JPH0861369A - Hydrostatic gas bearing - Google Patents
Hydrostatic gas bearingInfo
- Publication number
- JPH0861369A JPH0861369A JP19055294A JP19055294A JPH0861369A JP H0861369 A JPH0861369 A JP H0861369A JP 19055294 A JP19055294 A JP 19055294A JP 19055294 A JP19055294 A JP 19055294A JP H0861369 A JPH0861369 A JP H0861369A
- Authority
- JP
- Japan
- Prior art keywords
- bearing
- load side
- thrust bearing
- load
- thrust
- 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
Landscapes
- Turning (AREA)
- Magnetic Bearings And Hydrostatic Bearings (AREA)
Abstract
Description
【0001】[0001]
【産業上の利用分野】この発明は、穴明け機の主軸等に
用いる静圧気体軸受に関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hydrostatic gas bearing used for a main shaft of a punching machine.
【0002】[0002]
【従来の技術】従来、穴明け機の主軸等に用いる静圧軸
受としては、図3(a)、(b)、(c)のようなもの
がある。即ち、主軸1はスラスト板2を有し、そのスラ
スト板2の下方の主軸1の外径面とスラスト板2の下面
と対向した下軸受部材3がハウジング4に取付けられ
る。また、スラスト板2の上方の主軸1の外径面とスラ
スト板2の上面と対向した上軸受部材5がハウジング4
に取付けられる。2. Description of the Related Art Conventionally, as a hydrostatic bearing used for a main shaft of a punching machine, there are those shown in FIGS. 3 (a), 3 (b) and 3 (c). That is, the main shaft 1 has a thrust plate 2, and a lower bearing member 3 facing the outer diameter surface of the main shaft 1 below the thrust plate 2 and the lower surface of the thrust plate 2 is attached to the housing 4. Further, the upper bearing member 5 facing the outer diameter surface of the main shaft 1 above the thrust plate 2 and the upper surface of the thrust plate 2 has a housing 4
Mounted on.
【0003】上記の下軸受部材3には、ジャーナル軸受
部6及びスラスト軸受部7が設けられ、そのジャーナル
軸受部6は、主軸1の外径面とジャーナル軸受すきま8
を介して対向したジャーナル軸受面9を有し、そのジャ
ーナル軸受面9に自成絞り孔11が設けられる。The lower bearing member 3 is provided with a journal bearing portion 6 and a thrust bearing portion 7, and the journal bearing portion 6 has an outer diameter surface of the main shaft 1 and a journal bearing clearance 8.
Have journal bearing surfaces 9 facing each other, and the journal bearing surface 9 is provided with self-made throttle holes 11.
【0004】また、スラスト軸受部7は、スラスト板2
とスラスト軸受すきま12を介して対向するスラスト軸
受面13を有し、そのスラスト軸受面13に自成絞り穴
14が設けられる。The thrust bearing portion 7 is composed of the thrust plate 2
And a thrust bearing surface 13 facing each other through a thrust bearing clearance 12, and the self-made throttle hole 14 is provided in the thrust bearing surface 13.
【0005】上記の上軸受部材5にはスラスト軸受部
7’が設けられ、そのスラスト軸受部7’はスラスト板
2とスラスト軸受すきま12’を介して対向するスラス
ト軸受面13’を有し、そのスラスト軸受面13’に自
成絞り孔14’が設けられる。A thrust bearing portion 7'is provided on the upper bearing member 5, and the thrust bearing portion 7'has a thrust bearing surface 13 'which faces the thrust plate 2 with a thrust bearing clearance 12'. The thrust bearing surface 13 'is provided with a self-made throttle hole 14'.
【0006】ハウジング4に設けた通路15に圧縮気体
を供給すると、ジャーナル軸受部6及び各スラスト軸受
部7、7’に設けられた各絞り孔11、14、14’か
らジャーナル軸受すきま8、スラスト軸受すきま12、
12’に圧縮気体が流入し、主軸1を非接触で支持す
る。When compressed gas is supplied to the passage 15 provided in the housing 4, the journal bearing clearance 8 and the thrust are transmitted from the throttle holes 11, 14, 14 'provided in the journal bearing portion 6 and the thrust bearing portions 7, 7'. Bearing clearance 12,
The compressed gas flows into 12 'and supports the main shaft 1 in a non-contact manner.
【0007】上記の主軸1には、コレットチャック16
が取付けられており、そのコレットチャック16により
工具17を把持する。主軸1をモータ等で高速回転させ
ると工具17が回転し、その工具17をワークに押付け
ることにより穴明け加工等を行うことができる。工具1
7とワークが押付けられる力により主軸1がハウジング
4に対して変位する。これにより、上部スラスト軸受面
13’が負荷受面となり、下方のスラスト軸受面13が
反負荷側となる。The main shaft 1 has a collet chuck 16
Is attached, and the collet chuck 16 holds the tool 17. When the spindle 1 is rotated at a high speed by a motor or the like, the tool 17 is rotated, and by punching the tool 17 against the work, drilling or the like can be performed. Tool 1
The spindle 1 is displaced with respect to the housing 4 by the force of pressing the workpiece 7 and the work. As a result, the upper thrust bearing surface 13 'serves as a load receiving surface and the lower thrust bearing surface 13 serves as an anti-load side.
【0008】従来、穴明け機の主軸1等に使用されてい
たスラスト軸受は、負荷側、反負荷側を特に区別するこ
となく、両方とも全く同一構成の軸受を使用するのが一
般的であったが、焼付き等の故障防止の観点から、軸受
面積、給気孔数、給気孔径のそれぞれについて、負荷側
軸受の方が反負荷側軸受よりも大になるようにしたスラ
スト軸受が提案されている(特開平2−209622号
公報)。このものは、無負荷時に負荷側の軸受すきまを
大きくし、負荷状態で負荷側の軸受すきまを反負荷側の
軸受すきまに近づけるようにしただけのものである。Conventionally, the thrust bearings used for the main shaft 1 of a drilling machine are generally the same in structure, without any distinction between the load side and the non-load side. However, from the perspective of preventing seizures and other failures, thrust bearings have been proposed in which the bearing on the load side, the number of holes, and the diameter of the holes are larger on the load side than on the anti-load side. (Japanese Patent Laid-Open No. 2-209622). This is one in which the bearing clearance on the load side is increased when there is no load so that the bearing clearance on the load side approaches the bearing clearance on the anti-load side in a loaded state.
【0009】[0009]
【発明が解決しようとする課題】穴明け機の主軸等に用
いられるスラスト軸受の負荷容量は使用目的、使用方法
により決定される。ここでは、一例として負荷側の負荷
容量WOA、反負荷側の負荷容量WOBが必要である場合を
考える。ただし、WOA>WOBとする。The load capacity of the thrust bearing used for the main shaft of a drilling machine is determined by the purpose and method of use. Here, as an example, consider a case where the load capacity W OA on the load side and the load capacity W OB on the anti-load side are required. However, W OA > W OB .
【0010】図4に上記の負荷容量を満足し、かつ負荷
側および反負荷側に同一の自成絞りスラスト軸受を用い
た場合の負荷容量特性曲線図を示す。この場合、負荷側
の負荷容量W1A、反負荷側の負荷容量W1BとするとW1A
=W1Bであり、W1A=WOAとするとW1B>WOBである。
即ち、反負荷側の軸受の負荷容量は必要以上に大きいと
言える。FIG. 4 shows a load capacity characteristic curve diagram when the above load capacity is satisfied and the same self-made throttle thrust bearing is used on the load side and the anti-load side. In this case, if the load capacity on the load side is W 1A and the load capacity on the anti-load side is W 1B , then W 1A
= W 1B and W 1A = W OA , W 1B > W OB .
That is, it can be said that the load capacity of the bearing on the anti-load side is larger than necessary.
【0011】一般に、スラスト軸受において軸受面積が
一定のもとでは、負荷容量を大きくすると消費流量も大
きくなるという関係がある為、図4に示した軸受の構成
では必要以上に消費流量を大きくしていることになる。Generally, in a thrust bearing, when the bearing area is constant, there is a relation that the flow rate increases as the load capacity increases. Therefore, the flow rate of the bearing shown in FIG. Will be.
【0012】この問題を解決する方法として、前掲の特
開平2−209622号公報に記載されている通り、負
荷側の軸受の給気孔数を反負荷側の軸受よりも多くした
り、あるいは、負荷側の軸受の給気孔径を反負荷側の軸
受よりも大きくしたりする方法がある。つまり、反負荷
側の軸受の給気孔数を負荷側のそれよりも減らしたり、
あるいは、反負荷側の軸受の給気孔径を負荷側の軸受の
それよりも小さくしたりすることにより、反負荷側の軸
受の流量を節約することが考えられる。As a method for solving this problem, as described in the above-mentioned Japanese Patent Laid-Open No. 2-209622, the number of air supply holes in the bearing on the load side is made larger than that on the bearing on the anti-load side, or the load is reduced. There is a method of making the air supply hole diameter of the side bearing larger than that of the bearing on the opposite side. In other words, reduce the number of air supply holes in the bearing on the anti-load side compared to that on the load side,
Alternatively, it is conceivable to reduce the flow rate of the bearing on the anti-load side by making the supply hole diameter of the bearing on the anti-load side smaller than that of the bearing on the load side.
【0013】この方法でWOBを考慮し、軸受を選定した
場合の負荷容量特性曲線図を図5に示す。この場合の負
荷側の負荷容量W2A、反負荷側の負荷容量W2Bとすると
W2B=WOBとなる。その結果、消費流量をある程度少な
くすることが可能である。[0013] indicates the load capacitance characteristic curve diagram when considering W OB in this way were selected bearing in FIG. Load capacity W 2A on the load side of this case, when the load capacitance W 2B of the anti-load side and W 2B = W OB. As a result, it is possible to reduce the consumption flow rate to some extent.
【0014】しかし、近年、穴明け機等の高性能化が進
み、さらに消費流量の低減が求められ、上記の方法だけ
では不十分な場合があった。However, in recent years, the performance of punching machines and the like has been improved, and further reduction of the flow rate consumed has been demanded, and the above method alone may not be sufficient.
【0015】そこで、この発明は、負荷側、反負荷側に
それぞれ対向型のスラスト軸受を有する静圧気体軸受に
おいて、必要とされる負荷容量を保った状態でスラスト
軸受部の消費流量を一層低減することを目的とする。Therefore, according to the present invention, in a hydrostatic gas bearing having opposing thrust bearings on the load side and the anti-load side respectively, the flow rate consumed by the thrust bearing portion is further reduced while maintaining the required load capacity. The purpose is to do.
【0016】[0016]
【課題を解決するための手段】上記の課題を解決するた
めに、この発明は、負荷側、反負荷側の対向側スラスト
軸受を有し、各スラスト軸受面に所要数の給気孔を円周
上に設けてなる静圧気体軸受において、上記負荷側スラ
スト軸受面の給気孔のみを環状の溝の底面に設け、その
スラスト軸受すきまを可及的に小さくした構成としたも
のである。In order to solve the above-mentioned problems, the present invention has opposing thrust bearings on the load side and the anti-load side, and each thrust bearing surface has a required number of air supply holes circumferentially. In the static pressure gas bearing provided above, only the air supply hole of the load side thrust bearing surface is provided on the bottom surface of the annular groove, and the thrust bearing clearance is made as small as possible.
【0017】[0017]
【作用】例として、図5に示した負荷側軸受と同等の軸
受面積および負荷容量を有する溝付き軸受を用いた場合
の負荷容量特性曲線を図6に示す。溝付き軸受は溝の表
面絞り効果により、すきまが小さいときは自成絞り軸受
と同等の負荷容量であっても、軸受すきまが大きくなる
につれ負荷容量が自成絞り軸受の場合(波線参照)より
も小さくなる。よって、この場合の負荷側の負荷容量を
W3A、反負荷側の負荷容量をW3Bとすると、W3A=W2A
>W0A、W3B>W2B=W0Bとなる。As an example, FIG. 6 shows a load capacity characteristic curve in the case where a grooved bearing having a bearing area and load capacity equivalent to those of the load side bearing shown in FIG. 5 is used. Due to the surface drawing effect of the groove, the grooved bearing has a load capacity equivalent to that of the self-made throttle bearing when the clearance is small, but the load capacity is larger than that of the self-made throttle bearing as the bearing clearance increases (see the wavy line). Also becomes smaller. Therefore, if the load capacity on the load side in this case is W 3A and the load capacity on the anti-load side is W 3B , then W 3A = W 2A
> W 0A , W 3B > W 2B = W 0B .
【0018】ここで、負荷側軸受および反負荷側軸受と
もに必要以上に大きい負荷容量になっていることから、
軸受すきまを小さくし、負荷容量を減ずることが可能で
ある。一般に軸受すきまを小さくすると消費流量は小さ
くなるので、すきまを小さくすることは消費流量の低減
のための有効な手段である。Here, since the load side bearing and the anti-load side bearing both have an unnecessarily large load capacity,
It is possible to reduce the bearing clearance and load capacity. Generally, the smaller the bearing clearance is, the smaller the consumption flow rate is. Therefore, reducing the clearance is an effective means for reducing the consumption flow rate.
【0019】負荷容量WOA、WOBを考慮し軸受すきまを
小さくした結果が図7である。この場合の負荷側の負荷
容量W4A、反負荷側の負荷容量W4Bとすると、W4A=W
OA、W4B=W0Bである。このように、負荷側軸受を溝付
きスラスト軸受とし、反負荷側の軸受を自成絞り軸受と
することにより、穴明け機の主軸等に使用されるスラス
ト軸受部の消費流量の低減が可能となる。FIG. 7 shows the result of reducing the bearing clearance in consideration of the load capacities W OA and W OB . In this case, if the load capacity W 4A on the load side and the load capacity W 4B on the opposite side are W 4A = W
OA , W 4B = W 0B . In this way, by using a grooved thrust bearing as the load side bearing and a self-made throttle bearing as the counter load side bearing, it is possible to reduce the flow rate consumption of the thrust bearing portion used for the main shaft of a drilling machine, etc. Become.
【0020】[0020]
【実施例】図1(a)(b)(c)に示した実施例は、
先に図6に示した従来例と基本的構成は同一であるの
で、同一部分には同一符号を付して示すにとどめ、その
説明を省略する。EXAMPLE The example shown in FIGS. 1 (a), (b) and (c) is
Since the basic structure is the same as that of the conventional example shown in FIG. 6, the same parts are denoted by the same reference numerals and the description thereof is omitted.
【0021】相違する点は、負荷側のスラスト軸受面1
3’の絞り孔14’を主軸1と同心状の溝18の底面に
設けた点及びスラスト軸受すきま12’を可及的に小さ
く(例えば20μm)に設定した点である。The difference lies in the thrust bearing surface 1 on the load side.
3'is a throttle hole 14 'provided on the bottom surface of a groove 18 concentric with the main shaft 1 and a thrust bearing clearance 12' is set to be as small as possible (for example, 20 μm).
【0022】上記のように構成すると、先に図7に示し
たような負荷容量特性が得られ、負荷側の負荷容量をW
4A及び反負荷側の負荷容量をW4Aを、それぞれ所要の負
荷容量W0A、W0Bと一致させることができる。With the above construction, the load capacity characteristic as shown in FIG. 7 is obtained, and the load capacity on the load side is W.
The load capacity W 4A on the side of 4 A and the anti-load side can be matched with the required load capacity W 0A and W 0B , respectively.
【0023】図2は、上記の溝18及びその溝底に形成
される自成絞り孔14’の具体例であり、溝1の幅aは
0.7mm、深さbは0.01mm(10μm)である。FIG. 2 shows a specific example of the groove 18 and the self-made throttle hole 14 'formed in the groove bottom. The groove 1 has a width a of 0.7 mm and a depth b of 0.01 mm (10 μm). ).
【0024】なお、自成絞り孔に代え、その他適宜な形
状の給気孔を採用することができる。It should be noted that instead of the self-made throttle hole, an air supply hole having another suitable shape can be adopted.
【0025】[0025]
【発明の効果】以上のように、この発明は、負荷側スラ
スト軸受面の給気孔を環状の溝の底面に設け、そのスラ
スト軸受すきまを可及的に小さくした構成により、所要
の負荷容量を確保しつつ、消費流量の低減を図ることが
できる。As described above, according to the present invention, the required load capacity is provided by providing the air supply hole of the load side thrust bearing surface on the bottom surface of the annular groove and making the thrust bearing clearance as small as possible. It is possible to reduce the consumption flow rate while ensuring the amount.
【図1】(a)実施例の断面図 (b)同上の負荷側スラスト軸受面の平面図 (c)同上の反負荷側スラスト軸受面の平面図FIG. 1A is a cross-sectional view of an embodiment. FIG. 1B is a plan view of a load side thrust bearing surface of the same. FIG. 1C is a plan view of an anti-load side thrust bearing surface of the same.
【図2】同上の一部拡大断面図FIG. 2 is a partially enlarged sectional view of the above.
【図3】(a)従来例の断面図 (b)同上の負荷側スラスト軸受面の平面図 (c)同上の反負荷側スラスト軸受面の平面図FIG. 3A is a cross-sectional view of a conventional example. FIG. 3B is a plan view of a load side thrust bearing surface of the same. FIG. 3C is a plan view of an anti-load side thrust bearing surface of the same.
【図4】負荷容量特性図[Figure 4] Load capacity characteristic diagram
【図5】負荷容量特性図[Figure 5] Load capacity characteristic diagram
【図6】負荷容量特性図[Figure 6] Load capacity characteristic diagram
【図7】負荷容量特性図[Figure 7] Load capacity characteristic diagram
1 主軸 2 スラスト板 3 下軸受部材 4 ハウジング 5 上軸受部材 6 ジャーナル軸受部 7、7’ スラスト軸受部 8 ジャーナル軸受すきま 9 ジャーナル軸受面 11 自成絞り孔 12、12’ スラスト軸受すきま 13、13’ スラスト軸受面 14、14 自成絞り孔 15 通路 16 コレットチャック 17 工具 18 溝 1 main shaft 2 thrust plate 3 lower bearing member 4 housing 5 upper bearing member 6 journal bearing part 7, 7'thrust bearing part 8 journal bearing clearance 9 journal bearing surface 11 self-made throttle hole 12, 12 'thrust bearing clearance 13, 13' Thrust bearing surface 14, 14 Self-made throttle hole 15 Passage 16 Collet chuck 17 Tool 18 Groove
Claims (1)
スト軸受を有し、各スラスト軸受面に所要数の給気孔を
設けてなる静圧気体軸受において、上記負荷側スラスト
軸受面の給気孔のみを環状の溝の底面に設け、そのスラ
スト軸受すきまを可及的に小さくしたことを特徴とする
静圧気体軸受。1. A static pressure gas bearing having opposing thrust bearings on the load side and the anti-load side, respectively, and having a required number of air supply holes on each thrust bearing surface, wherein the air supply holes on the load side thrust bearing surface are provided. The static pressure gas bearing is characterized in that only the thrust bearing clearance is provided as small as possible on the bottom surface of the annular groove.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP19055294A JP3609455B2 (en) | 1994-08-12 | 1994-08-12 | Static pressure gas bearing |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP19055294A JP3609455B2 (en) | 1994-08-12 | 1994-08-12 | Static pressure gas bearing |
Publications (2)
Publication Number | Publication Date |
---|---|
JPH0861369A true JPH0861369A (en) | 1996-03-08 |
JP3609455B2 JP3609455B2 (en) | 2005-01-12 |
Family
ID=16259981
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP19055294A Expired - Lifetime JP3609455B2 (en) | 1994-08-12 | 1994-08-12 | Static pressure gas bearing |
Country Status (1)
Country | Link |
---|---|
JP (1) | JP3609455B2 (en) |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH11257346A (en) * | 1998-01-23 | 1999-09-21 | Rech Ind & Dev Sa:Co | Sliding bearing |
JP2008256100A (en) * | 2007-04-05 | 2008-10-23 | Toshiba Mach Co Ltd | Fixed throttle device for oil static pressure bearing |
WO2013065268A1 (en) * | 2011-10-31 | 2013-05-10 | オイレス工業株式会社 | Aerostatic bearing and linear guide employing said aerostatic bearing |
WO2013073166A1 (en) * | 2011-11-18 | 2013-05-23 | オイレス工業株式会社 | Aerostatic bearing and linear motion guiding device using said aerostatic bearing |
CN111120512A (en) * | 2020-01-10 | 2020-05-08 | 中国工程物理研究院机械制造工艺研究所 | Throttle air bearing and fast axle servo based on this bearing |
WO2022022100A1 (en) * | 2020-07-29 | 2022-02-03 | 青岛海尔智能技术研发有限公司 | Gas bearing, compressor, and air conditioner system |
-
1994
- 1994-08-12 JP JP19055294A patent/JP3609455B2/en not_active Expired - Lifetime
Cited By (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH11257346A (en) * | 1998-01-23 | 1999-09-21 | Rech Ind & Dev Sa:Co | Sliding bearing |
JP2008256100A (en) * | 2007-04-05 | 2008-10-23 | Toshiba Mach Co Ltd | Fixed throttle device for oil static pressure bearing |
WO2013065268A1 (en) * | 2011-10-31 | 2013-05-10 | オイレス工業株式会社 | Aerostatic bearing and linear guide employing said aerostatic bearing |
JP2013096502A (en) * | 2011-10-31 | 2013-05-20 | Oiles Corp | Aerostatic bearing and linear guide employing the aerostatic bearing |
TWI504821B (en) * | 2011-10-31 | 2015-10-21 | Oiles Industry Co Ltd | Static pressure gas bearings and the use of the static pressure gas bearing linear motion guide device |
WO2013073166A1 (en) * | 2011-11-18 | 2013-05-23 | オイレス工業株式会社 | Aerostatic bearing and linear motion guiding device using said aerostatic bearing |
JP2013108557A (en) * | 2011-11-18 | 2013-06-06 | Oiles Corp | Aerostatic bearing and linear motion guiding device using the same |
CN103842672A (en) * | 2011-11-18 | 2014-06-04 | 奥依列斯工业株式会社 | Aerostatic bearing and linear motion guiding device using said aerostatic bearing |
TWI491815B (en) * | 2011-11-18 | 2015-07-11 | Oiles Industry Co Ltd | Static pressure gas bearings and the use of the static pressure gas bearing linear motion guide device |
CN111120512A (en) * | 2020-01-10 | 2020-05-08 | 中国工程物理研究院机械制造工艺研究所 | Throttle air bearing and fast axle servo based on this bearing |
WO2022022100A1 (en) * | 2020-07-29 | 2022-02-03 | 青岛海尔智能技术研发有限公司 | Gas bearing, compressor, and air conditioner system |
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