JP2006207668A - Asymmetrical fluid bearing - Google Patents
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本発明は、主に地震の早期発見のため地下の構造や状態を監視、観測するために人工的に弾性波を発生し、地中に送信するための精密制御定常震源（Accurately Controlled Routine Operated Seismic Source, ＡＣＲＯＳＳ）のように、大負荷で作動する機器や加振器のような大きな衝撃負荷を発生する機器のラジアル軸受として適切に使用可能な非対称流体軸受に関するものである。 The present invention is a precision controlled steady-state source (Accurately Controlled Routine Operated Seismic) for artificially generating elastic waves and transmitting them underground, mainly for monitoring and observing underground structures and conditions for early detection of earthquakes. The present invention relates to an asymmetric fluid bearing that can be appropriately used as a radial bearing of a device that generates a large impact load, such as a device that operates with a large load, such as a source, ACROSS).
地球科学分野において、地震の波を用い地下構造を解明するには、自然地震で発生する弾性波を用いるのが従来の方法であった。しかし発生時刻が不定期で、震源の位置も望ましいところになく、また、その位置も正確にはわからなかった。火薬爆発などのノウレス的な人工震源も用いられてきたが、この方法は定常的に使えるものではなかった。地下の状態変化を常時モニターすることが重要な課題となっており、この目的のために精密制御定常震源（ＡＣＲＯＳＳ）が開発された。 In the earth science field, the conventional method has been to use elastic waves generated by natural earthquakes to elucidate underground structures using earthquake waves. However, the time of occurrence was irregular, the location of the epicenter was not desirable, and the location was not exactly known. Knowles-type artificial seismic sources such as explosive explosions have been used, but this method has not been used regularly. The constant monitoring of subsurface conditions has become an important issue, and a precisely controlled steady-state source (ACROSS) has been developed for this purpose.
ＡＣＲＯＳＳによる地下構造の連続モニタリングシステムは、ＡＣＲＯＳＳによりサイン状の定常弾性波を２４時間３６５日地下に連続送信し、これを遠隔地に設置した受信機で常時受信することにより地下の監視、観測を行うものである。 The ACROSS underground structure continuous monitoring system continuously transmits sine-like stationary elastic waves to the basement for 24 hours 365 days using ACROSS, and constantly receives and monitors them in a remote receiver. Is what you do.
連続弾性波発生に際しては、偏心質量を持つ回転体をデジタルサーボモータにより回転させ、偏心質量により遠心力を発生させる。現在使用されているＡＣＲＯＳＳは、回転周波数５０Hzでの信号振幅は２０tonfで、偏心質量は転がり軸受で支持する構造になっている。このような回転震源装置は、例えば特開平１０−１４２３４５号公報（特許文献１）等に記載されている。しかしながら、この装置はシャフトの回転による軸受摩擦がおよそ１５kWで、著しく大きい発熱を伴うため、各軸受に水冷管を設け、さらに潤滑管理を厳しくする等の対策を講じている。 When generating a continuous elastic wave, a rotating body having an eccentric mass is rotated by a digital servo motor, and a centrifugal force is generated by the eccentric mass. The ACROSS currently used has a signal amplitude of 20 tons at a rotation frequency of 50 Hz and a structure in which the eccentric mass is supported by a rolling bearing. Such a rotary source device is described in, for example, Japanese Patent Laid-Open No. 10-142345 (Patent Document 1). However, this apparatus has a bearing friction of about 15 kW due to the rotation of the shaft and is accompanied by a remarkably large heat generation. Therefore, measures such as providing water-cooled pipes for each bearing and stricter lubrication management are taken.
その対策として、従来のＡＣＲＯＳＳで用いられている転がり軸受に代えて静圧流体軸受等の流体軸受とすることが考えられている。流体軸受を用いると加圧流体を供給する設備が必要となるものの、(1)軸受摩擦が小さく、発熱、潤滑管理の問題がなくなる (2)転がり軸受に見られる転動がないため、運転精度が高く、きれいな信号が得られる (3)滑り面間で固体接触を行わないため、運転中の負荷の繰り返しによるフレーキングの心配がなく長寿命である (4)軸受給気により本体の冷却が可能である、という各種の効果が期待できる。 As a countermeasure, it is considered that a fluid bearing such as a hydrostatic fluid bearing is used instead of the rolling bearing used in the conventional ACROSS. The use of hydrodynamic bearings requires equipment to supply pressurized fluid, but (1) bearing friction is small and heat generation and lubrication management problems are eliminated. (2) Operation accuracy is eliminated because there is no rolling found in rolling bearings. (3) Since there is no solid contact between the sliding surfaces, there is no risk of flaking due to repeated load during operation, and the service life is long. Various effects can be expected.
そこで実際に、流体軸受を用いたＡＣＲＯＳＳの開発研究が本発明者等によりなされている。実際に製作した装置は２００kgf級の精密制御定常震源であり、図７に示すような構造のものであって、一部に切り欠き４１を設けた非対称シャフト４２をカップリング４３を介してモータ４４で回転させるに際して、上部ラジアル流体軸受４５と下部流体軸受４６とでラジアル方向を支持し、各流体軸受間にはスペーサ４７を配置している。 Therefore, the present inventors have actually conducted research on the development of ACROSS using fluid bearings. The actually manufactured device is a 200 kgf-class precision controlled steady-state earthquake source having a structure as shown in FIG. 7, and an asymmetric shaft 42 provided with a notch 41 in part is connected to a motor 44 via a coupling 43. , The radial direction is supported by the upper radial fluid bearing 45 and the lower fluid bearing 46, and a spacer 47 is disposed between the fluid bearings.
各ラジアル流体軸受はケーシング４８内に収納され、シャフト下端部はスラスト流体軸受５０で支持し、ケーシング４８の上下端部は各々上部プレート５１と下部プレート５２で閉じている。また、ケーシング４８はその周囲を固定用ボルト５３によってホルダー５４に固定支持され、ホルダー５４の下端を加震部材５５に固定し、ロードセル５６で監視しながらモータ４４の回転により非対称シャフトを精密制御して所定の回転をさせることによって生じる振動を加震部材５４に与え、地中に振動を与えて震源として利用するものである。このような流体軸受を用いることにより、所望の効果が得られている。
上記のような流体軸受を用いた精密制御定常震源においては、流体軸受を用いることによる種々の効果を奏することができるものであるが、通常の流体軸受は負荷容量に限界があり、現在運転している２０tonf級のＡＣＲＯＳＳと同程度のものを製造するのは困難であった。また、摩擦損失の少ない流体軸受であっても、更に摩擦損失の少ない、しかも安定して超寿命の流体軸受の開発が望まれている。 The precision controlled steady-state earthquake source using fluid bearings as described above can achieve various effects by using fluid bearings. However, ordinary fluid bearings have limited load capacity and are currently operated. It was difficult to manufacture a product equivalent to the 20 tonf class ACROSS. In addition, it is desired to develop a hydrodynamic bearing having a smaller friction loss and a lower friction loss and having a stable and long life.
このような課題は、前記のような精密制御定常震源装置に限らず、大負荷で作動する機器や加振器のような大きな衝撃負荷を発生する機器においても、大きな負荷を受けるラジアル軸受では全て共通の課題として存在する。 Such problems are not limited to the above-described precision controlled steady-state seismic source device, but all of the radial bearings that receive a large load, such as a device that operates with a large load and a device that generates a large impact load such as a vibrator. It exists as a common issue.
そこで本発明は、従来の非対称負荷を支持する機械式ラジアル軸受の寿命を流体潤滑により長寿命化するとともに、一般的な流体軸受では支持することができないような大きな負荷でも安定して支持することができ、また、回転時における流体軸受の軸受損失を大幅に軽減させることができるとともに、小さな偏心で大きな負荷を支持できる非対称流体軸受を提供することにある。 Therefore, the present invention extends the life of conventional mechanical radial bearings that support asymmetric loads by fluid lubrication, and stably supports even large loads that cannot be supported by general fluid bearings. Another object of the present invention is to provide an asymmetric fluid bearing that can significantly reduce bearing loss of a fluid bearing during rotation and can support a large load with a small eccentricity.
そのために、本発明では、非対称負荷を与えるために片側の一部に切り欠き部を設ける回転軸の性質を利用し、その切り欠き部を軸受面の一部にも存在するように設け、回転することによって負荷が加わる側の軸受面面積を大きくし、反負荷側の軸受面積を小さくした非対称流体軸受を形成することによって、流体軸受の負荷の加わる側の軸受面積を反負荷側の軸受面積より大きくし、軸受面積を負荷方向に対し非対称とすることにより大きな負荷を支持でき、あわせて、回転時の軸受損失を低減することできる。 Therefore, in the present invention, in order to apply an asymmetric load, the property of the rotating shaft provided with a notch part on one side is used, and the notch part is provided so as to exist also on a part of the bearing surface. By forming an asymmetric fluid bearing that increases the bearing surface area on the load application side and reduces the bearing area on the antiload side, the bearing area on the load application side of the fluid bearing is reduced to the bearing area on the antiload side. By making it larger and making the bearing area asymmetric with respect to the load direction, a large load can be supported, and at the same time, bearing loss during rotation can be reduced.
より具体的には、本発明の非対称流体軸受は、片側の一部に切り欠き部を設けることにより、回転時に非対称負荷を与える非対称シャフトを軸支するラジアル流体軸受において、前記非対称負荷を与える切り欠き部を前記流体軸受の軸受面内にも設け、切り欠きを設けない負荷側の軸受面より切り欠きを設ける反負荷側の軸受面を狭く形成したことを特徴とする。 More specifically, the asymmetric fluid bearing according to the present invention is a radial fluid bearing that supports an asymmetric shaft that applies an asymmetric load during rotation by providing a notch on a part of one side. The notched portion is also provided in the bearing surface of the fluid dynamic bearing, and the non-load side bearing surface provided with the notch is formed narrower than the load side bearing surface not provided with the notch.
また、本発明による他の非対称流体軸受は、前記切り欠きが、流体軸受の側方から該流体軸受の軸受面内に延びていることを特徴とする。 Another asymmetric fluid bearing according to the present invention is characterized in that the notch extends from a side of the fluid bearing into a bearing surface of the fluid bearing.
また、本発明による他の非対称流体軸受は、前記切り欠きは、流体軸受の中間部に形成したことを特徴とする。 Another asymmetric fluid bearing according to the present invention is characterized in that the notch is formed in an intermediate portion of the fluid bearing.
また、本発明による他の非対称流体軸受は、前記非対称流体軸受が、精密制御定常震源に用いることを特徴とする。 In addition, another asymmetric fluid bearing according to the present invention is characterized in that the asymmetric fluid bearing is used for a precision controlled stationary earthquake source.
本発明によると、以上の構成によれば、回転によって負荷の加わる側の流体軸受面積は、非対称負荷を発生させるために設ける回転軸の切り欠き部を単に軸受面内に拡張するのみで、負荷側の軸受面積を反負荷側の軸受面面積に比してより大きくすることができ、したがって負荷側と反負荷側との圧力の差によって支持力を発生する流体軸受は、反負荷側の圧力を発生する面積が小さことによる圧力の差がより大きくなり、高い負荷容量の流体軸受とすることができる。さらに、流体摩擦によって起こる軸受損失も反負荷側の軸受面面積の減少により低下させることができ、前記効果と相まって高負荷容量、低損失の流体軸受つすることができる。 According to the present invention, according to the configuration described above, the fluid bearing area on the side to which the load is applied by the rotation can be obtained by simply extending the notch portion of the rotating shaft provided for generating the asymmetric load within the bearing surface. The bearing area on the side can be made larger than the bearing surface area on the anti-load side, and therefore a hydrodynamic bearing that generates bearing force due to the pressure difference between the load side and the anti-load side The difference in pressure due to the small area for generating the pressure increases, and a fluid bearing having a high load capacity can be obtained. Furthermore, bearing loss caused by fluid friction can be reduced by reducing the bearing surface area on the anti-load side, and combined with the above effects, a fluid bearing with high load capacity and low loss can be achieved.
本発明は、流体軸受の負荷容量を簡単な構成により増加させ、軸受損失を減少する課題を、片側の一部に切り欠き部を設けることにより、回転時に非対称負荷を与える非対称シャフトを軸支するラジアル流体軸受において、前記非対称負荷を与える切り欠き部を前記流体軸受の軸受面内にも設け、切り欠きを設けない負荷側の軸受面より切り欠きを設ける反負荷側の軸受面を狭く形成することにより実現する。 The present invention has the object of increasing the load capacity of a fluid bearing with a simple configuration and reducing the bearing loss, and by providing a notch in a part of one side to support an asymmetric shaft that applies an asymmetric load during rotation. In the radial fluid bearing, a notch for applying the asymmetric load is also provided in the bearing surface of the fluid bearing, and the bearing surface on the non-load side where the notch is provided is narrower than the bearing surface on the load side where the notch is not provided. This is realized.
本発明による非対称流体軸受を前記精密制御定常震源（ＡＣＲＯＳＳ）に適用した例に基づいて説明する。図１は前記従来例として示したＡＣＲＯＳＳと同様の全体構成をなす装置を示しており、その概要は前記のとおりであるので、詳細な説明は省略するが、特に流体軸受部分の構成について述べると、この非対称シャフト１１には上方から順に第１切り欠き１２、第２切り欠き１３、第３切り欠き１４を形成しており、この非対称シャフト１１をカップリング１５を介してモータ１６で回転させるようにしている。この非対称シャフト１１は、その上部において第１切り欠き１２と第２切り欠き１３との間における、これらの切り欠きが設けられていない第１ランド部１７を中心として第１ラジアル流体軸受１８で支持され、その下部において第２切り欠き１３と第３切り欠き１４との間における、これらの切り欠きが設けられていない第２ランド部１９を中心として第２ラジアル流体軸受２０で支持されていると共に、各流体軸受間にはスペーサ２１を配置している。 The asymmetric fluid bearing according to the present invention will be described based on an example in which it is applied to the above-mentioned precision controlled steady-state source (ACROSS). FIG. 1 shows an apparatus having an overall configuration similar to that of ACROSS shown as the conventional example, and the outline thereof is as described above. Therefore, detailed description is omitted, but particularly the configuration of a fluid bearing portion will be described. The asymmetric shaft 11 is formed with a first notch 12, a second notch 13, and a third notch 14 in this order from above, and the asymmetric shaft 11 is rotated by a motor 16 via a coupling 15. I have to. The asymmetric shaft 11 is supported by the first radial fluid bearing 18 around the first land portion 17 between the first notch 12 and the second notch 13 where the notch is not provided. At the lower part thereof, the second radial fluid bearing 20 is supported around the second land portion 19 between the second notch 13 and the third notch 14 where these notches are not provided. A spacer 21 is disposed between the fluid bearings.
各ラジアル流体軸受はケーシング２２内に収納され、非対称シャフト１１の下端部はスラスト流体軸受２３で支持している。また、ケーシング２２はその周囲を固定用ボルト２４によってホルダー２５に固定支持され、ホルダー２５の下端を加震部材２６に固定し、モータ１６の回転を精密制御し非対称シャフト１１を所定の回転数で回転をさせ、ロードセル２７で監視しながらその回転によって生じる振動を加震部材２６に与え、地中に振動を与えて震源として利用する点において、前記従来例と同様の構成をなしている。 Each radial fluid bearing is housed in a casing 22, and the lower end portion of the asymmetric shaft 11 is supported by a thrust fluid bearing 23. The casing 22 is fixedly supported around the holder 25 by fixing bolts 24, the lower end of the holder 25 is fixed to the vibration member 26, the rotation of the motor 16 is precisely controlled, and the asymmetric shaft 11 is rotated at a predetermined rotational speed. The structure is the same as that of the above-described conventional example in that it is rotated, and the vibration generated by the rotation is applied to the seismic member 26 while being monitored by the load cell 27, and the vibration is applied to the ground and used as an earthquake source.
本発明はこのようなＡＣＲＯＳＳにおいて、例えば上部の第１ラジアル流体軸受１８についてみると、第１切り欠き１２の下端部２８を第１ラジアル流体軸受１８の軸受面２９内まで下方に延長し、また第２切り欠き１３の上端部３０を軸受面２９内まで上方に延長しており、それによりこれらの切り欠きが形成されていない第１ランド部１７は従来のものより幅が狭くなっている。 In the ACROSS of the present invention, for example, when viewing the upper first radial fluid bearing 18, the lower end portion 28 of the first notch 12 extends downward into the bearing surface 29 of the first radial fluid bearing 18, and The upper end 30 of the second notch 13 extends upward to the inside of the bearing surface 29, so that the first land portion 17 in which these notches are not formed is narrower than the conventional one.
下部の第２ラジアル流体軸受２０についても同様に、第２切り欠き１３の下端部３１を第２ラジアル流体軸受２０の軸受面３２内まで下方に延長し、また第３切り欠き１４の上端部３３を軸受面３２内まで上方に延長しており、それによりこれらの切り欠きが形成されていない第２ランド部１９は従来のものより幅が狭くなっている。 Similarly for the lower second radial fluid bearing 20, the lower end 31 of the second notch 13 extends downward into the bearing surface 32 of the second radial fluid bearing 20, and the upper end 33 of the third notch 14. Is extended upward into the bearing surface 32, so that the second land portion 19 in which these notches are not formed is narrower than the conventional one.
このようなラジアル流体軸受においては、非対称シャフト１１の回転時に負荷の小さなランド部が形成されている部分の軸受面積が狭く、反対側の切り欠きが設けられていない高負荷側の軸受面積が広い、非対称流体軸受が構成される。この非対称流体軸受において、第１ラジアル流体軸受１８部分を拡大し、模式的に示したのが図２であり、この構成は第２ラジアル流体軸受２０についても同様である。 In such a radial fluid bearing, when the asymmetric shaft 11 rotates, the bearing area of the portion where the land portion with a small load is formed is narrow, and the bearing area on the high load side where the notch on the opposite side is not provided is wide. An asymmetric fluid bearing is configured. In this asymmetric fluid bearing, the first radial fluid bearing 18 is enlarged and schematically shown in FIG. 2, and this configuration is the same for the second radial fluid bearing 20.
図２において、非対称シャフト１１の図中左側の第１切り欠き１２が軸受面２９の内部にＬｃだけ延びており、第２切り欠き１３が同様に軸受面２９の内部にＬｃだけ延びていて、それにより低負荷側に形成される第１ランド部１７の表面としての軸受面の幅Ｌａは、その反対側の高負荷側の軸受面の幅Ｌｂより狭く形成されて、非対称流体軸受となっている。このように、非対称流体軸受の軸受面の幅の調整、即ち軸受面積の調整は、各切り欠きが軸受面に入り込む長さＬｃを調節することにより行うことができる。 In FIG. 2, the first notch 12 on the left side of the asymmetric shaft 11 extends in the bearing surface 29 by Lc, and the second notch 13 similarly extends in the bearing surface 29 by Lc. Thereby, the width La of the bearing surface as the surface of the first land portion 17 formed on the low load side is formed narrower than the width Lb of the bearing surface on the high load side on the opposite side to form an asymmetric fluid bearing. Yes. As described above, the adjustment of the width of the bearing surface of the asymmetric fluid bearing, that is, the adjustment of the bearing area, can be performed by adjusting the length Lc in which each notch enters the bearing surface.
この非対称流体軸受においては、環状に形成された流体供給路３４から複数個の孔３５により軸受面に圧力流体を供給するようにしている。この非対称流体軸受においては、負荷の状態に応じて切り欠きの深さ（Ｒ−Ｒｃ）、切り欠きが軸受面に入り込む長さ（Ｌｃ）、及び周方向の幅（切り欠き範囲の角度）を調節する。 In this asymmetric fluid bearing, a pressure fluid is supplied to the bearing surface through a plurality of holes 35 from an annular fluid supply passage 34. In this asymmetrical fluid bearing, the notch depth (R-Rc), the length of the notch entering the bearing surface (Lc), and the width in the circumferential direction (angle of the notch range) according to the load state. Adjust.
図１及び図２に示す実施例においては、本発明による非対称流体軸受を形成するに際して、流体軸受の両側に配置される非対称シャフト形成用の切り欠きを延長することによって形成した例を示したが、それ以外に例えば図３に示すように、非対称シャフト３５における幅Ｌｄの流体軸受の中心部に、幅Ｌｅの切り欠き３６を設け、それによりこの切り欠き３６の両側に軸受面を形成している。このような軸受構成によっても、非対称シャフトを形成するための切り欠き３６を用いて、低負荷側が高負荷側より軸受面積の小さな、非対称軸受を構成することができ、各軸受面に給気孔３７から加圧流体を供給し、中央の排気孔３８から排気することによって所定の流体軸受の作動を行わせることができる。 In the embodiment shown in FIG. 1 and FIG. 2, when forming the asymmetric fluid bearing according to the present invention, an example in which the asymmetric shaft forming notches arranged on both sides of the fluid bearing are extended is shown. In addition, as shown in FIG. 3, for example, a notch 36 having a width Le is provided at the center of a fluid bearing having a width Ld in the asymmetric shaft 35, thereby forming bearing surfaces on both sides of the notch 36. Yes. Even with such a bearing configuration, the notch 36 for forming the asymmetric shaft can be used to form an asymmetric bearing having a smaller bearing area on the low load side than on the high load side. A predetermined fluid bearing can be operated by supplying a pressurized fluid from the center and exhausting from the central exhaust hole 38.
図４は上記のような非対称流体軸受の軸方向圧力分布を模式的に示したもので、実線は負荷側の圧力分布、破線は反負荷側の圧力分布である。軸受反力は軸受面に作用する圧力に依存するから、反負荷側の軸受面積が小さく、圧力も低い非対称軸受の負荷容量は通常の対称形軸受に比べ飛躍的に向上する。また、軸受損失は軸受面積に比例するから、切り欠きを設けることにより、切り欠き面積に比例して軸受損失は減少する。 FIG. 4 schematically shows the axial pressure distribution of the asymmetric fluid bearing as described above. The solid line represents the pressure distribution on the load side, and the broken line represents the pressure distribution on the anti-load side. Since the bearing reaction force depends on the pressure acting on the bearing surface, the load capacity of an asymmetric bearing having a small bearing area on the anti-load side and a low pressure is dramatically improved as compared with a normal symmetrical bearing. Since the bearing loss is proportional to the bearing area, providing the notch reduces the bearing loss in proportion to the notch area.
図５には従来の対称流体軸受と本発明の非対称流体軸受との偏心率に対する負荷容量の計算結果の比較を示す。この計算においては、本発明の非対称軸受として、給気構造はスロットル絞り形式で軸受面長さの半分が切り欠きになっている構造のものを用い、直径６０ｍｍ、軸受長さ1２０ｍｍ、給気圧力６ｋｇｆ／cm2、軸受すきま３０μｍである。非対称軸受の無回転状態では、軸受面積の差で生じる負荷容量分だけ切り欠きを設けた軸受面側に回転軸が偏って停止している。回転上昇により非対称構造を持つ回転軸に遠心力が働くため回転軸は、軸受中心を通り負荷側（切り欠きの無い側）に向かって移動していき、通常の対称軸受より偏心量を大きくとれるため大きな負荷を支持できることが分かる。 FIG. 5 shows a comparison of the calculation results of the load capacity with respect to the eccentricity between the conventional symmetric fluid bearing and the asymmetric fluid bearing of the present invention. In this calculation, as the asymmetric bearing of the present invention, the air supply structure is a throttle throttle type and has a structure in which half of the bearing surface length is notched, and has a diameter of 60 mm, a bearing length of 120 mm, and an air supply pressure. 6 kgf / cm @ 2 and bearing clearance 30 .mu.m. In the non-rotating state of the asymmetric bearing, the rotating shaft is biased and stopped on the bearing surface side provided with a notch corresponding to the load capacity caused by the difference in bearing area. Since the centrifugal force acts on the rotating shaft with an asymmetric structure due to the rotation rise, the rotating shaft moves toward the load side (the side without the notch) through the bearing center, and can take a larger amount of eccentricity than a normal symmetrical bearing. Therefore, it turns out that a big load can be supported.
図６に従来の対称流体軸受と本発明の非対称流体軸受との偏心率に対する負荷容量の計算結果の比較を示す。計算における本発明の非対称軸受では、給気構造はスロットル絞り形式で軸受面長さの半分が切り欠きになっている構造で、直径６０ｍｍ、軸受長さ1２０ｍｍ、給気圧力６ｋｇｆ／cm2、軸受すきま３０μｍである。非対称軸受の無回転状態では、軸受面積の差で生じる負荷容量分だけ切り欠きを設けた軸受面側に回転軸が偏って停止している。回転上昇により非対称構造を持つ回転軸に遠心力が働くため回転軸は、軸受中心を通り負荷側（切り欠きのない側）に向かって移動していき、通常の対称軸受より偏心量を大きくとれるため大きな負荷を支持できることが分かる。 FIG. 6 shows a comparison of the calculation results of the load capacity with respect to the eccentricity between the conventional symmetric fluid bearing and the asymmetric fluid bearing of the present invention. In the calculation of the asymmetrical bearing according to the present invention, the air supply structure is a throttle throttle type with half of the bearing surface length notched, with a diameter of 60 mm, a bearing length of 120 mm, an air supply pressure of 6 kgf / cm2, and a bearing clearance. 30 μm. In the non-rotating state of the asymmetric bearing, the rotating shaft is biased and stopped on the bearing surface side provided with a notch corresponding to the load capacity caused by the difference in bearing area. Centrifugal force acts on the rotating shaft with an asymmetrical structure due to the rotation rise, so the rotating shaft moves toward the load side (the side without notches) through the center of the bearing, and can take a larger amount of eccentricity than a normal symmetrical bearing. Therefore, it turns out that a big load can be supported.
図６として示す表に２０tf級の精密制御定常震源について概略計算した本発明の非対称流体軸受と従来の対称流体軸受の負荷容量をほぼ同一としたときの軸受一個あたりの特性比較を示す。負荷容量を同一とすると、軸受流量で６０％の減少、軸受摩擦で４９％の減少であり、総動力でほぼ５０％低下できることがわかる。 The table shown as FIG. 6 shows a characteristic comparison per bearing when the load capacities of the asymmetric fluid bearing of the present invention and the conventional symmetric fluid bearing, which are roughly calculated for a 20 tf-class precision controlled steady-state earthquake source, are almost the same. It can be seen that if the load capacity is the same, the bearing flow rate is reduced by 60%, the bearing friction is reduced by 49%, and the total power can be reduced by almost 50%.
上記実施例は本発明を精密制御定常震源に適用した例を示したが、それ以外に、大負荷で作動する機器や加振器のような大きな衝撃負荷を発生する機器のラジアル軸受として広範囲に用いることができる。 In the above embodiment, the present invention is applied to a precision controlled steady-state epicenter, but in addition to this, it is widely used as a radial bearing for equipment that generates a large impact load such as equipment that operates with a large load or a vibrator. Can be used.
１１ 非対称シャフト
１２ 第１切り欠き
１３ 第２切り欠き
１４ 第３切り欠き
１５ カップリング
１６ モータ
１７ 第１ランド部
１８ 第１ラジアル流体軸受
１９ 第２ランド部
２０ 第２ラジアル流体軸受
２１ スペーサ
２２ ケーシング
２３ スラスト流体軸受
２４ 固定用ボルト
２５ ホルダー
２６ 加震部材
２７ ロードセル
２８ 第１切り欠き１２の下端部
２９ 軸受面
３０ 第２切り欠き１３の上端部
３１ 第２切り欠き１３の下端部
３２ 軸受面
３３ 第３切り欠き１３の上端部
DESCRIPTION OF SYMBOLS 11 Asymmetric shaft 12 1st notch 13 2nd notch 14 3rd notch 15 Coupling 16 Motor 17 1st land part 18 1st radial fluid bearing 19 2nd land part 20 2nd radial fluid bearing 21 Spacer 22 Casing 23 Thrust fluid bearing 24 Fixing bolt 25 Holder 26 Seismic member 27 Load cell 28 Lower end portion of first notch 12 29 Bearing surface 30 Upper end portion of second notch 13 31 Lower end portion of second notch 13 32 Bearing surface 33 First Upper end of 3 notches 13
Claims (4)
前記非対称負荷を与える切り欠き部を前記流体軸受の軸受面内にも設け、切り欠きを設けない負荷側の軸受面より切り欠きを設ける反負荷側の軸受面を狭く形成したことを特徴とする非対称流体軸受。 In a radial fluid bearing that supports an asymmetric shaft that gives an asymmetric load during rotation by providing a notch on a part of one side,
The notched portion for providing the asymmetric load is also provided in the bearing surface of the fluid dynamic bearing, and the bearing surface on the non-load side where the notch is provided is narrower than the bearing surface on the load side where the notch is not provided. Asymmetric fluid bearing.
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2009092195A (en) * | 2007-10-11 | 2009-04-30 | Daiya Seiki Co Ltd | Static pressure fluid bearing |
| CN104155684A (en) * | 2014-08-25 | 2014-11-19 | 中国矿业大学 | Self-compensating controlled seismic source for seismic wave CT detection of underground coal seam working face impact danger zone and seismic source generation method |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH10142345A (en) * | 1996-11-08 | 1998-05-29 | Fuji Electric Co Ltd | Rotary seismic source unit |
| JP2000146748A (en) * | 1998-11-17 | 2000-05-26 | Shinken:Kk | Vibration generator |
| JP2003301841A (en) * | 2002-04-11 | 2003-10-24 | Ntn Corp | Hydrostatic gas bearing, and spindle device using the same |
-
2005
- 2005-01-27 JP JP2005019127A patent/JP4484109B2/en not_active Expired - Fee Related
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH10142345A (en) * | 1996-11-08 | 1998-05-29 | Fuji Electric Co Ltd | Rotary seismic source unit |
| JP2000146748A (en) * | 1998-11-17 | 2000-05-26 | Shinken:Kk | Vibration generator |
| JP2003301841A (en) * | 2002-04-11 | 2003-10-24 | Ntn Corp | Hydrostatic gas bearing, and spindle device using the same |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2009092195A (en) * | 2007-10-11 | 2009-04-30 | Daiya Seiki Co Ltd | Static pressure fluid bearing |
| CN104155684A (en) * | 2014-08-25 | 2014-11-19 | 中国矿业大学 | Self-compensating controlled seismic source for seismic wave CT detection of underground coal seam working face impact danger zone and seismic source generation method |
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