JP2652377B2 - Protective ball bearings in magnetic bearing devices - Google Patents
Protective ball bearings in magnetic bearing devicesInfo
- Publication number
- JP2652377B2 JP2652377B2 JP62123214A JP12321487A JP2652377B2 JP 2652377 B2 JP2652377 B2 JP 2652377B2 JP 62123214 A JP62123214 A JP 62123214A JP 12321487 A JP12321487 A JP 12321487A JP 2652377 B2 JP2652377 B2 JP 2652377B2
- Authority
- JP
- Japan
- Prior art keywords
- bearing
- protective
- fixed
- rotor
- magnetic 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
- F16C32/00—Bearings not otherwise provided for
- F16C32/04—Bearings not otherwise provided for using magnetic or electric supporting means
- F16C32/0406—Magnetic bearings
- F16C32/044—Active magnetic bearings
- F16C32/0442—Active magnetic bearings with devices affected by abnormal, undesired or non-standard conditions such as shock-load, power outage, start-up or touchdown
-
- 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
- F16C33/6696—Special parts or details in view of lubrication with solids as lubricant, e.g. dry coatings, powder
-
- 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
- F16C39/00—Relieving load on bearings
- F16C39/02—Relieving load on bearings using mechanical means
-
- 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
- F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
- F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
- F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls
-
- 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
- F16C2300/00—Application independent of particular apparatuses
- F16C2300/40—Application independent of particular apparatuses related to environment, i.e. operating conditions
- F16C2300/62—Application independent of particular apparatuses related to environment, i.e. operating conditions low pressure, e.g. elements operating under vacuum conditions
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Magnetic Bearings And Hydrostatic Bearings (AREA)
- Rolling Contact Bearings (AREA)
Description
【発明の詳細な説明】 産業上の利用分野 この発明は、たとえば真空ポンプなどの磁気軸受装置
における保護用玉軸受に関する。Description: TECHNICAL FIELD The present invention relates to a protective ball bearing in a magnetic bearing device such as a vacuum pump.
従来の技術とその問題点 第３図は従来の磁気軸受装置の１例を示し、垂直固定
軸（１）の周囲に円筒状のロータ（２）が配置されてい
る。ロータ（２）は、固定軸（１）に設けられたラジア
ル磁気軸受（３）（４）およびアキシャル磁気軸受
（５）（６）で非接触状態に支持され、たとえば30000r
pm程度の高速で回転する。固定軸（１）の上下２箇所
に、ロータ（２）の停止時にこれを受けるための保護用
玉軸受（７）（８）が設けられている。各保護用軸受
（７）（８）には負荷能力を増すため総玉軸受が使用さ
れ、その内輪（7a）（8a）が固定軸（１）の外周の円筒
面に嵌合固定されている。ロータ（２）が正常に回転し
ているときは、ロータ（２）と保護用軸受（７）（８）
との間にはたとえば0.1〜数mm程度のすきまがある。そ
して、ロータ（２）が停止するときには、ロータ（２）
が保護用軸受（７）（８）の外輪（7b）（8b）に接触し
てこれに受けられ、ロータ（２）が磁気軸受（３）
（４）（５）（６）などに接触してこれらを損傷しない
ようになっている。なお、このようにロータが保護用軸
受に受けられて停止する動作をタッチダウンという。FIG. 3 shows an example of a conventional magnetic bearing device, in which a cylindrical rotor (2) is arranged around a vertical fixed shaft (1). The rotor (2) is supported in a non-contact state by radial magnetic bearings (3) and (4) and axial magnetic bearings (5) and (6) provided on the fixed shaft (1).
It rotates at a high speed of about pm. Protective ball bearings (7) and (8) are provided at two locations above and below the fixed shaft (1) to receive the rotor (2) when it stops. A full ball bearing is used for each of the protective bearings (7) and (8) to increase the load capacity, and the inner rings (7a) and (8a) are fitted and fixed to the cylindrical surface on the outer periphery of the fixed shaft (1). . When the rotor (2) is rotating normally, the rotor (2) and the protective bearings (7) (8)
Is between 0.1 and several mm, for example. When the rotor (2) stops, the rotor (2)
Contacts the outer races (7b) and (8b) of the protective bearings (7) and (8) and is received by the outer races (7b) and (8b).
(4) (5), (6), etc., so as not to damage them. The operation in which the rotor is stopped by being received by the protective bearing is called touch-down.
ところで、磁気軸受装置が正常な状態で停止する場
合、ロータ（２）は徐々に減速され、かなり低速になっ
てから保護用軸受（７）（８）に接触して低速でタッチ
ダウンするため、保護用軸受（７）（８）が損傷するこ
とはない。これに対し、停電その他の故障により磁気軸
受（３）（４）（５）（６）が作動しなくなった場合
は、高速で回転しているロータ（２）が保護用軸受
（７）（８）の接触して高速でタッチダウンするため、
とくに真空ポンプの磁気軸受装置の場合、保護用軸受
（７）（８）が真空中（たとえば10-2〜10-3Torr）にお
いて急激な立上りで高速回転（たとえばdmn＞300×1
04）することになる。このため、従来の保護用軸受
（７）（８）では、耐久性が劣っており、１回の高速タ
ッチダウンの途中で保護用軸受（７）（８）が損傷する
というような問題があった。By the way, when the magnetic bearing device is stopped in a normal state, the rotor (2) is gradually decelerated to a relatively low speed, and then comes into contact with the protective bearings (7) and (8) to perform a touchdown at a low speed. The protective bearings (7), (8) are not damaged. On the other hand, when the magnetic bearings (3), (4), (5), and (6) stop operating due to a power failure or other failure, the rotor (2) rotating at a high speed causes the protective bearings (7), (8). ) To touch down quickly at the touch,
In particular, in the case of a magnetic bearing device of a vacuum pump, the protective bearings (7) and (8) rotate rapidly at a rapid rise in a vacuum (for example, 10 −2 to 10 −3 Torr) (for example, dmn> 300 × 1).
0 4 ). For this reason, the conventional protective bearings (7) and (8) are inferior in durability and have a problem that the protective bearings (7) and (8) are damaged during one high-speed touchdown. Was.
また、保護用玉軸受は、上記のような使用条件の厳し
さから、多くても10回程度のタッチダウンで破損するた
め、頻繁に取替えを行う必要がある。また、保護用軸受
においては、当然ながら、大きな衝撃および駆動トルク
により、たとえばハウジングなどの固定部分との嵌合面
が破損したり、焼付きなどの損傷を受ける。そのような
場合、ハウジングからの保護用軸受の取外しが不可能に
なり、保護用軸受をハウジングごと交換することにな
り、メンテナンス費用がかさむという問題がある。Further, since the protective ball bearing is damaged by at most ten touchdowns due to the severe operating conditions as described above, it must be replaced frequently. Also, in the protective bearing, a large impact and a driving torque naturally damage the fitting surface with a fixed portion such as a housing, or suffer damage such as seizure. In such a case, it becomes impossible to remove the protective bearing from the housing, and the protective bearing must be replaced together with the housing, resulting in an increase in maintenance costs.
磁気軸受装置には、上記のように固定軸の周囲を筒状
のロータが回転する形式の他に、筒状の固定ケースの内
側をロータ軸が回転する形式もある。この場合、ケース
の上下２箇所に保護用軸受が設けられ、軸が停止すると
きに、軸が保護用軸受の内輪に接触してこれに受けられ
るが、上記と同様の問題がある。In the magnetic bearing device, in addition to the type in which the cylindrical rotor rotates around the fixed shaft as described above, there is also a type in which the rotor shaft rotates inside the cylindrical fixed case. In this case, protective bearings are provided at the upper and lower portions of the case, and when the shaft stops, the shaft contacts the inner ring of the protective bearing and is received by the inner ring. However, there is the same problem as described above.
この発明の目的は、上記のような問題を解決した交換
の容易な保護用玉軸受を提供することにある。An object of the present invention is to provide an easily replaceable protective ball bearing that solves the above-described problems.
問題点を解決するための手段 この発明による保護用玉軸受は、固定部分に対し回転
部分を磁気軸受で非接触状態に支持して回転させる磁気
軸受装置において、回転部分の停止時に回転部分を受け
るために固定部分の複数箇所に設けられる保護用玉軸受
であって、一方の軌道輪が固定部分の円筒面に嵌合固定
され、この軌道輪の固定部分との嵌合面に固体潤滑剤が
コーティングされていることを特徴とするものである。Means for Solving the Problems A protective ball bearing according to the present invention is a magnetic bearing device that rotates while supporting a rotating part in a non-contact state with a magnetic part with respect to a fixed part, and receives the rotating part when the rotating part stops. A ball bearing for protection provided at a plurality of locations of the fixed part, one of the races is fitted and fixed to the cylindrical surface of the fixed part, and a solid lubricant is applied to the fitting surface of the race with the fixed part. It is characterized by being coated.
作用 固定部分の円筒面に嵌合固定される軌道輪の固定部分
との嵌合面に固体潤滑剤がコーティングされているの
で、高速タッチダウン時などの大きな衝撃による上記嵌
合面の破損や焼付きが防止される。また、固体潤滑剤に
より固定部分との摩擦力が小さくなるため、軌道論の抜
取りが容易である。したがって、保護用玉軸受が破損し
たときに、それだけを容易に交換することができる。Action Since the solid lubricant is coated on the fitting surface of the bearing ring that is fitted and fixed to the cylindrical surface of the fixed part, the above-mentioned mating surface may be damaged or burned by a large impact such as during high-speed touchdown. Sticking is prevented. In addition, since the frictional force with the fixed portion is reduced by the solid lubricant, it is easy to extract the orbit theory. Therefore, when the protective ball bearing is damaged, only the protective ball bearing can be easily replaced.
実 施 例 第１図は、磁気軸受装置の保護用ラジアル玉軸受の１
具体例を示す。FIG. 1 shows a radial ball bearing 1 for protection of a magnetic bearing device.
A specific example will be described.
この軸受（10）は総玉軸受であり、内輪（12）および
外輪（13）の全表面に固体潤滑剤たとえば二流化モリブ
デン層（16）がコーティングにより形成されている。The bearing (10) is a full ball bearing, and has a solid lubricant, for example, a dihydrated molybdenum layer (16) formed on the entire surface of the inner ring (12) and the outer ring (13) by coating.
この軸受（10）を第３図のような固定軸の周囲を筒状
のロータが回転する形式の磁気軸受装置に使用する場
合、内輪（12）固定軸の外周の円筒面に嵌合固定され
る。When this bearing (10) is used in a magnetic bearing device in which a cylindrical rotor rotates around a fixed shaft as shown in FIG. 3, the bearing (10) is fitted and fixed to the cylindrical surface on the outer periphery of the inner ring (12) fixed shaft. You.
ロータが正常に回転している場合、ロータは磁気軸受
により非接触状態に支持され、ロータ軸受（10）の外輪
（13）との間には適当なすきまがあり、外輪（13）は停
止している。When the rotor is rotating normally, the rotor is supported by the magnetic bearing in a non-contact state, there is a suitable clearance between the rotor bearing (10) and the outer ring (13), and the outer ring (13) stops and stops. ing.
高速タッチダウンの場合、高速で回転しているロータ
が軸受（10）の外輪（13）に接触し、外輪（13）も高速
で回転を開始する。このため、従来の軸受では、外輪は
第２図に破線（Ａ）で示すように非常に急激な立上りで
高速回転を開始し、外輪の最高回転数（ａ）はロータの
回転数（ｃ）に近くなる。このため、前述のように、軸
受が損傷する。なお、第２図において、鎖線（Ｃ）はロ
ータの回転数の変化を示す。In the case of high-speed touchdown, the rotor rotating at high speed comes into contact with the outer ring (13) of the bearing (10), and the outer ring (13) also starts rotating at high speed. For this reason, in the conventional bearing, the outer ring starts high-speed rotation at a very steep rise as shown by a broken line (A) in FIG. 2, and the maximum rotation number (a) of the outer ring is equal to the rotation number (c) of the rotor. Become closer to Therefore, the bearing is damaged as described above. In FIG. 2, a chain line (C) indicates a change in the number of revolutions of the rotor.
ところが、上記の軸受（10）の場合、内輪（12）と外
輪（13）の全表面に二流化モリブデン層（16）がコーテ
ィングにより形成されているので、次に説明するよう
に、耐久性が高く、このような損傷を防止することがで
きる。However, in the case of the above-mentioned bearing (10), the entire surface of the inner ring (12) and the outer ring (13) is formed with a coating of a molybdenum disulfide layer (16). Highly, such damage can be prevented.
すなわち、まず、外輪（13）の外周面にコーティング
された二硫化モリブデン層（16）がロータと外輪（13）
の間のすべりを助長するため、第２図に実線（Ｂ）で示
すように高速タッチダウン時の外輪（13）の立上りは緩
やかになり、外輪（13）の最高回転数（ｂ）も小さくな
る。そして、このように外輪（13）の最高回転数が小さ
くなるため、外輪（13）および玉（11）の遠心力が小さ
くなる。内輪（12）および外輪（13）の軌道みぞ（14）
（15）の二流化モリブデン層（16）は玉（11）との間の
潤滑剤となる。したがって、軸受（10）の損傷の度合が
小さくなる。また、固定軸との固定嵌合面である内輪
（12）の内周面に二流化モリブデン層（16）が形成され
ているので、高速タッチダウン時などの大きな衝撃によ
る内輪（12）の内周面の損傷や焼付きが防止される。ま
た、二流化モリブデン層（16）により固定軸との間の摩
擦力が小さくなっているので、内輪（12）の抜取りが容
易である。したがって、軸受（10）が破損したときに、
軸受（10）だけを容易に交換することができる。That is, first, the molybdenum disulfide layer (16) coated on the outer peripheral surface of the outer ring (13) is formed by the rotor and the outer ring (13).
As shown by the solid line (B) in FIG. 2, the outer ring (13) rises gently during high-speed touchdown, and the maximum rotational speed (b) of the outer ring (13) is small, as shown by the solid line (B) in FIG. Become. Since the maximum rotation speed of the outer ring (13) is reduced in this way, the centrifugal force of the outer ring (13) and the ball (11) is reduced. Track groove (14) for inner ring (12) and outer ring (13)
The difluidized molybdenum layer (16) of (15) serves as a lubricant between the balls (11). Therefore, the degree of damage to the bearing (10) is reduced. In addition, since the molybdenum layer (16) is formed on the inner peripheral surface of the inner ring (12), which is the fixed fitting surface with the fixed shaft, the inner ring (12) is subjected to a large impact such as during high-speed touchdown. The peripheral surface is prevented from being damaged or seized. Further, since the frictional force between the molybdenum layer (16) and the fixed shaft is reduced, the inner ring (12) can be easily removed. Therefore, when the bearing (10) is broken,
Only the bearing (10) can be easily replaced.
上記の軸受（10）は、たとえば第４図に示すように筒
状の固定ケース（17）の内側をロータ軸（18）が回転す
る形式の磁気軸受装置にも使用できる。この場合、外輪
（13）が固定ケース（17）の内周の円筒面に嵌合固定さ
れ、外輪（13）の外周面がケース（17）との固定嵌合面
となり、ロータ軸（18）は内輪（12）の内周面の二硫化
モリブデン層（16）に接触する。そして、この場合も、
二流化モリブデン層（16）により、上記とほぼ同様の効
果が奏される。また、第５図に示すように、内輪（12）
の内面およびその表面の二硫化モリブデン層（16）にテ
ーパ状部分を設け、これに対応するようにロータ軸（1
8）にもテーパ状部分を設けることにより、タッチダウ
ン時に、高速回転しているロータ軸（18）のみそすり運
動による軸受の焼付きが防止できる。The above-mentioned bearing (10) can also be used for a magnetic bearing device of a type in which a rotor shaft (18) rotates inside a cylindrical fixed case (17) as shown in FIG. 4, for example. In this case, the outer ring (13) is fitted and fixed to the inner cylindrical surface of the fixed case (17), and the outer peripheral surface of the outer ring (13) becomes a fixed fitting surface with the case (17), and the rotor shaft (18) Contacts the molybdenum disulfide layer (16) on the inner peripheral surface of the inner ring (12). And also in this case,
Almost the same effects as described above can be obtained by the molybdenum disulfide layer (16). Also, as shown in FIG.
Of the molybdenum disulfide layer (16) on the inner surface of the
By providing a tapered portion also in 8), seizure of the bearing due to the sliding motion of only the rotor shaft (18) rotating at high speed during touchdown can be prevented.
上記実施例には総玉軸受を示したが、この発明は保持
器付玉軸受にも適用できる。また、潤滑剤を軌道みぞ
（14）（15）にコーティングするかわりに玉（11）の表
面にコーティングしてもよい。Although the above-described embodiment shows a full ball bearing, the present invention can be applied to a ball bearing with a cage. Instead of coating the track grooves (14) and (15) with a lubricant, the lubricant may be coated on the surface of the ball (11).
発明の効果 この発明の磁気軸受装置における保護用玉軸受によれ
ば、固定部分の円筒面に嵌合固定される軌道輪の固定部
分との嵌合面に固体潤滑剤がコーティングされているか
ら、高速タッチダウン時などの大きな衝撃による上記嵌
合面の破損や焼付きが防止されるとともに、固定部分と
の間の摩擦力が小さくなり、玉軸受が破損したときにそ
れだけを容易に交換することができる。したがって、従
来のように玉軸受をハウジングごと交換するような必要
がなく、メンテナンス費用が安くなる。According to the protective ball bearing in the magnetic bearing device of the present invention, the solid lubricant is coated on the fitting surface of the fixed portion of the bearing ring that is fitted and fixed on the cylindrical surface of the fixed portion, Damage and seizure of the mating surface due to large impact such as high-speed touchdown are prevented, and the frictional force with the fixed part is reduced, so if the ball bearing is damaged, it can be replaced easily Can be. Therefore, there is no need to replace the ball bearing with the housing as in the related art, and the maintenance cost is reduced.
第１図はこの発明の１実施例を示す保護用ラジアル玉軸
受の主要部縦断面図、第２図は高速タッチダウン時の外
輪の回転速度の変化を示すグラフ、第３図は従来の保護
用玉軸受を組込んだ磁気軸受装置を示す縦断面図、第４
図はこの発明の他の実施例を示す磁気軸受装置の保護用
ラジアル玉軸受の部分の縦断面図、第５図はこの発明の
さらに他の実施例を示す第４図相当の図面である。 （10）……保護用ラジアル玉軸受、（11）……玉、（1
2）……内輪、（13）……外輪、（14）（15）…軌道み
ぞ。FIG. 1 is a longitudinal sectional view of a main part of a radial ball bearing for protection showing one embodiment of the present invention, FIG. 2 is a graph showing a change in the rotation speed of an outer ring at the time of high-speed touchdown, and FIG. Sectional view showing a magnetic bearing device incorporating a ball bearing for a vehicle, FIG.
FIG. 5 is a longitudinal sectional view of a portion of a radial ball bearing for protection of a magnetic bearing device according to another embodiment of the present invention, and FIG. 5 is a drawing corresponding to FIG. 4 showing still another embodiment of the present invention. (10) ... radial ball bearing for protection, (11) ... ball, (1
2) ... Inner ring, (13) ... Outer ring, (14) (15) ... Track groove.
───────────────────────────────────────────────────── フロントページの続き (56)参考文献 特開 昭61−165021（ＪＰ，Ａ) 特開 昭63−270917（ＪＰ，Ａ) 実開 昭61−83243（ＪＰ，Ｕ) ──────────────────────────────────────────────────続 き Continuation of the front page (56) References JP-A-61-165021 (JP, A) JP-A-63-270917 (JP, A) Real opening Sho-61-83243 (JP, U)
Claims (1)
触状態に支持して回転させる磁気軸受装置において、回
転部分の停止時に回転部分を受けるために固定部分の複
数箇所に設けられる保護用玉軸受であって、 一方の軌道輪が固定部分の円筒面に嵌合固定され、この
軌道輪の固定部分との嵌合面に固体潤滑剤がコーティン
グされていることを特徴とする磁気軸受装置における保
護用玉軸受。In a magnetic bearing device for rotating a rotating portion while supporting a rotating portion in a non-contact state with a fixed portion with respect to a fixed portion, a protection portion provided at a plurality of portions of the fixed portion to receive the rotating portion when the rotating portion is stopped. A magnetic bearing device, characterized in that one bearing ring is fixedly fitted to a cylindrical surface of a fixed portion, and a solid lubricant is coated on a fitting surface of the bearing ring with the fixed portion. Ball bearing for protection.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP62123214A JP2652377B2 (en) | 1987-05-20 | 1987-05-20 | Protective ball bearings in magnetic bearing devices |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP62123214A JP2652377B2 (en) | 1987-05-20 | 1987-05-20 | Protective ball bearings in magnetic bearing devices |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS63289317A JPS63289317A (en) | 1988-11-25 |
| JP2652377B2 true JP2652377B2 (en) | 1997-09-10 |
Family
ID=14855024
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP62123214A Expired - Lifetime JP2652377B2 (en) | 1987-05-20 | 1987-05-20 | Protective ball bearings in magnetic bearing devices |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2652377B2 (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5272403A (en) * | 1991-02-15 | 1993-12-21 | The Glacier Metal Company Limited | Low friction backup system for magnetic bearings |
| JP4539861B2 (en) * | 2004-12-01 | 2010-09-08 | 株式会社ジェイテクト | Touchdown bearing |
| WO2006059651A1 (en) * | 2004-12-01 | 2006-06-08 | Jtekt Corporation | Touchdown bearing |
| US7806596B2 (en) * | 2007-08-31 | 2010-10-05 | Hamilton Sundstrand Corporation | High speed bearing system with bind-free axial displacement |
| EP2770222A1 (en) * | 2013-02-20 | 2014-08-27 | Sulzer Pump Solutions AB | A machine provided with safety bearing |
| CN112392859A (en) * | 2020-11-24 | 2021-02-23 | 中国电子科技集团公司第十四研究所 | Bearing raceway antifriction method based on low-temperature low-pressure high-load working condition |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6183243U (en) * | 1984-11-08 | 1986-06-02 | ||
| JPS61165021A (en) * | 1985-01-11 | 1986-07-25 | Koyo Seiko Co Ltd | Roller bearing |
| JPS63270917A (en) * | 1987-04-27 | 1988-11-08 | Nippon Seiko Kk | Bearing device |
-
1987
- 1987-05-20 JP JP62123214A patent/JP2652377B2/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| JPS63289317A (en) | 1988-11-25 |
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