JPS60188617A - Roller bearing capable of standing both radial and thrust loads - Google Patents
Roller bearing capable of standing both radial and thrust loadsInfo
- Publication number
- JPS60188617A JPS60188617A JP59042120A JP4212084A JPS60188617A JP S60188617 A JPS60188617 A JP S60188617A JP 59042120 A JP59042120 A JP 59042120A JP 4212084 A JP4212084 A JP 4212084A JP S60188617 A JPS60188617 A JP S60188617A
- Authority
- JP
- Japan
- Prior art keywords
- inner ring
- rollers
- ring
- center
- outer ring
- 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
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
- F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
- F16C23/06—Ball or roller bearings
- F16C23/08—Ball or roller bearings self-adjusting
- F16C23/082—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface
- F16C23/086—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface forming a track for rolling elements
-
- 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
- F16C19/26—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 a single row 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
- F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
- F16C23/06—Ball or roller bearings
- F16C23/08—Ball or roller bearings self-adjusting
- F16C23/082—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface
- F16C23/084—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface sliding on a complementary spherical surface
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Support Of The Bearing (AREA)
Abstract
Description
【発明の詳細な説明】
本発明はラジアル及びスラスト両荷重を受けることがで
きるころがり軸受に関するものである０
従来技術においては、撓みを有する軸を支持する場合、
第１図に示すような角度調整機能を有する自動調芯軸受
が多く利用されていた。この軸受け、軸／に固定する内
輪コの外表面を円弧状の凸面状に形成し、外輪３の内表
面を円弧状の凹面状に形成し、内外輪コ、３間に外表面
が円弧状をした多数のコログ＋ −−−＋ ５ ＋ −
ｍ−をコ列に配置し、両側のコログ、左を間隔保持器乙
により一定間隔に保持されている。尚、図中７はハウジ
ング、ざはハウジング７に固定した外輪３を保持したエ
ンドプレートである。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a rolling bearing capable of receiving both radial and thrust loads. In the prior art, when supporting a shaft with deflection,
Self-aligning bearings with an angle adjustment function as shown in FIG. 1 have been widely used. In this bearing, the outer surface of the inner ring fixed to the shaft is formed into a convex arc shape, the inner surface of the outer ring 3 is formed into a concave arc shape, and the outer surface between the inner and outer rings 3 is formed into an arc shape. A large number of Korogs + −−−+ 5 + −
M- are arranged in a row, and held at constant intervals by Korok on both sides and a spacer O on the left. In the figure, 7 is a housing, and 7 is an end plate that holds the outer ring 3 fixed to the housing 7.
前記従来の軸受け、外輪３内面の調芯方向の曲率半径は
外輪３の内径と同一でなければならない。したがって、
このような自動調芯軸受にスラスト方向の荷重が作用し
た場合、外輪の負荷を支持する有効断面積は、第２図（
イ）に示１ようにコログの両端を結ぶ領域Ｘ内である。In the conventional bearing, the radius of curvature of the inner surface of the outer ring 3 in the alignment direction must be the same as the inner diameter of the outer ring 3. therefore,
When a load in the thrust direction is applied to such a self-aligning bearing, the effective cross-sectional area that supports the load on the outer ring is shown in Figure 2 (
B) As shown in 1, it is within the region X that connects both ends of the corrog.
それ故、軸受の大きさによって一義的に決まってしまう
。この領域又は一般的に少さく、自動調芯軸受はスラス
ト荷重には非常に弱いとされており、第２図（ロ）にｙ
で示すように外輪３の端部が割れを生じるという欠点が
あった。Therefore, it is determined primarily by the size of the bearing. In this region or generally less, self-aligning bearings are said to be extremely weak against thrust loads, and Fig. 2 (b) shows y
As shown in the figure, there was a drawback in that the end of the outer ring 3 was cracked.
特に、連続鋳造機のように錯綜する機器配列にある軸受
の入るスペースが非常に限定されている上に、スラスト
荷重が大きい場合には、第第３図に示す球面座付円筒コ
ロ軸受が使用されている。In particular, when the space for a bearing in a complex equipment arrangement such as a continuous casting machine is extremely limited and the thrust load is large, a cylindrical roller bearing with a spherical seat as shown in Figure 3 is used. has been done.
第３図に示す従来の球面座付円筒コロ軸受は、内輪コの
外表面を直線状に形成してコログを円筒状に形成し、と
のコログを内表面に設けた嵌合溝りに嵌合した球面座／
θの外表面を断面円弧状の凸状面で形成し、この球面座
１０を、内表面が中芯から片側輪重でを断面円弧状に形
成した外輪３に嵌合している。In the conventional cylindrical roller bearing with a spherical seat shown in Fig. 3, the outer surface of the inner ring is formed linearly, the rollers are formed into a cylindrical shape, and the rollers are fitted into fitting grooves provided on the inner surface. Combined spherical seat/
The outer surface of θ is formed as a convex surface with an arcuate cross section, and this spherical seat 10 is fitted into an outer ring 3 whose inner surface is formed with an arcuate cross section from the center center to one side of the wheel load.
この球面座付円筒コロ軸受は、内輪１とコログとの間で
滑るだめ位置固定ができないという問題がある。This cylindrical roller bearing with a spherical seat has a problem in that the inner ring 1 and the rollers do not slip and cannot be fixed in position.
そこで、本発明においては限定されたスペースでラジア
ル荷重とスラスト荷重を同時に受けることができ、しか
も自動調芯機能を壱するラジアル及びスラスト両荷重を
受けることができるころがり軸受を提供するのが目的で
ある。Therefore, an object of the present invention is to provide a rolling bearing that can receive both radial and thrust loads in a limited space and that also has a self-aligning function. be.
本発明の構成を第７図及び第５図に示す実施例に基き詳
細に説明すると、軸／に内側を固定する内輪２′の外表
面コ“を、軸／の半径方向の中心（０）を曲率中心とす
る断面を円弧状の凸面に形成する。この内輪２′に対向
する外輪３′は内輪２１よりも幅を狭く形成し、内表面
３“を内輪２′の内表面２“と対向する位置を曲率中心
とする同一曲率を持った断面を円弧状の凸面に形成する
。そして、内外輪、２／ 、 ３／間には多数の鼓形コ
ロク′。The structure of the present invention will be explained in detail based on the embodiment shown in FIGS. 7 and 5. The cross section with the center of curvature at A cross section with the same curvature with the center of curvature at the opposing position is formed into an arc-shaped convex surface.A large number of drum-shaped rollers' are formed between the inner and outer rings, 2/ and 3/.
−−−１５’ｌ −−一が軸受の中心に対し、左右対称
に２列配列され、両側の各コロ＜ｔｌ、 ｓｌは夫々間
隔保持器乙により従来と同様に一定間隔に保持されてい
る。---15'l ---1 are arranged in two rows symmetrically with respect to the center of the bearing, and the rollers on both sides (tl, sl) are each held at a constant interval by a spacing retainer (b), as in the past. .
各鼓形コログ′、３′はその外円筒面の曲率半径を内輪
２′の外表面２′の曲率半径よりも大きく形成する。こ
の曲率半径を適当に定めることにより鼓形コロｙ ／
、 ｓ ／の走行軌跡（外輪上でコロが接触しながら通
過していく範囲）の幅を自由に設計することができる。The radius of curvature of the outer cylindrical surface of each of the hourglass-shaped corrugations', 3' is larger than the radius of curvature of the outer surface 2' of the inner ring 2'. By appropriately determining this radius of curvature, the drum-shaped roller y /
, s / (the range in which the rollers pass while contacting each other on the outer ring) can be freely designed.
この鼓形コロｙ／ 、 ｓｌは軸受中心の左右に位置す
るだめ、内輪２′の外表面２“の一部と接触することに
なる。それ故、中心側の径は小さく外側の径が大きい形
状となる。Since these drum-shaped rollers y/ and sl are located on the left and right sides of the bearing center, they come into contact with a part of the outer surface 2'' of the inner ring 2'.Therefore, the diameter on the center side is small and the diameter on the outside is large. It becomes a shape.
そして、外側ｍ１り“、り′は夫々鼓形コロｙ／ ＋、
ｓ／中心からある半径を有する球面状に形成している
。And the outer m1 and ri′ are respectively drum-shaped colo y/ +,
s/It is formed into a spherical shape with a certain radius from the center.
又、前記外輪３′の外周両仙ｊ面に切欠部／／。Also, there are notches on both sacrum surfaces of the outer circumference of the outer ring 3'.
／／を設け、中央に内孔／３を設けた円形をした側面支
持盤／λ、／２の外周内面に係止部／３゜／３を突設し
、との係止部／３．／３を前記切欠部／’／、／／に嵌
合して側面支持盤／２．／１を夫々外輪３′の両側面に
固定する。尚、両側の側面支持盤／２．／２の外側間の
距離は内輪２′の幅とほぼ同一に形成する。そして、両
側の側面支持盤／２．／２の内面には夫々鼓形コログ′
。A circular side support plate /λ with an inner hole /3 in the center and a locking portion /3°/3 protruding from the outer peripheral inner surface of /2, and a locking portion /3. /3 is fitted into the notches /'/, // to form the side support plate /2. /1 are respectively fixed to both sides of the outer ring 3'. In addition, side support plates on both sides/2. The distance between the outer sides of the inner ring 2' is approximately the same as the width of the inner ring 2'. And side support plates on both sides/2. /2 has a drum-shaped korog on the inside.
.
−−−２３′、−ｍ−の夫々球面状の外側面り“。---23', -m- each have a spherical outer surface.
Ｓ〃を嵌合支持できるようにや＼曲率半径を太きくした
支持溝／グ、／グを設けている。又、両側面支持盤／、
２．／２の前記内孔／左は内輪２′の内表面ｒとの間に
ラビリンスンール／左′を形成する。Support grooves /g and /g with a thicker radius of curvature are provided so that S can be fitted and supported. Also, support plates on both sides/
2. The inner hole /2 forms a labyrinth rule /left' with the inner surface r of the inner ring 2'.
尚、第グ図中／乙は両ｇＡ１１の鼓形コログ′、ｓ′及
び内外輪、ｚ／ 、 ３／間に形成される潤滑剤充填空
間、／７は潤滑剤充填用孔、７は従来と同じノ・ウンン
グ、ｇはエンドプレートである。In addition, /B in Fig. 1 is the lubricant filling space formed between the drum-shaped corrugs', s' and the inner and outer rings of both gA11, z/, 3/, /7 is the lubricant filling hole, and 7 is the conventional lubricant filling space. Same as No-ung, g is the end plate.
本実施例は前記のように構成したもので、軸／が撓みに
よりある角度θをもった傾斜を行うと、第Ｓ図に示すよ
うに内輪２′はこれにつれて同じくθだけ傾くが、鼓形
コログ’＋ −−−＋ ５’＋−−−は夫々元の位置に
保持されるため、自動調芯効果により軸受は撓みの影響
を受けない。This embodiment is constructed as described above, and when the shaft/shaft tilts by a certain angle θ due to flexure, the inner ring 2' tilts by the same angle θ as shown in FIG. Since the corrugs '+ ---+ 5'+ --- are held in their original positions, the bearing is not affected by deflection due to the self-aligning effect.
又、ラジアル荷重と同時にスラスト荷重が作用した場合
、第７図鎖線に示すように、ラジアル荷重の荷重分布は
従来の自動調芯コロ軸受と同様に、鼓形コロｙｌ 、
ｓ／の中央部で最大となる面圧が外輪３′に作用して支
持される。この時、スラスト荷重の荷重分布は鼓形コロ
グ′の球面中心に向って山形を呈し、その荷重は１ｌｊ
ｊ面支持盤／２に伝達され、十分長い支持長さを有する
ハウジング７によって支持きれ、外輪３′にはスラスト
荷重がほとんど作用しない。したがって、従来の自動調
芯コロ軸受のような外輪の割れによる損傷を防止するこ
とができる。In addition, when a thrust load acts simultaneously with a radial load, the load distribution of the radial load is similar to the conventional self-aligning roller bearing, as shown by the chain line in Figure 7.
The maximum surface pressure at the center of s/ acts on and supports the outer ring 3'. At this time, the load distribution of the thrust load takes on a mountain shape toward the center of the spherical surface of the drum-shaped Korok', and the load is 1 lj
The thrust load is transmitted to the j-plane support plate/2 and can be fully supported by the housing 7 having a sufficiently long support length, so that almost no thrust load acts on the outer ring 3'. Therefore, damage caused by cracking of the outer ring as in conventional self-aligning roller bearings can be prevented.
又、潤滑剤充填空間／乙にはグリス等の潤滑剤が充填さ
れるが、両側の側面支持盤／２．／２の内孔／３と内輪
２′の外表面コ“との間にラビリンスシール／ ５’を
形成しているので潤滑剤封入型の軸受として無給脂で使
用することもできる。Also, the lubricant filling space/B is filled with lubricant such as grease, but the side support plates on both sides/2. Since a labyrinth seal /5' is formed between the inner hole /3 of /2 and the outer surface of the inner ring 2', it can also be used as a lubricant-filled bearing without lubrication.
本発明は前記のような構成、作用を有償るから、小さな
空間で調芯性を鳴し、ラジアル及びスラスト両方向の荷
重を受けることができ、従来のように外輪が割れる恐れ
がないものである・尚、内輪λ′と側面支持盤／２の内
孔／左の間にラビリンス７−ルを設けることに、より潤
滑剤を封入することができ、外部からの異物や水等の侵
入を防止することもできる。Since the present invention has the above-described structure and function, it can achieve alignment in a small space, can receive loads in both radial and thrust directions, and does not have the fear of cracking of the outer ring as in the past.・In addition, by providing a labyrinth 7-rule between the inner ring λ' and the inner hole/left of the side support plate/2, it is possible to seal in more lubricant and prevent foreign matter and water from entering from the outside. You can also.
第１図は従来のころがり軸受の断面図、第２図（イ）、
（ロ）はその作用説明図、第３図は従来の球面座付円筒
コロ軸受の断面図、第７図は本発明 □に係るラジアル
及びスラスト両荷重を受けることができるころがり軸受
の断面図、第３図はその軸撓み時の断面図である。
°尚、図中コ′は内輪、ｒは外表面、３′は外輪、３“
は内表面、グ′、Ｓ′は鼓形コロ、グ〃、左“は外表面
、／２は１ｌＩＩｊ面支持盤、／グは支持ｔＱ、ｉ゛ｓ
ｕｓｕ内孔′はラビリンス７−ルである。
偶許出願人 川崎製鉄株式会社
第１図
′ 第２図
（イ）
第２図
（ロ）
第３ＮFigure 1 is a cross-sectional view of a conventional rolling bearing, Figure 2 (a),
(B) is an explanatory diagram of its operation, FIG. 3 is a sectional view of a conventional cylindrical roller bearing with a spherical seat, and FIG. 7 is a sectional view of a rolling bearing capable of receiving both radial and thrust loads according to the present invention. FIG. 3 is a sectional view when the shaft is bent. °In the figure, C' is the inner ring, r is the outer surface, 3' is the outer ring, and 3"
is the inner surface, G′, S′ are the drum-shaped rollers, G〃, left” is the outer surface, /2 is the 1lIIj surface support plate, /g is the support tQ, i゛s
The usu inner hole' is a labyrinth 7-hole. Applicant: Kawasaki Steel Corporation Figure 1' Figure 2 (A) Figure 2 (B) Figure 3N
Claims (1)
円弧状の凸面で形成し、外輪３′の内表面３“を対向す
る断面円弧状の凸面で形成し、内外輪、２／ 、 ３／
間に転動外周面を凹面で形成した多数の鼓形コログ’＋
−−−＋ｊ’＋ −−一を、２列に配置し、各鼓形コ
ロｙ／ 、 ｓ／の両性側面ｆ′。 ＆／／を球面状に形成し、外輪３′の両性側に固定した
内孔／Ｓを有する円形の側面支持盤／２゜／２に前記鼓
形コロ＆’、 ＆’の球面状の外側面グ“、左“と接す
る断面円弧状の支持溝／グ、／￥を設けたことを特徴と
するラジアル及びスラスト両荷重を受けることができる
ころがり軸受。 １．２） 内輪２′の幅を両側の側面支持盤／２．／２
の間隔とほぼ一致させ、内輪２′の外表面λ〃と側面支
持盤／２．／２の内孔／左にラビリンスシール／ ５’
を形成したことを特徴とする特許、請求の範囲第１項記
載のラジアル及びスラスト両荷重を受けることができる
ころがり軸受。(1) The outer surface r of the inner ring 2' is formed by a convex surface having an arcuate cross section with the center of curvature on the shaft side, and the inner surface 3'' of the outer ring 3' is formed by opposing convex surfaces having an arcuate cross section. 2/, 3/
Numerous drum-shaped corogs with concave rolling outer peripheral surfaces in between.
---+j'+--1 are arranged in two rows, and the bilateral sides f' of each hourglass y/, s/. &// is formed into a spherical shape and has an inner hole /S fixed to both sides of the outer ring 3'. A rolling bearing capable of receiving both radial and thrust loads, characterized by having support grooves having an arcuate cross section in contact with the side surfaces. 1.2) Adjust the width of the inner ring 2' by the side support plates on both sides/2. /2
The distance between the outer surface λ〃 of the inner ring 2' and the side support plate /2. / 2 inner holes / Labyrinth seal on the left / 5'
A rolling bearing capable of receiving both radial and thrust loads as claimed in claim 1.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP59042120A JPS60188617A (en) | 1984-03-07 | 1984-03-07 | Roller bearing capable of standing both radial and thrust loads |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP59042120A JPS60188617A (en) | 1984-03-07 | 1984-03-07 | Roller bearing capable of standing both radial and thrust loads |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS60188617A true JPS60188617A (en) | 1985-09-26 |
Family
ID=12627090
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP59042120A Pending JPS60188617A (en) | 1984-03-07 | 1984-03-07 | Roller bearing capable of standing both radial and thrust loads |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS60188617A (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS639718A (en) * | 1986-06-30 | 1988-01-16 | エマ−ソン・エレクトリツク・カンパニ− | Two row type cylindrical type bearing receiving expansion inaxial direction of shaft |
| US5413416A (en) * | 1993-12-03 | 1995-05-09 | Rexnord Corporation | Roller guide member for full complement roller bearing |
| US5441351A (en) * | 1993-10-26 | 1995-08-15 | Rexnord Corporation | Full complement self-aligning roller bearing |
| WO2002021007A1 (en) | 2000-09-05 | 2002-03-14 | Rexnord Corporation | Retainerless precessing roller bearing |
| FR2872233A1 (en) * | 2004-06-23 | 2005-12-30 | Bertin Technologies Soc Par Ac | Electric motor`s output shaft guiding device for rapid vibration of biological sample tubes, has ball rings provided between ball and outer rings and nut screwed on upper part of crown gear and supported on outer ring of upper ball bearing |
| WO2006008397A1 (en) * | 2004-06-23 | 2006-01-26 | Bertin Technologies | Device for guiding a shaft in an oscillating movement |
-
1984
- 1984-03-07 JP JP59042120A patent/JPS60188617A/en active Pending
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS639718A (en) * | 1986-06-30 | 1988-01-16 | エマ−ソン・エレクトリツク・カンパニ− | Two row type cylindrical type bearing receiving expansion inaxial direction of shaft |
| JPH0461970B2 (en) * | 1986-06-30 | 1992-10-02 | Emerson Electric Co | |
| US5441351A (en) * | 1993-10-26 | 1995-08-15 | Rexnord Corporation | Full complement self-aligning roller bearing |
| US5413416A (en) * | 1993-12-03 | 1995-05-09 | Rexnord Corporation | Roller guide member for full complement roller bearing |
| US5582483A (en) * | 1993-12-03 | 1996-12-10 | Rexnord Corporation | Roller guide member for full complement roller bearing |
| US5667312A (en) * | 1993-12-03 | 1997-09-16 | Rexnord Corporation | Roller bearing for use in oscillatory applications |
| WO2002021007A1 (en) | 2000-09-05 | 2002-03-14 | Rexnord Corporation | Retainerless precessing roller bearing |
| US6394656B1 (en) | 2000-09-05 | 2002-05-28 | Rexnord Corporation | Retainerless precessing roller bearing |
| FR2872233A1 (en) * | 2004-06-23 | 2005-12-30 | Bertin Technologies Soc Par Ac | Electric motor`s output shaft guiding device for rapid vibration of biological sample tubes, has ball rings provided between ball and outer rings and nut screwed on upper part of crown gear and supported on outer ring of upper ball bearing |
| WO2006008397A1 (en) * | 2004-06-23 | 2006-01-26 | Bertin Technologies | Device for guiding a shaft in an oscillating movement |
| US7448789B2 (en) | 2004-06-23 | 2008-11-11 | Bertin Technologies | Device for guiding a shaft in an oscillating movement |
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