JP2524835Y2 - Radial bearing device - Google Patents
Radial bearing deviceInfo
- Publication number
- JP2524835Y2 JP2524835Y2 JP178691U JP178691U JP2524835Y2 JP 2524835 Y2 JP2524835 Y2 JP 2524835Y2 JP 178691 U JP178691 U JP 178691U JP 178691 U JP178691 U JP 178691U JP 2524835 Y2 JP2524835 Y2 JP 2524835Y2
- Authority
- JP
- Japan
- Prior art keywords
- bearing
- present
- rings
- radial bearing
- radial
- 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 - Fee Related
Links
Landscapes
- Magnetic Bearings And Hydrostatic Bearings (AREA)
- Sliding-Contact Bearings (AREA)
- Support Of The Bearing (AREA)
- Vibration Prevention Devices (AREA)
Description
【０００１】[0001]
【産業上の利用分野】本考案は、コンプレッサ、タービ
ン、真空ポンプ等の高速回転体を支持する玉軸受、気体
軸受、流体軸受等のラジアル軸受装置の改良に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to improvements in radial bearing devices such as ball bearings, gas bearings, and fluid bearings for supporting high-speed rotating bodies such as compressors, turbines, and vacuum pumps.
【０００２】[0002]
【従来の技術】図６に従来の軸受装置の１例を示す。軸
受の例として、静圧型と動圧型を組み合わせた複合型気
体軸受が図６に示されている。回転軸１は気体軸受２で
回転自在に支持される。気体軸受２には、複数の溝３
ａ，３ｂが設けてあり、回転軸１が、高速回転すること
で動圧が発生し回転軸１を支持する。また、複数の給気
口４を気体軸受２に配置し、圧縮気体を給気口６から給
気することで静圧が発生し同様に回転軸１を支持する。2. Description of the Related Art FIG. 6 shows an example of a conventional bearing device. As an example of the bearing, FIG. 6 shows a composite gas bearing combining a static pressure type and a dynamic pressure type. The rotating shaft 1 is rotatably supported by a gas bearing 2. The gas bearing 2 has a plurality of grooves 3
a and 3b are provided, and when the rotating shaft 1 rotates at a high speed, a dynamic pressure is generated to support the rotating shaft 1. In addition, a plurality of air supply ports 4 are arranged in the gas bearing 2, and a compressed gas is supplied from the air supply port 6 to generate a static pressure, thereby similarly supporting the rotary shaft 1.
【０００３】気体軸受２の外周部と軸受のハウジング７
の半径方向隙間にはＯリング５ａ，５ｂ，５ｃ，５ｄを
複数個配置されている。前記Ｏリングは、通常、ニトリ
ルゴム等の有機物弾性材からなり、回転軸１から気体軸
受２に伝達される振動を減衰させる役割を有する。ま
た、Ｎは回転軸１の回転方向、Ａは静圧の給気方向を示
す。[0003] Outer peripheral portion of gas bearing 2 and bearing housing 7
A plurality of O-rings 5a, 5b, 5c, 5d are arranged in the radial gap. The O-ring is generally made of an organic elastic material such as nitrile rubber, and has a role of attenuating vibration transmitted from the rotating shaft 1 to the gas bearing 2. N indicates the rotation direction of the rotary shaft 1, and A indicates the static pressure air supply direction.
【０００４】[0004]
【考案が解決しようとする課題】前記の従来の静圧型と
動圧型を組み合わせた複合型気体軸受の場合、静圧給気
は、低回転数域でのみ補助的に行い、通常の運転時（高
速回転時）には、静圧給気を止め、動圧効果のみにより
回転軸を支持する。In the case of the above-mentioned composite type gas bearing combining the conventional static pressure type and the dynamic pressure type, static pressure air supply is performed only in a low rotational speed range, and during normal operation ( During high-speed rotation), the static pressure air supply is stopped, and the rotating shaft is supported only by the dynamic pressure effect.
【０００５】この場合、動圧効果による軸受負荷能力
は、回転軸１と気体軸受２と隙間の３乗に比例して増大
するが、中回転数域において、回転軸を組み込み可能な
隙間では、軸受負荷能力は不十分である。そのため、回
転軸１を支持できる軸受負荷能力が生じるまで回転軸１
が半径方向にドリフトした状態で周方向に回転移動し、
一定固有振動数の不安定振動、即ち、ホワールが発生し
てしまう。In this case, the bearing load capacity due to the dynamic pressure effect increases in proportion to the cube of the gap between the rotating shaft 1 and the gas bearing 2. The bearing load capacity is insufficient. Therefore, until the bearing load capacity capable of supporting the rotating shaft 1 is generated, the rotating shaft 1
Rotates in the circumferential direction while drifting in the radial direction,
Unstable vibration with a constant natural frequency, that is, whirl occurs.
【０００６】また、高速回転数域においては回転軸１と
気体軸受２との隙間での気体の周方向速度が大きく、そ
の速度に対応した気体の粘性による周方向力が回転軸１
に作用し、回転軸１を振れ廻し、同様なホワールが発生
してしまう。In the high speed range, the circumferential speed of the gas in the gap between the rotating shaft 1 and the gas bearing 2 is large, and the circumferential force due to the viscosity of the gas corresponding to the speed is large.
, Causing the rotating shaft 1 to oscillate, and a similar whirl occurs.
【０００７】この不安定振動、即ち、ホワールは、軸受
の剛性を小さくし、減衰効果を大きくすることで制振さ
せることが可能である。This unstable vibration, that is, whirl, can be suppressed by reducing the rigidity of the bearing and increasing the damping effect.
【０００８】しかし、前記の従来の複合型気体軸受のよ
うに有機物弾性材からなるＯリングのみを用いる場合、
剛性と減衰効果は比例関係にあり、同時に、剛性を小さ
くし、減衰効果を大きくすることはできない。また、剛
性を小さくしすぎると、軸受組み込み時に、同軸度、直
角度等の必要精度を保つことができなくなる。However, when only the O-ring made of an organic elastic material is used as in the above-mentioned conventional composite gas bearing,
The stiffness and the damping effect are in a proportional relationship, and at the same time, the stiffness cannot be reduced and the damping effect cannot be increased. On the other hand, if the rigidity is too small, it is not possible to maintain the required accuracy such as coaxiality and squareness when the bearing is assembled.
【０００９】本考案は、以上に鑑みて、剛性を低下させ
ることなく減衰効果を大きくしたラジアル軸受装置を提
供しようとするものである。The present invention has been made in view of the above, and an object of the present invention is to provide a radial bearing device in which the damping effect is increased without reducing rigidity.
【００１０】[0010]
【課題を解決するための手段】１ 本考案のラジアル軸
受装置は、回転体を支持するラジアル軸受において、弾
性材からなる円筒状リングを軸方向に配置し、同リング
の一端を軸受の軸方向端面に取付け、他端を軸受ハウジ
ングに設けられた押えディスクに取付けた。 ２ また本考案のラジアル軸受装置は、前記１の考案に
おいて、前記リングを周方向に複数に分割した。 ３ また本考案のラジアル軸受装置は、前記１の考案に
おいて、前記リングを複数個ほぼ同心状に配置し、前記
リング間の隙間に粘性の高い流体を充填した。A radial bearing device according to the present invention is a radial bearing for supporting a rotating body, in which a cylindrical ring made of an elastic material is arranged in an axial direction, and one end of the ring is connected to the axial direction of the bearing. It was attached to the end face, and the other end was attached to a holding disk provided in the bearing housing. 2 In the radial bearing device according to the present invention, the ring is divided into a plurality in the circumferential direction in the first invention. 3. In the radial bearing device of the present invention, in the first invention, a plurality of the rings are arranged substantially concentrically, and a gap between the rings is filled with a highly viscous fluid.
【００１１】[0011]
【作用】前記１の本考案では、軸受の軸方向端面と軸受
ハウジングに設けられた押えディスクに両端が取付けら
れた弾性材からなる円筒状リングは、そのせん断変形を
利用しているため、圧縮変形に比べ材料力学的にも剛性
の増加は小さく、また、前記円筒状リングの軸方向長さ
を長くすることで弾性体内部減衰効果が大きくなる。さ
らに、同リングの材質として剛性が小さく、振動吸収性
の高いものを選定することにより、より制振効果を大き
くでき。これによって、前記の不安定振動、即ち、ホワ
ールの発生を防止することが可能となる。According to the first aspect of the present invention, since the cylindrical ring made of an elastic material having both ends attached to the axial end surface of the bearing and the holding disk provided in the bearing housing utilizes its shear deformation, it is compressed. The increase in rigidity is small in material mechanics as compared with the deformation, and by increasing the axial length of the cylindrical ring, the internal damping effect of the elastic body is increased. Further, by selecting a material of the ring having low rigidity and high vibration absorption, the vibration damping effect can be further enhanced. This makes it possible to prevent the above-mentioned unstable vibration, that is, the generation of whirl.
【００１２】前記２の本考案では、円筒状リングを周方
向に複数に分割することによって、ラジアル剛性が低下
し、かつ内部減衰効果を維持することができる。In the second aspect of the present invention, by dividing the cylindrical ring into a plurality in the circumferential direction, the radial rigidity is reduced and the internal damping effect can be maintained.
【００１３】前記３の本考案では、ほぼ同心状に配置し
た円筒状リング間の隙間に粘性の高い流体を充填したこ
とによって、同流体のスクイズ効果によって減衰作用が
増大して、前記の不安定振動の制振が効果的に行なわれ
る。According to the third aspect of the present invention, the gap between the cylindrical rings arranged substantially concentrically is filled with a highly viscous fluid, so that the damping action is increased by the squeeze effect of the fluid, and the unstable state is increased. Vibration is effectively suppressed.
【００１４】[0014]
【実施例】本考案の第１の実施例を、図１によって説明
する。本実施例は、図６に示す従来の装置において、以
下説明する円筒状リングを設けたものであり、同一の部
分は、図１において図６におけると同一の符号が付せら
れており、その説明を省略する。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A first embodiment of the present invention will be described with reference to FIG. In the present embodiment, a cylindrical ring described below is provided in the conventional device shown in FIG. 6, and the same portions are denoted by the same reference numerals in FIG. 1 as in FIG. Description is omitted.
【００１５】円筒状リング１８，１９は、振動吸収性の
高いゴム（弾性材）でできており、その各々の両端は、
ラジアル気体軸受２の両端面に設けた溝及び軸受のハウ
ジング７に取付けられた押さえディスク１１０，１１１
に設けた溝に嵌め込まれ、適当な押さえ込み量で圧縮さ
れている。また、円筒状リングの１８，１９の肉厚を薄
くし、軸方向長さを適当な長さとなるよう設定されてい
る。The cylindrical rings 18 and 19 are made of rubber (elastic material) having high vibration absorption, and both ends thereof are
Grooves provided on both end surfaces of the radial gas bearing 2 and holding disks 110 and 111 attached to the housing 7 of the bearing.
And compressed by an appropriate amount of pressing. Further, the thickness of the cylindrical rings 18 and 19 is reduced, and the axial length is set to an appropriate length.
【００１６】本実施例では、ラジアル気体軸受２がラジ
アル方向に振動すると円筒状リング１８，１９はせん断
変形し、振動エネルギを吸収し減衰効果を発揮すること
ができる。この際、同円筒状リング１８，１９は、振動
吸収性の高いゴムの肉厚を薄くし軸方向長さを適当な長
さとしてせん断変形を利用しているために、剛性が小さ
く内部減衰効果を大きくすることができ、回転軸１の不
安定振動、即ちホワールを効果的に制振することができ
る。In the present embodiment, when the radial gas bearing 2 vibrates in the radial direction, the cylindrical rings 18 and 19 undergo shear deformation, absorb vibration energy and exhibit a damping effect. At this time, the cylindrical rings 18 and 19 have a small rigidity because the thickness of the rubber having high vibration absorption is made thin and the axial length is made an appropriate length to utilize shear deformation. Can be increased, and unstable vibration of the rotating shaft 1, that is, whirl can be effectively damped.
【００１７】本考案の第２の実施例を、図２によって説
明する。本実施例は、前記第１の実施例に高粘性流体を
併用したものに相当する。A second embodiment of the present invention will be described with reference to FIG. This embodiment corresponds to a combination of the first embodiment and a high-viscosity fluid.
【００１８】円筒状リング１８，１９の内側に、同心の
内側円筒状リング２１２，２１３を加え、複数個の円筒
状リングが設けられている。前記内側円筒状リング２１
２，２１３は、軸受ハウジング７に取付けられた溝に嵌
め込まれ、適当な押さえ込み量で圧縮されている。Inside the cylindrical rings 18 and 19, concentric inner cylindrical rings 212 and 213 are added, and a plurality of cylindrical rings are provided. The inner cylindrical ring 21
Reference numerals 2 and 213 are fitted into grooves mounted on the bearing housing 7 and are compressed with an appropriate pressing amount.
【００１９】さらに、前記円筒状リング間及びＯリング
５ａ，５ｄ間に、高粘性流体２１４，２１５を充填し、
流体のスクイズ効果による減衰効果も付加し、より制振
効果を大きくしている。Further, high viscosity fluids 214 and 215 are filled between the cylindrical rings and between the O-rings 5a and 5d.
The damping effect by the squeeze effect of the fluid is also added, and the damping effect is further increased.
【００２０】本実施例では、ラジアル気体軸受２がラジ
アル方向に振動すると円筒状リング１８，１９及び内側
円筒状リング２１２，２１３がせん断変形し、振動エネ
ルギを吸収するとともに、高粘性流体２１４，２１５が
各円筒状リングのせん断変形とともに移動することで、
振動エネルギが高粘性流体に吸収され、また、円筒状リ
ング表面の高粘性流体の流れ変動によるスクイズ効果に
よる減衰効果も付加し、より大きな制振効果が生じる。In this embodiment, when the radial gas bearing 2 vibrates in the radial direction, the cylindrical rings 18 and 19 and the inner cylindrical rings 212 and 213 undergo shear deformation to absorb vibration energy, and at the same time to absorb high-viscosity fluids 214 and 215. Moves along with the shear deformation of each cylindrical ring,
Vibration energy is absorbed by the high-viscosity fluid, and a damping effect by a squeeze effect due to the flow fluctuation of the high-viscosity fluid on the surface of the cylindrical ring is added.
【００２１】本考案の第３の実施例を、図３によって説
明する。本実施例は、前記第１の実施例の円筒状リング
１８，１９を周方向に複数個分割し、より剛性の増加を
小さくしたものである。即ち、本実施例では、前記第１
の実施例の円筒状リング１８，１９に相当する気体軸受
２と押さえディスク１１０，１１１に取付けられた円筒
状リング３８，３９は、その同方向に複数に分割されて
いる。A third embodiment of the present invention will be described with reference to FIG. In this embodiment, the cylindrical rings 18 and 19 of the first embodiment are divided into a plurality in the circumferential direction to further reduce the increase in rigidity. That is, in the present embodiment, the first
The gas bearing 2 corresponding to the cylindrical rings 18 and 19 of this embodiment and the cylindrical rings 38 and 39 attached to the holding disks 110 and 111 are divided into a plurality in the same direction.
【００２２】回転軸及び軸受全体を考慮した回転安定性
を高めるには、軸受剛性を極力小さくし、減衰係数を大
きくする必要があり、円筒状リングで形成されるせん断
力を利用したダンパの剛性は極力小さくした方がよい。
そこで、本実施例では、円筒状リングの剛性のみを下
げ、減衰係数の低下はないようにするために円筒状リン
グ３８，３９を周方向に複数個分割している。前記第１
の実施例の円筒状リング１８，１９は一体構造体である
ため、周方向で力が発生し、ラジアル力が大きくなる
が、本実施例のように、円筒状リング３８，３９を分割
すれば、その周方向力はなくなり、ラジアル剛性を小さ
くすることができると共に、減衰係数を維持することが
できる。In order to increase the rotational stability in consideration of the rotating shaft and the entire bearing, it is necessary to minimize the bearing rigidity and increase the damping coefficient. The rigidity of the damper utilizing the shear force formed by the cylindrical ring is required. Should be as small as possible.
Therefore, in the present embodiment, a plurality of cylindrical rings 38 and 39 are divided in the circumferential direction in order to reduce only the rigidity of the cylindrical ring and prevent the reduction of the damping coefficient. The first
Since the cylindrical rings 18 and 19 of this embodiment are an integral structure, a force is generated in the circumferential direction and the radial force increases. However, if the cylindrical rings 38 and 39 are divided as in this embodiment, The circumferential force is eliminated, so that the radial rigidity can be reduced and the damping coefficient can be maintained.
【００２３】本考案の第４の実施例を、図４によって説
明する。本実施例では、前記第３の実施例の分割された
円筒状リング３８，３９に相当する気体軸受２と押さえ
ディスク１１０，１１１に取付けられた円筒状リング４
８，４９の肉厚を厚くし、その減衰係数を大きくしたも
のである。A fourth embodiment of the present invention will be described with reference to FIG. In this embodiment, the gas bearing 2 corresponding to the divided cylindrical rings 38 and 39 of the third embodiment and the cylindrical ring 4 attached to the holding discs 110 and 111 are used.
8, 49, and the damping coefficient thereof is increased.
【００２４】図５に、本考案を実際に試験機に組み込
み、その制振効果を確認した例を示す。横軸に回転数、
縦軸にホワール振幅をとり、動圧効果のみで回転軸を支
持したまま、昇速した場合のホワール制振効果を円筒状
リングよりなるダンパの条件をパラメータに整理したも
のである。FIG. 5 shows an example in which the present invention is actually incorporated into a testing machine and its vibration damping effect is confirmed. Rotation speed on the horizontal axis,
The whirl amplitude is plotted on the vertical axis, and the whirl vibration damping effect when the speed is increased while the rotating shaft is supported only by the dynamic pressure effect is arranged by using the condition of the damper composed of the cylindrical ring as a parameter.
【００２５】シェアダンパの制振効果（振動減衰効果）
は、 制振効果＝比例係数×（弾性材ゴム素材減衰能Ｅ）×
（円筒状リングの肉厚Ｔ）×（軸方向長さＬ）×（圧縮
変形量δ）×（分割個数Ｎ）で表わされる。The damping effect of the shear damper (vibration damping effect)
Is: Damping effect = proportional coefficient x (elastic rubber material damping capacity E) x
(Thickness T of cylindrical ring) × (Length in axial direction L) × (Compression deformation amount δ) × (Number of divisions N).
【００２６】本試験に用いた各例では、弾性材ゴム素材
減衰能を一定にし、円筒状リングの肉厚Ｔを３ｍｍ〜５
ｍｍ、軸方向長さＬを５ｍｍ〜１０ｍｍ、圧縮変形量δ
を０．５ｍｍ〜２．０ｍｍ、分割個数Ｎを０〜１０の範
囲で変えている。これを条件１〜条件３のグラフに示
す。また、図５に示す最適条件では、円筒状リングの肉
厚Ｔを５ｍｍ、軸方向長さＬを１０ｍｍ、圧縮変形量δ
を１．０ｍｍ、分割個数Ｎを８とした。この場合には、
図５に示すように、ホワール振幅は０μｍP-P となり、
完全にホワールを防止することができた。In each of the examples used in this test, the damping capacity of the elastic rubber material was fixed, and the thickness T of the cylindrical ring was 3 mm to 5 mm.
mm, the axial length L is 5 mm to 10 mm, and the amount of compressive deformation δ
Is changed in the range of 0.5 mm to 2.0 mm, and the number of divisions N is changed in the range of 0 to 10. This is shown in the graphs of Condition 1 to Condition 3. Under the optimum conditions shown in FIG. 5, the thickness T of the cylindrical ring is 5 mm, the axial length L is 10 mm, and the amount of compressive deformation δ
Was set to 1.0 mm, and the number of divisions N was set to 8. In this case,
As shown in FIG. 5, the Whirl amplitude is 0 μm PP ,
Whirl was completely prevented.
【００２７】[0027]
【考案の効果】以上説明したように、請求項１の本考案
は、軸受の軸方向端面と軸受ハウジングに設けられた押
さえディスクに両端が取付けられ軸方向に配置された円
筒状リングを用いたことによって、剛性を小さくし、振
動の減衰効果を増大させることができ、回転軸のホワー
ルの発生を防止することができる。As described above, the present invention of claim 1 uses a cylindrical ring having both ends attached to an axial end face of a bearing and a holding disk provided in a bearing housing and arranged axially. Thus, the rigidity can be reduced, the vibration damping effect can be increased, and the occurrence of whirling of the rotating shaft can be prevented.
【００２８】請求項２の本考案は、請求項１の本考案に
おいて、円筒状リングを周方向に複数に分割することに
よって、減衰効果を維持し、かつラジアル剛性を低下さ
せ、前記ホワールの発生の防止に更に効果がある。According to a second aspect of the present invention, in accordance with the first aspect of the present invention, by dividing the cylindrical ring into a plurality of pieces in the circumferential direction, the damping effect is maintained, the radial rigidity is reduced, and the generation of the whirl is reduced. It is even more effective in preventing
【００２９】請求項３の本考案は、請求項１の本考案に
おいて、ほぼ同心状に配置された複数の円筒状リングの
隙間に粘性の高い流体を充填することによって、流体の
スクイズ効果によって減衰効果が増大し、ホワールの制
振を更に効果的に行なうことができる。According to a third aspect of the present invention, in the first aspect of the present invention, a gap between a plurality of cylindrical rings arranged substantially concentrically is filled with a highly viscous fluid, whereby the fluid is damped by the squeezing effect of the fluid. The effect is increased, and the whirl can be more effectively damped.
【図１】本考案の第１の実施例を示し、 (ａ) はその断
面図， (ｂ) は図１（ａ）のＩ−Ｉ矢視断面図である。FIGS. 1A and 1B show a first embodiment of the present invention, wherein FIG. 1A is a cross-sectional view thereof, and FIG. 1B is a cross-sectional view taken along line II of FIG. 1A.
【図２】本考案の第２の実施例を示し、（ａ）はその断
面図，（ｂ）は図２（ａ）のII−II矢視断面図である。2A and 2B show a second embodiment of the present invention, wherein FIG. 2A is a cross-sectional view thereof, and FIG. 2B is a cross-sectional view taken along the line II-II of FIG. 2A.
【図３】本考案の第３の実施例を示し、（ａ）はその断
面図，（ｂ）は図３（ａ）のIII −III 矢視断面図であ
る。3A and 3B show a third embodiment of the present invention, wherein FIG. 3A is a sectional view thereof, and FIG. 3B is a sectional view taken along the line III-III of FIG. 3A.
【図４】本考案の第４の実施例を示し、（ａ）はその断
面図，（ｂ）は図４（ａ）のIV−IV矢視断面図である。4A and 4B show a fourth embodiment of the present invention, wherein FIG. 4A is a sectional view thereof, and FIG. 4B is a sectional view taken along the line IV-IV of FIG. 4A.
【図５】本考案の軸受装置の試験結果を示すグラフであ
る。FIG. 5 is a graph showing test results of the bearing device of the present invention.
【図６】従来の軸受装置の１例の断面図である。FIG. 6 is a sectional view of an example of a conventional bearing device.
１ 回転軸 ２ 気体軸受 ７ 軸受のハウジング １８，１９，３８，３９，４８，４９，２１２，２１３
円筒状リング １１０，１１１ 押さえディスク ２１４，２１５ 高粘性流体DESCRIPTION OF SYMBOLS 1 Rotating shaft 2 Gas bearing 7 Housing of bearing 18, 19, 38, 39, 48, 49, 212, 213
Cylindrical ring 110, 111 Holding disk 214, 215 High viscous fluid
───────────────────────────────────────────────────── フロントページの続き (51)Int.Cl.6 識別記号 庁内整理番号 ＦＩ 技術表示箇所 Ｆ１６Ｆ 15/02 8917−3Ｊ Ｆ１６Ｆ 15/02 Ｆ 15/08 8917−3Ｊ 15/08 Ｇ ──────────────────────────────────────────────────続 き Continued on the front page (51) Int.Cl. 6 Identification code Agency reference number FI Technical display location F16F 15/02 8917-3J F16F 15/02 F 15/08 8917-3J 15/08 G
Claims (3)
て、弾性材からなる円筒状リングを軸方向に配置し、同
リングの一端を軸受の軸方向端面に取付け、他端を軸受
ハウジングに設けられた押さえディスクに取付けたこと
を特徴とするラジアル軸受装置。In a radial bearing for supporting a rotating body, a cylindrical ring made of an elastic material is arranged in an axial direction, one end of the ring is attached to an axial end face of the bearing, and the other end is provided in a bearing housing. A radial bearing device mounted on a holding disc.
とを特徴とする請求項１に記載のラジアル軸受装置。2. The radial bearing device according to claim 1, wherein the ring is divided into a plurality in the circumferential direction.
し、前記リング間の隙間に粘性の高い流体を充填したこ
とを特徴とする請求項１に記載のラジアル軸受装置。3. The radial bearing device according to claim 1, wherein a plurality of the rings are arranged substantially concentrically, and a gap between the rings is filled with a highly viscous fluid.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP178691U JP2524835Y2 (en) | 1991-01-24 | 1991-01-24 | Radial bearing device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP178691U JP2524835Y2 (en) | 1991-01-24 | 1991-01-24 | Radial bearing device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0499416U JPH0499416U (en) | 1992-08-27 |
| JP2524835Y2 true JP2524835Y2 (en) | 1997-02-05 |
Family
ID=31729392
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP178691U Expired - Fee Related JP2524835Y2 (en) | 1991-01-24 | 1991-01-24 | Radial bearing device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2524835Y2 (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2543159Y2 (en) * | 1991-04-26 | 1997-08-06 | 光洋精工株式会社 | Bearing device |
| JP6804231B2 (en) * | 2016-08-04 | 2020-12-23 | Ntn株式会社 | Air turbine drive spindle |
-
1991
- 1991-01-24 JP JP178691U patent/JP2524835Y2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0499416U (en) | 1992-08-27 |
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