JPS63167120A - Magnetic bearing device - Google Patents
Magnetic bearing deviceInfo
- Publication number
- JPS63167120A JPS63167120A JP31370086A JP31370086A JPS63167120A JP S63167120 A JPS63167120 A JP S63167120A JP 31370086 A JP31370086 A JP 31370086A JP 31370086 A JP31370086 A JP 31370086A JP S63167120 A JPS63167120 A JP S63167120A
- Authority
- JP
- Japan
- Prior art keywords
- bearing
- bearings
- tapered surface
- ring
- protective
- 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.)
- Granted
Links
- 230000001681 protective effect Effects 0.000 claims description 28
- 230000007423 decrease Effects 0.000 description 10
- 230000036316 preload Effects 0.000 description 4
- 230000002159 abnormal effect Effects 0.000 description 1
- 229910003460 diamond Inorganic materials 0.000 description 1
- 239000010432 diamond Substances 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000007257 malfunction Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 125000006850 spacer group Chemical group 0.000 description 1
- 229920003051 synthetic elastomer Polymers 0.000 description 1
- 229920003002 synthetic resin Polymers 0.000 description 1
- 239000000057 synthetic resin Substances 0.000 description 1
- 239000005061 synthetic rubber Substances 0.000 description 1
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
- F16C39/00—Relieving load on bearings
- F16C39/02—Relieving load on bearings using mechanical means
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Support Of The Bearing (AREA)
- Magnetic Bearings And Hydrostatic Bearings (AREA)
Abstract
Description
【発明の詳細な説明】 産業上の利用分野 この発明は、磁気軸受装置に関する。[Detailed description of the invention] Industrial applications The present invention relates to a magnetic bearing device.
従来の技術とその問題点
第5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
) (8)で非接触状態に支持され、たとえば3000
0 rpm程度の高速で回転する。Prior art and its problems FIG. 5 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) has radial magnetic bearings (3) (4) and axial magnetic bearings (5) provided on the fixed shaft (1).
) (8) in a non-contact state, for example 3000
Rotates at a high speed of about 0 rpm.
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) (8
a)が固定軸(1)に固定されている。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1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(1) (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。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)に接触するため、保護用軸受(7
)(8)が損傷することはない。ところが、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)か保護用軸受(7)(8)に接触するため、保護
用軸受(7)(8)が損傷するというような問題があっ
た。これは、次のような理由によるものと考えられる。Protective bearings (7) and (8) are provided at two locations above and below the fixed shaft (1) to receive the rotor (2) when it is stopped. Full ball bearings are used for each protective bearing (7) (8) to increase the load capacity, and their inner rings (7a) (8)
a) is fixed to a fixed shaft (1). When the rotor (2) is rotating normally, there is, for example, 0.0 mm between the rotor (2) and the protective bearings (7) and (8). There is a gap of about 1 to several 1. When the rotor (2) stops, the rotor (2) contacts and is received by the outer rings (7b) (8b) of the protective bearings (7) (8), and the rotor (2) is moved by the magnetic bearings ( 1) (4) (5) (6) etc., so as not to damage them by contacting them. By the way, when the magnetic bearing device stops in a normal state, the rotor (2) is gradually decelerated and comes into contact with the protective bearings (7) and (8) after reaching a considerably low speed.
)(8) will not be damaged. However, due to a power outage or other failure, the magnetic bearing (3) (4) (5) (6)
If it stops working, it will come into contact with the rotor (2), which is rotating at high speed, and the protective bearings (7) and (8), causing problems such as damage to the protective bearings (7) and (8). there were. This is considered to be due to the following reasons.
すなわち、高速で回転しているロータが保護用軸受の外
輪に接触すると、外輪も高速で回転を開始するため、玉
の遠心力と外輪自身の遠心力とにより外輪が膨張して、
軸受すきまが異常に増大する。In other words, when the rotor rotating at high speed contacts the outer ring of the protective bearing, the outer ring also starts rotating at high speed, and the outer ring expands due to the centrifugal force of the balls and the outer ring itself.
Bearing clearance increases abnormally.
このため、内輪と接触する玉数が減少し、内輪と接触し
ない玉同志の接触により玉の自転数および公転数が減少
する。、このため、内輪と接触する玉にすべりが発生し
、高速回転のため摩擦により玉と内輪の温度が上昇し、
焼入硬さの低下あるいは異常摩耗および変形などの不具
合で軸受は正常に回転しなくなる。Therefore, the number of balls that come into contact with the inner ring decreases, and the number of rotations and revolutions of the balls decreases due to contact between balls that do not contact the inner ring. As a result, slipping occurs on the balls that come into contact with the inner ring, and due to high-speed rotation, the temperature of the balls and inner ring increases due to friction.
Bearings do not rotate normally due to problems such as a decrease in quenched hardness or abnormal wear and deformation.
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
。In addition to the type of magnetic bearing device in which a cylindrical rotor rotates around a fixed shaft as described above, there is also a type in which a rotor shaft rotates inside a cylindrical fixed case. In this case, protective bearings are provided at two locations on the upper and lower sides of the case, and when the shaft stops, the shaft contacts and is received by the inner ring of the protective bearing.
ところが、この場合には、停電その他の故障により磁気
軸受が作動しなくなったときに、高速で回転している軸
が保護用軸受の内輪に接触すると、内輪も高速で回転を
開始し、遠心力により内輪が膨張するため、軸受すきま
が減少して、完全な負すきまとなる。このため、高速回
転では玉同志が過大な力で接触することとなり、やはり
保護用軸受が損傷することがある。However, in this case, when the magnetic bearing stops working due to a power outage or other failure, if the shaft rotating at high speed comes into contact with the inner ring of the protective bearing, the inner ring also starts rotating at high speed, creating a centrifugal force. As the inner ring expands, the bearing clearance decreases and becomes completely negative. Therefore, at high speed rotation, the balls come into contact with each other with excessive force, which may also damage the protective bearing.
この発明の目的は、上記のような問題を解決した磁気軸
受装置を提供することにある。An object of the present invention is to provide a magnetic bearing device that solves the above problems.
問題点を解決するための手段
この発明による磁気軸受装置は、
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、回転部分の停止時に回転部分を受ける保護用軸受が
固定部分の複数箇所に設けられた磁気軸受装置において
、
保護用軸受が2個の玉軸受よりなり、保護用軸受の回転
部分側の軌道輪相互間に、遠心力により径方向外側に移
動して軸受すきまを調節しつる一体状または複数に分割
されたリング部材が設けられているものである。Means for Solving the Problems The magnetic bearing device according to the present invention supports a rotating part with a magnetic bearing in a non-contact state with respect to a fixed part, and a plurality of protective bearings that receive the rotating part when the rotating part is stopped are attached to a plurality of the fixed parts. In a magnetic bearing device installed at a location, the protective bearing consists of two ball bearings, and the bearing rings on the rotating part side of the protective bearing are moved radially outward by centrifugal force to adjust the bearing clearance. The ring member is provided with a ring member that is integral or divided into a plurality of parts.
作 用
停電その他の故障により回転部分が高速回転状態のまま
2個の玉軸受の軌道輪に接触すると、これらの軌道輪も
高速で回転を開始して遠心力により膨張するが、リング
部材も同時に回転を開始し、遠心力により径方向外側に
移動して軌道輪を軸方向に移動させ、軸受すきまを調節
する。また、遠心力に応じた力で軸受すきまを調節する
ことになるので、軸受すきまが過度に増大したり減少し
たりすることがなく、玉軸受は正常に作動し、損傷する
ことがない。If the rotating parts come into contact with the rings of the two ball bearings while rotating at high speed due to a power outage or other malfunction, these rings will also start rotating at high speed and expand due to centrifugal force, but the ring members will also expand at the same time. It starts rotating and moves radially outward due to centrifugal force, moving the bearing ring axially and adjusting the bearing clearance. Furthermore, since the bearing clearance is adjusted by a force corresponding to the centrifugal force, the bearing clearance will not increase or decrease excessively, and the ball bearing will operate normally and will not be damaged.
実 施 例
第1図および第2図は、固定軸(lO)の周囲を筒状の
ロータ(11)が回転する形式の磁気軸受装置に設けら
れた保護用軸受(12)の1例を示す。Embodiment Figures 1 and 2 show an example of a protective bearing (12) installed in a magnetic bearing device in which a cylindrical rotor (11) rotates around a fixed shaft (lO). .
この保護用軸受(12)は背面組合わせの2個の単列外
輪非分離アンギュラ総玉軸受(13)よりなる。2個の
軸受(13)の内輪(14)はスペーサ(15)を介し
て固定軸(10)に固定されている。2個の軸受(13
)の外輪(16)の対向端面は凸状に形成され、内側に
あって斜め内側を向くテーパ面(16a)と外側にあっ
て斜め外側に向くテーパ面(16b)が設けられている
。また、これらの対向端面の間には、円を4等分した形
のリング部材(17〉が挾まれている。リング部材(1
7)の外輪(1G)に対向する端面は凹状に形成され、
内側にあって外輪(16)のテーパ面(lea)に対向
する斜め外向きのテーパ面(17a)と外側にあって外
輪(16)のテーパ面(18b)に対向する斜め内向き
のテーパ面(17b)が設けられている。This protective bearing (12) consists of two single row outer ring non-separable angular full ball bearings (13) in a back-to-back combination. Inner rings (14) of the two bearings (13) are fixed to a fixed shaft (10) via a spacer (15). 2 bearings (13
The opposing end surfaces of the outer ring (16) of ) are formed in a convex shape, and are provided with an inner tapered surface (16a) facing diagonally inward and an outer tapered surface (16b) facing diagonally outward. Furthermore, a ring member (17) in the shape of a circle divided into four equal parts is sandwiched between these opposing end surfaces.
The end face facing the outer ring (1G) of 7) is formed in a concave shape,
A diagonally outward tapered surface (17a) on the inside facing the tapered surface (lea) of the outer ring (16), and a diagonally inward tapered surface located on the outside facing the tapered surface (18b) of the outer ring (16). (17b) is provided.
ロータ(11)が正常に回転している場合、ロータ(1
1)は図示しない磁気軸受により非接触状態に支持され
、ロータ(11)と軸受(12)の外輪(16)との間
には適当なすきまがあり、外輪(【6)は停止している
。このとき、リング部材(17)のテーパ面(1°γa
) (17b)が上下の外輪(16)の対応するテーパ
面(lea) (16b)に接触し、軸受(13)には
適当な予圧が与えられている。また、リング部材(17
)の凹状の部分が上下の外輪(16)の凸状の部分の間
に挾まれているので、リング部材(17)が脱落するこ
とがない。If the rotor (11) is rotating normally, the rotor (11)
1) is supported in a non-contact state by a magnetic bearing (not shown), there is an appropriate clearance between the rotor (11) and the outer ring (16) of the bearing (12), and the outer ring ([6) is stationary. . At this time, the tapered surface (1°γa
) (17b) are in contact with the corresponding tapered surfaces (lea) (16b) of the upper and lower outer rings (16), and an appropriate preload is applied to the bearing (13). In addition, a ring member (17
) is sandwiched between the convex portions of the upper and lower outer rings (16), so the ring member (17) does not fall off.
停電その他の故障により、高速で回転しているロータ(
11)が軸受(13)の外輪(IB)に接触すると、外
輪(lB)も高速で回転を開始して遠心力により膨張し
、軸受すきまが増大しようとする。Due to a power outage or other failure, the rotor (
11) comes into contact with the outer ring (IB) of the bearing (13), the outer ring (IB) also starts rotating at high speed and expands due to centrifugal force, increasing the bearing clearance.
ところが、これと同時に、リング部材(17)も高速で
回転を開始し、遠心力により径方向外側に移動して、テ
ーパ面(17a)で外輪(1B)を斜め外向きに押す。However, at the same time, the ring member (17) also starts rotating at high speed, moves radially outward due to centrifugal force, and pushes the outer ring (1B) obliquely outward with its tapered surface (17a).
これにより、2個の外輪(1G)は上下に離れる方向す
なわち軸受すきまを減少させる方向に移動し、軸受(1
3)には適当な予圧が負荷される。このため、玉(18
)が正常に自転して、軸受(13)が正常に作動し、焼
付ロックが生じて軸受(13)が損傷することはない。As a result, the two outer rings (1G) move vertically away from each other, that is, in the direction that reduces the bearing clearance, and the bearing (1G)
3) is loaded with an appropriate preload. For this reason, the ball (18
) rotates normally, the bearing (13) operates normally, and the bearing (13) will not be damaged due to seizure lock.
ロータ(11)の回転速度が徐々に低下して、遠心力に
よる外輪(1B)の膨張量が小さくなると、リング部材
(17)に働く遠心力も小さくなり、予圧荷重は小さく
なる。そして、ロータ(11)が停止したときには、軸
受(13)は元の状態に戻る。When the rotational speed of the rotor (11) gradually decreases and the amount of expansion of the outer ring (1B) due to centrifugal force decreases, the centrifugal force acting on the ring member (17) also decreases, and the preload load decreases. Then, when the rotor (11) stops, the bearing (13) returns to its original state.
磁気軸受装置の保護用軸受のうち、全ての箇所を上記の
保護用軸受(12)のようにしてもよいし、とくに損傷
を受は易い箇所だけを上記の保護用軸受(12)のよう
にしてもよい。Of the protective bearings of the magnetic bearing device, all parts may be made like the above-mentioned protective bearing (12), or only the parts that are particularly susceptible to damage may be made like the above-mentioned protective bearing (12). It's okay.
第3図は、上記と少し異なる保護用軸受(19)を示す
。なお、第3図において、第1図のものと同じ部分には
同一の符号を付している。FIG. 3 shows a protective bearing (19) that is slightly different from the one described above. In FIG. 3, the same parts as those in FIG. 1 are given the same reference numerals.
第3図の場合、2個の軸受(13)の外輪(16)の対
向端面の一部が凹状に形成され、内側にあって斜め外側
を向くテーパ面(lee)と外側にあって斜め内側を向
くテーパ面(lad)が設けられている。また、リング
部材(20)は断回路ひし形をなし、外輪(16)に対
向する端面には、内側にあって外輪(16)のテーパ面
(lee)に対向する斜め内向きのテーパ面(20a)
と外側にあって外輪(16)のテーパ面(led)に対
向する斜め外向きのテーパ面(20b)が設けられてい
る。他は第1図および第2図の場合と同様である。In the case of Fig. 3, parts of the opposing end surfaces of the outer rings (16) of the two bearings (13) are formed in a concave shape, with a tapered surface (lee) on the inside facing diagonally outward and a tapered surface (lee) on the outside facing diagonally inward. A tapered surface (lad) is provided that faces toward. The ring member (20) has a disconnected diamond shape, and the end face facing the outer ring (16) has an obliquely inward tapered face (20a) located on the inner side and opposite to the tapered face (lee) of the outer ring (16). )
A tapered surface (20b) facing diagonally outward is provided on the outside and facing the tapered surface (LED) of the outer ring (16). The rest is the same as in FIGS. 1 and 2.
第4図は、さらに上記と少し異なる保護用軸受(21)
を示す。なお、第4図において、第3図のものと同じ部
分には同一の符号を付している。Figure 4 shows a protective bearing (21) that is slightly different from the above.
shows. In FIG. 4, the same parts as those in FIG. 3 are given the same reference numerals.
第4図の場合、第3図のリング部材(20)のかわりに
断面円形のリング部材(22)が用いられている。他は
第3図の場合と同様である。In the case of FIG. 4, a ring member (22) having a circular cross section is used in place of the ring member (20) of FIG. 3. The rest is the same as in the case of FIG.
リング部材(17) (20) (22)は、金属、合
成樹脂、ゴムなどの適当な材料で作られる。また、テー
パ面の角度(くさび角度)は、遠心力による軸受すきま
の増減とくさび角度による外輪の軸方向移動量を考慮し
て、常に適当な予圧荷重が与えられるように設定される
。The ring members (17), (20), and (22) are made of a suitable material such as metal, synthetic resin, or rubber. Furthermore, the angle of the tapered surface (wedge angle) is set so that an appropriate preload is always applied, taking into consideration the increase or decrease in the bearing clearance due to centrifugal force and the amount of axial movement of the outer ring due to the wedge angle.
上記実施例では、円を複数に分割したリング部材を使用
しているが、完全な円形をなす一体状のリング部材また
はこれをltl所で切離したリング部材などを使用する
こともできる。In the above embodiment, a ring member having a circle divided into a plurality of parts is used, but it is also possible to use a completely circular integral ring member or a ring member obtained by cutting this ring member at the ltl point.
さらに、上記実施例はアンギュラ玉軸受に関するもので
あるが、実際使用時には軸受すきまによりある程度の接
触角がつく深みぞ玉軸受にも適用しうろことは言うまで
もない。Furthermore, although the above embodiments relate to angular contact ball bearings, it goes without saying that the present invention can also be applied to deep groove ball bearings in which a certain degree of contact angle occurs due to the bearing clearance during actual use.
発明の効果
この発明の磁気軸受装置によれば、上述のように、保護
用軸受の損傷を確実に防止することができる。また、2
個の玉軸受とリング部材を使用するだけでよく、従来の
ものに比べて構造がさほど複雑になることもない。Effects of the Invention According to the magnetic bearing device of the present invention, damage to the protective bearing can be reliably prevented as described above. Also, 2
It only requires the use of individual ball bearings and ring members, and the structure is not much more complicated than conventional ones.
第1図はこの発明の1実施例を示す磁気軸受装置の保護
用軸受の部分の縦断面図、第2図は第1図■−■線の断
面図、第3図はこの発明の他の実施例を示す第1図相当
の図面、第4図はこの発明のさらに他の実施例を示す第
1図相当の図面、第5図は従来の磁気軸受装置を示す縦
断面図である。
(lO)・・・固定軸、(11)・・・ロータ、(12
) (19) (21)・・・保護用軸受、(13)・
・・アンギュラ総玉軸受、(17) (20) (22
)・・・リング部材。
以 上FIG. 1 is a longitudinal cross-sectional view of a protective bearing portion of a magnetic bearing device showing one embodiment of the present invention, FIG. 2 is a cross-sectional view taken along line ■-■ in FIG. 1, and FIG. FIG. 4 is a drawing corresponding to FIG. 1 showing an embodiment of the present invention, FIG. 4 is a drawing corresponding to FIG. 1 showing still another embodiment of the present invention, and FIG. 5 is a longitudinal sectional view showing a conventional magnetic bearing device. (lO)...Fixed shaft, (11)...Rotor, (12
) (19) (21)...protective bearing, (13)...
...Angular full ball bearing, (17) (20) (22
)...Ring member. that's all
Claims (1)
し、回転部分の停止時に回転部分を受ける保護用軸受が
固定部分の複数箇所に設けられた磁気軸受装置において
、 保護用軸受が2個の玉軸受よりなり、保護用軸受の回転
部分側の軌道輪相互間に、遠心力により径方向外側に移
動して軸受すきまを調節しうる一体状または複数に分割
されたリング部材が設けられている磁気軸受装置。[Scope of Claims] A magnetic bearing device in which a rotating part is supported by magnetic bearings in a non-contact state with respect to a fixed part, and protective bearings are provided at a plurality of locations on the fixed part to receive the rotating part when the rotating part is stopped, The protective bearing consists of two ball bearings, and between the bearing rings on the rotating part side of the protective bearing, there is a bearing ring that can be moved radially outward by centrifugal force to adjust the bearing clearance. A magnetic bearing device provided with a ring member.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP31370086A JPH0788849B2 (en) | 1986-12-26 | 1986-12-26 | Magnetic bearing device |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP31370086A JPH0788849B2 (en) | 1986-12-26 | 1986-12-26 | Magnetic bearing device |
Publications (2)
Publication Number | Publication Date |
---|---|
JPS63167120A true JPS63167120A (en) | 1988-07-11 |
JPH0788849B2 JPH0788849B2 (en) | 1995-09-27 |
Family
ID=18044464
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP31370086A Expired - Fee Related JPH0788849B2 (en) | 1986-12-26 | 1986-12-26 | Magnetic bearing device |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPH0788849B2 (en) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH01179116A (en) * | 1988-01-08 | 1989-07-17 | Minolta Camera Co Ltd | Zoom lens |
JPH0293517U (en) * | 1989-01-13 | 1990-07-25 | ||
JPH04249616A (en) * | 1990-12-29 | 1992-09-04 | Nagano Nippon Densan Kk | Bearing structure body and spindle motor using the same |
CN103912589A (en) * | 2014-03-25 | 2014-07-09 | 南京航空航天大学 | Centripetal thrust protection bearing device for automatically eliminating clearance |
-
1986
- 1986-12-26 JP JP31370086A patent/JPH0788849B2/en not_active Expired - Fee Related
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH01179116A (en) * | 1988-01-08 | 1989-07-17 | Minolta Camera Co Ltd | Zoom lens |
JPH0293517U (en) * | 1989-01-13 | 1990-07-25 | ||
JPH04249616A (en) * | 1990-12-29 | 1992-09-04 | Nagano Nippon Densan Kk | Bearing structure body and spindle motor using the same |
CN103912589A (en) * | 2014-03-25 | 2014-07-09 | 南京航空航天大学 | Centripetal thrust protection bearing device for automatically eliminating clearance |
Also Published As
Publication number | Publication date |
---|---|
JPH0788849B2 (en) | 1995-09-27 |
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Legal Events
Date | Code | Title | Description |
---|---|---|---|
LAPS | Cancellation because of no payment of annual fees |