JPH02142919A - Squeeze bearing - Google Patents
Squeeze bearingInfo
- Publication number
- JPH02142919A JPH02142919A JP29241888A JP29241888A JPH02142919A JP H02142919 A JPH02142919 A JP H02142919A JP 29241888 A JP29241888 A JP 29241888A JP 29241888 A JP29241888 A JP 29241888A JP H02142919 A JPH02142919 A JP H02142919A
- Authority
- JP
- Japan
- Prior art keywords
- rotor
- vibrator
- electrodes
- sphere
- 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.)
- Pending
Links
- 230000003746 surface roughness Effects 0.000 claims abstract description 10
- 238000010586 diagram Methods 0.000 description 6
- 230000000694 effects Effects 0.000 description 2
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
- F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion 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
- F16C32/00—Bearings not otherwise provided for
- F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
- F16C32/0603—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a gas cushion, e.g. an air cushion
- F16C32/0607—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a gas cushion, e.g. an air cushion the gas being retained in a gap, e.g. squeeze film bearings
- F16C32/0611—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a gas cushion, e.g. an air cushion the gas being retained in a gap, e.g. squeeze film bearings by means of vibrations
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (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]
本発明は、回転子を、高周波振動する振動子を用い、回
転子と振動子の微小の隙間に発生する正圧空気膜により
非接触支持するスクイーズ軸受に関する。Detailed Description of the Invention [Industrial Application Field] The present invention uses a vibrator that vibrates at a high frequency to support a rotor in a non-contact manner by a positive pressure air film generated in a minute gap between the rotor and the vibrator. related to squeeze bearings.
[従来の技術] 第10図はスクィーズ軸受の原理を説明する図である。[Conventional technology] FIG. 10 is a diagram explaining the principle of a squeeze bearing.
可動子21と振動子22を面粗さが小さい面同志を対向
させて配置し、振動子22を高周波振動させると、空気
の粘性と圧縮性および可動子21の慣性によって空気膜
23が形成され、可動子21が振動子22に非接触で支
持される。When the movable element 21 and the vibrator 22 are arranged with their surfaces with small surface roughness facing each other and the vibrator 22 is vibrated at a high frequency, an air film 23 is formed due to the viscosity and compressibility of air and the inertia of the movable element 21. , the movable element 21 is supported by the vibrator 22 in a non-contact manner.
第11図はスクィーズ軸受の従来の概略図である。FIG. 11 is a schematic diagram of a conventional squeeze bearing.
回転子24は中空円筒状のラジアル支持用振動子25内
に配置され、回転子24の両端面にはある隙間をもって
スラスト支持用振動子26.27が配置されており、振
動子25,26.27を高周波振動させることにより、
回転子24と振動子25 26.27の間に周囲よりも
高い圧力の空気膜28,29.30が形成され、回転子
24は振動子25,26.27に非接触支持される。The rotor 24 is disposed within a hollow cylindrical radial support vibrator 25, and thrust support vibrators 26, 27 are disposed on both end faces of the rotor 24 with a certain gap between them. By making 27 vibrate at high frequency,
An air film 28, 29.30 having a pressure higher than that of the surroundings is formed between the rotor 24 and the vibrator 25, 26.27, and the rotor 24 is supported by the vibrator 25, 26.27 in a non-contact manner.
[発明が解決しようとする課題]
上述した従来のスクィーズ軸受は、回転子を非接触支持
するためには回転子と振動子の間の隙間はミクロンオー
ダではなくてはならず、したがって回転子と振動子の互
いに対向する面は面粗さを小さく仕上げなければならな
いことは勿論、相互の組立精度も操めて正確でなれけば
ならないため、高価になるという欠点がある。[Problems to be Solved by the Invention] In the conventional squeeze bearing described above, in order to support the rotor in a non-contact manner, the gap between the rotor and the vibrator must be on the order of microns. The mutually opposing surfaces of the vibrators must be finished with minimal surface roughness, and the mutual assembly precision must also be manipulated to ensure accuracy, which has the disadvantage of being expensive.
[課題を解決するための手段]
本発明のスクィーズ軸受は、
柱状で、少なくとも一方の端面に、表面粗さが小さく球
の一部の形をなす凹部または凸部を、核球の中心が軸線
上に位置するように有する回転子と、
回転子の各端面と対向して設けられ、表面粗さが小さい
平面あるいは曲面であって、前記回転子の端面が平坦な
場合には平坦な凹部が設けられている場合には該凹部の
球より小さい球の一部の形の凸部の、凸部が設けられて
いる場合(こは該凸部の球より大きい球の一部の形の凹
部の振動面を、回転子の端面とある隙間を保って有する
振動子とを含む9
[作用]
回転子の少なくとも一方の端面に1球状の凹部あるいは
凸部を形成し、これと対向する振動子の振動面も凸部ま
たは凹部とすることにより、組立精度が厳しくなくても
よく、また部品点数も減るため、安価になる。[Means for Solving the Problems] The squeeze bearing of the present invention is columnar, and has a concave or convex portion in the shape of a part of a sphere with small surface roughness on at least one end surface, so that the center of the core sphere is the axis. A rotor positioned on a line, and a flat or curved surface with small surface roughness provided opposite each end face of the rotor, and if the end face of the rotor is flat, a flat recess is provided. If a convex part is provided, the convex part is in the shape of a part of a sphere smaller than the sphere of the concave part. [Operation] A spherical concave or convex portion is formed on at least one end surface of the rotor, and a vibrator facing this By making the vibration surface also a convex portion or a concave portion, assembly accuracy does not need to be strict and the number of parts is reduced, resulting in lower cost.
次に、本発明の実施例について図面を参照して説明する
。Next, embodiments of the present invention will be described with reference to the drawings.
第1図は本発明のスクィーズ軸受の第1の実施例の斜視
図、第2図はその縦断面図、第3図は振動子2の内面図
、第4図は振動子2の振動モードを示す図である。FIG. 1 is a perspective view of the first embodiment of the squeeze bearing of the present invention, FIG. 2 is a longitudinal sectional view thereof, FIG. 3 is an inner view of the vibrator 2, and FIG. 4 is a diagram showing the vibration mode of the vibrator 2. FIG.
回転子10両端面には表面粗さが小さい半球面の凹部1
a、lbが球中心が軸線上に位置するように設けられて
いる。一方、凹部1a、lbより小さい中空半球の形を
なし、表面粗さが小さ(圧電材料でできた振動子2,3
が回転子1の凹部la、lbの表面と微小な間隙を保っ
て固定棒4.5にそれぞれ取り付けられている。振動子
2は、第3図に示すように、内面が4つの電極2a、2
b、2c、2dに分割され、外面は軸受面を兼ねた一様
な電極2eとなっており、電極2aと20の紐、電極2
bと2dの組には互いに逆相の電圧が印加されて、第4
図の破線で示すようなモードで振動するようになってい
る(この方が一様に伸び縮みするよりも能率がよい)。Hemispherical recesses 1 with small surface roughness are provided on both end faces of the rotor 10.
a and lb are provided so that the center of the sphere is located on the axis. On the other hand, it has the shape of a hollow hemisphere smaller than the recesses 1a and lb, and has a small surface roughness (the vibrators 2 and 3 made of piezoelectric material
are attached to the fixed rods 4.5 with a small gap between them and the surfaces of the recesses la and lb of the rotor 1, respectively. As shown in FIG. 3, the vibrator 2 has four electrodes 2a, 2 on its inner surface.
It is divided into electrodes b, 2c, and 2d, and the outer surface is a uniform electrode 2e that also serves as a bearing surface.
Voltages with opposite phases are applied to the pair b and 2d, and the fourth
It vibrates in the mode shown by the broken line in the figure (this is more efficient than expanding and contracting uniformly).
振動子3も同様である。The same applies to the vibrator 3.
振動子2.3を振動させると、先に述べたように、周囲
よりも圧力の高い空気膜6.7が形成され、回転子1を
ラジアル、スラスト両方向に非接触支持できる。When the vibrator 2.3 is vibrated, an air film 6.7 having a higher pressure than the surrounding air is formed as described above, and the rotor 1 can be supported in both radial and thrust directions without contact.
このように、回転子1と振動子2.3は、球面で互いに
対向しているので、両者の配置において相対的な角度お
よび回転子1の中心軸に直角な方向に誤差があっても吸
収できる。したがって、振動子2と3との間隔を回転子
1の寸法との関係において正確に設定するのみでよい。In this way, since the rotor 1 and the vibrator 2.3 are spherical and face each other, even if there is an error in the relative angle or direction perpendicular to the central axis of the rotor 1 in their arrangement, it can be absorbed. can. Therefore, it is only necessary to accurately set the distance between the vibrators 2 and 3 in relation to the dimensions of the rotor 1.
なお、本実施例では部品点数が少なくなっている。Note that in this embodiment, the number of parts is reduced.
第5図は本発明のスクィーズ軸受の第2の実施例の側面
図である。FIG. 5 is a side view of a second embodiment of the squeeze bearing of the present invention.
本実施例では、振動子2が板バネ8で支持されている。In this embodiment, the vibrator 2 is supported by a leaf spring 8.
こうすることにより、第1の実施例に比へ振動子2の位
置の設定の精度がさらに緩くなり、軸受を経済的に構成
できる。By doing so, the accuracy of setting the position of the vibrator 2 is further reduced compared to the first embodiment, and the bearing can be constructed economically.
第6図は本発明のスクィーズ軸受の第3の実施例の側面
図である。FIG. 6 is a side view of a third embodiment of the squeeze bearing of the present invention.
本実施例では、振動子2がコイルバネ9で支持されてい
る。なお、振動子2.3をともにバネで支持することも
できる。In this embodiment, the vibrator 2 is supported by a coil spring 9. Note that both vibrators 2 and 3 can also be supported by springs.
第7図は本発明のスクィーズ軸受の第4の実施例の斜視
図、第8図はその縦側面図である。FIG. 7 is a perspective view of a fourth embodiment of the squeeze bearing of the present invention, and FIG. 8 is a longitudinal side view thereof.
本実施例では、回転子9の下側の端面が平坦となってお
り、従来と同様な形状をした振動子lOが用いられてい
る。In this embodiment, the lower end surface of the rotor 9 is flat, and a vibrator lO having a shape similar to that of the conventional one is used.
第9図は本発明のスクィーズ軸受の第5の実施例の縦側
面図である。FIG. 9 is a longitudinal side view of a fifth embodiment of the squeeze bearing of the present invention.
本実施例では、回転子の12の両端面には半球状の凸部
!2a、12bが設けられ、これに対向する振動子13
.14の振動面は半球状の凹部となっている。この場合
、振動子13.14の分割された電極は振動子13.1
4の外側に形成されている。In this embodiment, hemispherical convex portions are formed on both end faces of the rotor 12! 2a and 12b are provided, and a vibrator 13 facing thereto.
.. The vibration surface 14 is a hemispherical recess. In this case, the divided electrodes of oscillator 13.14 are
It is formed on the outside of 4.
[発明の効果]
以上説明したように本発明は、回転子の少なくとも一方
の端面に、球状の凹部または凸部を形成し、これと対向
する振動子の振動面も凸部または凹部とすることにより
、組立精度が厳しくなくても良く、また部品点数も減る
ため、安価になるという効果がある。[Effects of the Invention] As explained above, the present invention is characterized in that a spherical recess or convex portion is formed on at least one end face of the rotor, and the vibrating surface of the vibrator facing the spherical concave portion is also formed as a convex portion or a concave portion. Therefore, assembly accuracy does not have to be strict, and the number of parts is reduced, which has the effect of lowering the cost.
第1図は本発明のスクィーズ軸受の第1の実施例の斜視
図、第2図はその縦断面図、第3図は振動子2の内面図
、第4図は振動子2の振動モードを示す図、第5図、第
6図はそれぞれ本発明のスクィーズ軸受の第2.第3の
実施例の側面図、第7図、第8図はそれぞれ本発明のス
クィーズ軸受の第4の実施例の斜視図と縦断面図、第9
図は本発明のスクィーズ軸受の第5の実施例の縦側面図
、第10図はスクィーズ軸受の原理を説明する図、第1
1図はスクィーズ軸受の従来例の縦断面図である。
1.9.12・・・回転子、
la、lb・・・凹部、
12a、12b・・・凸部、
2.3.10.13.14・・・振動子、28〜2e・
・・電極、
4.5・・・固定棒、
6.7・1空気膜、
8・・・板バネ、
9・・・コイルバネ。
特許出願人 日本電信電話株式会社FIG. 1 is a perspective view of the first embodiment of the squeeze bearing of the present invention, FIG. 2 is a longitudinal sectional view thereof, FIG. 3 is an inner view of the vibrator 2, and FIG. 4 is a diagram showing the vibration mode of the vibrator 2. The diagrams shown in FIGS. 5 and 6 respectively show the second embodiment of the squeeze bearing of the present invention. A side view of the third embodiment, FIG. 7, and FIG. 8 are respectively a perspective view and a vertical cross-sectional view of the fourth embodiment of the squeeze bearing of the present invention.
The figure is a longitudinal side view of the fifth embodiment of the squeeze bearing of the present invention, FIG. 10 is a diagram explaining the principle of the squeeze bearing, and FIG.
FIG. 1 is a longitudinal sectional view of a conventional example of a squeeze bearing. 1.9.12... Rotor, la, lb... Concave portion, 12a, 12b... Convex portion, 2.3.10.13.14... Vibrator, 28-2e.
...electrode, 4.5...fixing rod, 6.7.1 air film, 8...plate spring, 9...coil spring. Patent applicant Nippon Telegraph and Telephone Corporation
Claims (1)
く球の一部の形をなす凹部または凸部を、該球の中心が
軸線上に位置するように有する回転子と、 回転子の各端面と対向して設けられ、表面粗さが小さい
平面あるいは曲面であって、前記回転子の端面が平坦な
場合には平坦な、凹部が設けられている場合には該凹部
の球より小さい球の一部の形の凸部の、凸部が設けられ
ている場合には該凸部の球より大きい球の一部の形の凹
部の振動面を、回転子の端面とある隙間を保って有する
振動子とを含むスクィーズ軸受。[Scope of Claims] 1. A rotating device that is columnar and has a concave or convex portion in the shape of a part of a sphere with low surface roughness on at least one end surface so that the center of the sphere is located on the axis. A flat or curved surface with small surface roughness, which is provided facing each end face of the rotor, and is flat when the end face of the rotor is flat, and is flat when a recess is provided. The vibration surface of the convex part in the shape of a part of a sphere smaller than the sphere in the concave part, or, if a convex part is provided, in the shape of a part of a sphere larger than the sphere in the convex part, of the rotor. A squeeze bearing that includes an end face and a vibrator with a certain gap.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP29241888A JPH02142919A (en) | 1988-11-21 | 1988-11-21 | Squeeze bearing |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP29241888A JPH02142919A (en) | 1988-11-21 | 1988-11-21 | Squeeze bearing |
Publications (1)
Publication Number | Publication Date |
---|---|
JPH02142919A true JPH02142919A (en) | 1990-06-01 |
Family
ID=17781532
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP29241888A Pending JPH02142919A (en) | 1988-11-21 | 1988-11-21 | Squeeze bearing |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPH02142919A (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6045265A (en) * | 1996-05-02 | 2000-04-04 | Thk Co., Ltd. | Rolling motion guide apparatus and method of manufacturing movable member of rolling motion guide apparatus |
-
1988
- 1988-11-21 JP JP29241888A patent/JPH02142919A/en active Pending
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6045265A (en) * | 1996-05-02 | 2000-04-04 | Thk Co., Ltd. | Rolling motion guide apparatus and method of manufacturing movable member of rolling motion guide apparatus |
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