outer ring (3, 4, 5, 6) is provided for each roller row (8a, 8b, 8c, 8d). A common inner ring (1,2) is provided for the outer roller row and the inner roller row adjacent to each other, and the inner outer ring (4,5) and the inner ring (1,2) face each other. 13,18,1
9), the end faces (14, 15a) located on opposite sides of the inner outer ring (4, 5) are connected to the outer outer ring (3, 6).
Characterized in that they are arranged in direct contact with the end faces (14a, 15) of the four-row tapered roller bearing.
8,19)が、案内軌道(10b,10c,11a,1
1b,11c,11d)より軸方向に突出している内側
内輪(1,2)および外輪(3,4,5,6)の軸方向
延長部(16,16a,17,17a)に形成されてい
ることとする請求項1に記載の四列円錐ころ軸受。2. An end face (14, 14a, 15, 15a, 1
8, 19) are the guide tracks (10b, 10c, 11a, 1).
1b, 11c, 11d) are formed at axially extending portions (16, 16a, 17, 17a) of the inner inner ring (1, 2) and the outer ring (3, 4, 5, 6) projecting in the axial direction. The four-row tapered roller bearing according to claim 1.
側に内周面に大きな傾斜部(23)を備えていることと
する請求項1又は請求項2に記載の四列円錐ころ軸受。3. The four-row tapered roller bearing according to claim 1, wherein the inner outer ring (4, 5) has a large inclined portion (23) on the inner peripheral surface on the side facing each other.
19,25,26)から発した傾斜部(24)を有して
いることとする請求項1ないし請求項3のいずれか1つ
に記載の四列円錐ころ軸受。4. An inner ring (1, 2) having an end face (18,
The four-row tapered roller bearing according to any one of claims 1 to 3, wherein the bearing has an inclined portion (24) emanating from each of (19, 25, 26).
換可能に作られていることを特徴とする請求項1ないし
請求項4のいずれか1つに記載の四列円錐ころ軸受。5. The four-row tapered roller bearing according to claim 1, wherein all bearing parts are made interchangeable according to the position of the seat.
幅公差が±0.25mmより小さいこととする請求項1な
いし請求項5のいずれか1つに記載の四列円錐ころ軸
受。6. The four-row tapered roller bearing according to claim 1, wherein a width tolerance of the bearing measured for the inner ring (1, 2) is smaller than ± 0.25 mm.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE4142802A DE4142802A1 (en) | 1991-12-23 | 1991-12-23 | FOUR ROW BEARING BEARING |
DE4142802.1 | 1991-12-23 |
Publications (2)
Publication Number | Publication Date |
---|---|
JPH05248430A JPH05248430A (en) | 1993-09-24 |
JP3025594B2 true JP3025594B2 (en) | 2000-03-27 |
Family
ID=6448039
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP4354859A Expired - Lifetime JP3025594B2 (en) | 1991-12-23 | 1992-12-18 | Four-row tapered roller bearing |
Country Status (5)
Country | Link |
---|---|
JP (1) | JP3025594B2 (en) |
CN (1) | CN1038869C (en) |
DE (1) | DE4142802A1 (en) |
FR (1) | FR2685410B1 (en) |
GB (1) | GB2262785B (en) |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5462367A (en) * | 1994-08-18 | 1995-10-31 | The Timken Company | Compact bearing and stiffened journal |
DE29704386U1 (en) * | 1997-03-11 | 1997-04-24 | Skf Gmbh | Four-row tapered roller bearing, especially for work rolls on roll stands |
DE102005022205A1 (en) * | 2005-05-13 | 2006-11-16 | Schaeffler Kg | Four row tapered roller bearing |
JP5315847B2 (en) | 2007-08-09 | 2013-10-16 | 株式会社ジェイテクト | Roller bearing |
CN102829076A (en) * | 2011-06-14 | 2012-12-19 | 瓦房店正达冶金轧机轴承有限公司 | Sealed four-row cylinder bearing |
DE102012203803A1 (en) * | 2012-03-12 | 2013-09-12 | Schaeffler Technologies AG & Co. KG | Rolling bearing with split bearing ring unit |
Family Cites Families (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CH56202A (en) * | 1912-06-01 | 1912-10-16 | Weibel Mulisch Margareta | Ball bearings for radial and axial pressure |
US1144484A (en) * | 1915-02-19 | 1915-06-29 | Hyatt Roller Bearing Co | Roller-bearing with thrust-collar. |
US1283713A (en) * | 1916-07-27 | 1918-11-05 | Skf Svenska Kullagerfab Ab | Roller-bearing. |
US1961134A (en) * | 1932-09-06 | 1934-06-05 | Timken Roller Bearing Co | Antifriction bearing |
US1971782A (en) * | 1933-09-30 | 1934-08-28 | Karl L Herrmann | Roller bearing |
GB724535A (en) * | 1953-01-02 | 1955-02-23 | British Timken Ltd | Improvements relating to roller bearings |
US3958847A (en) * | 1975-01-31 | 1976-05-25 | Tribotech | Bearing assembly |
CN85108036B (en) * | 1985-05-06 | 1988-08-17 | 托林顿公司 | Multirow roller bearing |
DE3542265A1 (en) * | 1985-11-29 | 1987-06-04 | Skf Gmbh | Support of a horizontal roll |
DE3607729C3 (en) * | 1986-03-08 | 1995-06-29 | Skf Gmbh | Rolling bearing, for work rolls in high-speed rolling mills |
DE3622299A1 (en) * | 1986-07-03 | 1988-01-07 | Kugelfischer G Schaefer & Co | Shaft bearing arrangement |
-
1991
- 1991-12-23 DE DE4142802A patent/DE4142802A1/en not_active Ceased
-
1992
- 1992-12-18 JP JP4354859A patent/JP3025594B2/en not_active Expired - Lifetime
- 1992-12-22 FR FR9215525A patent/FR2685410B1/en not_active Expired - Fee Related
- 1992-12-22 GB GB9226672A patent/GB2262785B/en not_active Expired - Fee Related
- 1992-12-23 CN CN92114851A patent/CN1038869C/en not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
---|---|
DE4142802A1 (en) | 1993-07-01 |
FR2685410A1 (en) | 1993-06-25 |
GB9226672D0 (en) | 1993-02-17 |
JPH05248430A (en) | 1993-09-24 |
GB2262785B (en) | 1995-06-21 |
CN1038869C (en) | 1998-06-24 |
CN1074983A (en) | 1993-08-04 |
FR2685410B1 (en) | 1996-08-02 |
GB2262785A (en) | 1993-06-30 |
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