JP3233685B2 - Hybrid bearing - Google Patents
Hybrid bearingInfo
- Publication number
- JP3233685B2 JP3233685B2 JP13692492A JP13692492A JP3233685B2 JP 3233685 B2 JP3233685 B2 JP 3233685B2 JP 13692492 A JP13692492 A JP 13692492A JP 13692492 A JP13692492 A JP 13692492A JP 3233685 B2 JP3233685 B2 JP 3233685B2
- Authority
- JP
- Japan
- Prior art keywords
- bearing
- load
- shaft
- split
- oil film
- 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
- Sliding-Contact Bearings (AREA)
- Magnetic Bearings And Hydrostatic Bearings (AREA)
Description
【０００１】[0001]
【産業上の利用分野】本発明は、回転機械に用いられる
軸受、特に、運転範囲が広く、軸受荷重が非常に小さく
なる領域の運転を含む高回転数の回転機械に用いられる
軸受に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a bearing used for a rotating machine, and more particularly to a bearing used for a rotating machine having a wide operating range and a high rotating speed including an operation in a region where a bearing load is extremely small.
【０００２】[0002]
【従来の技術】従来の代表的な軸受として、軸受安定性
に優れた分割軸受や、軸受背面をダンパ構造としたダン
パ形分割軸受がある。2. Description of the Related Art As conventional representative bearings, there are a split bearing having excellent bearing stability and a damper-type split bearing having a damper structure on the back surface of the bearing.
【０００３】ダンパ分割軸受には、ラジアル荷重を図７
に示すようにすべり軸受としたものと、図８のように転
がり軸受としたものとがある。図７において、１５はダ
ンパ軸受支持用板ばね、１６は軸受パッド、１７はパッ
ド支持ピボット、１８は背面ダンパ、２０は軸を示して
いる。図８において、１９はダンパ軸受支持用丸棒、２
１は背面ダンパ、２２は転がり軸受を示している。[0003] The damper split bearing, FIG radial load 7
There to those with sliding bearing as shown in, and those with rolling bearings as shown in FIG. 8. 7 , reference numeral 15 denotes a leaf spring for supporting a damper bearing, 16 denotes a bearing pad, 17 denotes a pad supporting pivot, 18 denotes a rear damper, and 20 denotes a shaft. In FIG. 8 , 19 is a round bar for supporting a damper bearing, 2
Reference numeral 1 denotes a rear damper, and 22 denotes a rolling bearing.
【０００４】高速回転機械において、振動の小さい安定
的な運転状態を実現するためには通常の危険速度の有
無、不釣合い応答特性の良否に加えて軸系安定性の確認
検討が不可欠であり、特に軸系安定性が機械の成否を左
右する。[0004] In a high-speed rotating machine, in order to realize a stable operation state with small vibration, it is indispensable to confirm the presence / absence of a normal critical speed, the quality of unbalanced response characteristics, and the stability of the shaft system. In particular, shaft system stability determines the success or failure of the machine.
【０００５】従来、分割軸受は油膜係数の連成項が生じ
ないため、絶対的に安定な軸受として安定性の検討はな
されていなかった。しかし、高速回転機での運転になる
と、軸受荷重が小さいため、油膜係数の主対角項も小さ
くなり、軸受パッド自身の慣性効果により生じる油膜係
数の連成項が無視できなくなり不安定振動が発生する。Conventionally, split bearings do not involve a coupled term of the oil film coefficient, and therefore, no study has been made on the stability as an absolutely stable bearing. However, when operating with a high-speed rotating machine, the bearing load is small, so the main diagonal term of the oil film coefficient also becomes small, and the coupled term of the oil film coefficient caused by the inertia effect of the bearing pad itself cannot be ignored, causing unstable vibration. appear.
【０００６】このため、パッド枚数を増やし１個あたり
のパッド慣性を低減したり、パッドの裏側を切除するな
どパッド慣性を減らし、安定性能改善を実施中であるが
充分な安定性を確保できない。特に、軽荷重域では油膜
剛性が小さく不安定となり易い。For this reason, the pad performance is being improved by increasing the number of pads to reduce the pad inertia per pad or by cutting off the back side of the pad to improve the stability performance. However, sufficient stability cannot be secured. In particular, in a light load range, the oil film rigidity is small and tends to be unstable.
【０００７】一方、ダンパ形軸受についていえば、高速
回転機械の軸受は、一般に小さくなるためダンパ軸受の
芯保持が非常に困難となり、信頼性の高いダンパ特性が
得にくい。On the other hand, regarding the damper type bearing, since the bearing of a high-speed rotating machine is generally small, it is very difficult to hold the core of the damper bearing, and it is difficult to obtain highly reliable damper characteristics.
【０００８】また、ダンパー油膜のばね係数ＫE は、Ｋ
E ＝Ｋd −Ｍω2 （ここでＭは可動部重量、ωは回転角
速度）で示されるが、回転数が高くなるとＭω2 の項が
大きくなるため、ＫE の絶対値が大きくなり、ダンパー
部が可動しにくくなり、ダンパー減衰による有効な制振
効果が期待できない。The spring coefficient K E of the damper oil film is K
E = K d −Mω 2 (where M is the weight of the movable portion and ω is the rotational angular velocity). As the number of rotations increases, the term of Mω 2 increases, so that the absolute value of K E increases and the damper The part becomes difficult to move, and an effective vibration damping effect due to damper damping cannot be expected.
【０００９】このように、近年の高速、軽荷重の軸系に
ついては、充分な軸系安定性を確保できず、従来技術で
は限界に近づいている。As described above, with regard to the recent high-speed, light-load shaft system, sufficient shaft system stability cannot be secured, and the conventional technology is approaching its limit.
【００１０】[0010]
【発明が解決しようとする課題】本発明は、前述の従来
の軸受にみられた欠点を解消し、高速軽荷重の運転状態
を含む回転機械の安定性を向上させうる軸受を提供する
ことを目的としている。SUMMARY OF THE INVENTION An object of the present invention is to provide a bearing which can solve the above-mentioned drawbacks of the conventional bearing and can improve the stability of a rotating machine including a high-speed and light-load operating state. The purpose is.
【００１１】特に、本発明では、単なる高速軽荷重軸受
の安定性を増すというのではなく、運転範囲内に軽荷重
状態があるもの、即ち、重荷重から軽荷重状態を含む運
転荷重範囲の広い機械に対して安定的な軸受性能をもつ
軸受を提供することを課題としている。In particular, according to the present invention, the stability of a high-speed light-load bearing is not simply increased, but a light-load condition exists in the operating range, that is, a wide operating load range including a heavy load to a light load condition. It is an object to provide a bearing having stable bearing performance for a machine.
【００１２】[0012]
【課題を解決するための手段】本発明では、前記課題を
解決するため軸受に対し次の手段を採用している。According to the present invention, the following means are employed for a bearing to solve the above-mentioned problems.
【００１３】（１）油膜の動圧効果を利用する分割軸受
形の負荷面と、軸を定められた方向に強制的に偏心させ
る力を生じさせるオフセット加工部をもつスリーブ軸受
とを組み合せる。( 1 ) A load surface of a split bearing type utilizing a dynamic pressure effect of an oil film is combined with a sleeve bearing having an offset portion for generating a force for forcibly eccentrically moving a shaft in a predetermined direction.
【００１４】（２）油膜の動圧効果を利用する分割軸受
形の負荷面と、軸を定められた方向に強制的に偏心させ
る力を生ずる圧力ダムをもつ中央溝を形成したスリーブ
軸受とを組み合せる。( 2 ) A split bearing type load surface utilizing a dynamic pressure effect of an oil film, and a sleeve bearing having a central groove having a pressure dam which generates a force for forcibly eccentrically moving a shaft in a predetermined direction. Combine.
【００１５】[0015]
【作用】（１）油膜の動圧効果を利用する分割軸受形の
負荷面と、軸を定められた方向に強制的に偏心させる力
を生じさせるオフセット加工部をもつスリーブ軸受とを
組み合せたものでは、荷重は分割軸受形の負荷面で受
け、高速域で軸受荷重が軽くなり分割軸受でも不安定と
なりうる領域では分割軸受の反対側に配設されたオフセ
ット加工したスリーブ軸受の油膜反力で軸を分割軸受側
に押して等価荷重を大きくし軸系の安定性を向上させ
る。[Function] ( 1 ) A combination of a split bearing type load surface utilizing a dynamic pressure effect of an oil film and a sleeve bearing having an offset portion for generating a force for forcibly eccentrically moving a shaft in a predetermined direction. In this case, the load is received on the load surface of the split bearing type, and in the region where the bearing load becomes light at high speed and the split bearing becomes unstable, the oil film reaction force of the offset processed sleeve bearing installed on the opposite side of the split bearing The shaft is pushed toward the split bearing to increase the equivalent load and improve the stability of the shaft system.
【００１６】（２）油膜の動圧効果を利用する分割軸受
形の負荷面と、軸を定められた方向に強制的に偏心させ
る力を生ずる圧力ダムをもつ中央溝を形成したスリーブ
軸受を組み合せたものでは、下向き荷重の場合には従来
の圧力型軸受に近い特性を示すが上向き荷重の時には分
割軸受の安定的な特性を期待でき、かつスリーブ軸受メ
タルの中央溝の圧力ダムでせき止られて生じる油膜圧力
により軸を分割軸受側に押える。このため、分割軸受で
安定性が悪化する軽負荷状態を作らないようにすること
ができる。( 2 ) Combination of a split bearing type load surface utilizing the dynamic pressure effect of an oil film and a sleeve bearing having a central groove having a pressure dam which generates a force for forcibly eccentrically moving a shaft in a predetermined direction. In the case of a downward load, the characteristics are similar to those of a conventional pressure type bearing, but in the case of an upward load, the stable characteristics of the split bearing can be expected, and it is blocked by the pressure dam in the central groove of the sleeve bearing metal. The shaft is pressed to the split bearing side by the oil film pressure generated. For this reason, it is possible to prevent the split bearing from creating a light load state in which stability is deteriorated.
【００１７】[0017]
【実施例】（実施例１） 以下、本発明を図示した実施例に基いて具体的に説明す
る。Embodiment (Embodiment 1) Hereinafter, the present invention will be specifically described based on an illustrated embodiment.
【００１８】まず、広範囲な軸受荷重変化のある回転軸
系の例として歯車駆動方式によるコンプレッサー軸の軸
受について図３、図４によって説明する。図３、図４に
おいて、モータ８がフレキシブルカップリング９を介し
てホイール軸１２に連結されている。 First , as an example of a rotating shaft system having a wide range of bearing load changes, a shaft of a compressor shaft by a gear drive system is used.
3 with the receiving will be described by Figure 4. 3 and 4 , a motor 8 is connected to a wheel shaft 12 via a flexible coupling 9.
【００１９】１０′は、ホイール軸を支える従来形の軸
受、１１はホイールである。ホイール１１はピニオン１
４と噛み合っている。１３はピニオン１４が取付けられ
たコンプレッサ軸で、コンプレッサ軸１３を支持するの
に図１に示したハイブリッド軸受が用いられている。Reference numeral 10 'denotes a conventional bearing for supporting a wheel shaft, and reference numeral 11 denotes a wheel. Wheel 11 is pinion 1
4 is engaged. Reference numeral 13 denotes a compressor shaft to which a pinion 14 is attached, and the hybrid bearing shown in FIG. 1 is used to support the compressor shaft 13.
【００２０】この図３、図４に示すコンプレッサー軸１
３の軸受１０に関し、軸系安定性に重大な影響を与える
軸受荷重について、実際の運用を想定して説明すれば次
のようになる。コンプレッサー軸１３はホイール１１と
ピニオン１４の噛み合いにより噛み上げられるのでコン
プレッサー軸１３の軸受１０は負荷に応じた上向きの力
を受ける。（図４参照）この場合、起動時には無負荷で
あるので軸受荷重はロータの自重に応じた下向きの荷重
を受けている。但し、通常定格負荷の場合には噛み上げ
による荷重が自重に比べ相当に大きくなる。[0020] FIG. 3, the compressor shaft 1 shown in FIG. 4
Regarding the bearing 10 of No. 3, the bearing load that significantly affects the stability of the shaft system will be described assuming actual operation as follows. Since the compressor shaft 13 is engaged by the engagement between the wheel 11 and the pinion 14, the bearing 10 of the compressor shaft 13 receives an upward force according to the load. (See FIG. 4) In this case, bearing load because at startup is unloaded is under downward load corresponding to the own weight of the rotor. However, in the case of a normal rated load, the load due to biting is considerably larger than its own weight.
【００２１】このため、実機では無負荷で定格回転数ま
で回転上昇させた後、負荷をかける段階で噛み上げによ
る上向き荷重とロータ自重による軸受荷重が釣り合い、
有効な軸受荷重がゼロとなり、極めて安定性の悪い領域
が存在する。For this reason, in the actual machine, after rotating up to the rated speed with no load, the upward load due to biting and the bearing load due to the rotor's own weight are balanced at the stage of applying the load.
The effective bearing load becomes zero and there is a region with extremely poor stability.
【００２２】また、負荷によっては軸受荷重がゼロには
ならないまでも非常に小さくなる領域が存在すること
で、軸系の安定性が確保できない。以上のことを踏ま
え、図３に示すコンプレッサー軸１３に図１及び図２に
示す軸受を採用することで軸受の荷重が極端に軽くなる
領域を無くすことができ軸系の安定的な運転が可能とな
る。Further, depending on the load, there is a region where the bearing load becomes very small even if it does not become zero, so that the stability of the shaft system cannot be ensured. Based on the above, by adopting the bearings shown in FIGS . 1 and 2 for the compressor shaft 13 shown in FIG. 3 , the region where the load on the bearing becomes extremely light can be eliminated and the shaft system can be operated stably. Becomes
【００２３】図１において、１は軸受パッド、２はパッ
ド支持ピボット、３は軸受裏金、４は給油穴、７はスリ
ーブ軸受メタルを示している。In FIG. 1, reference numeral 1 denotes a bearing pad, 2 denotes a pad supporting pivot, 3 denotes a bearing backing, 4 denotes an oil supply hole, and 7 denotes a sleeve bearing metal.
【００２４】図２において、２５は軸受パッドの加工曲
率による隙間円、２６はスリーブ軸受の加工曲率による
隙間円、そしてＡは、前記隙間円２５，２６により定ま
る本発明によるハイブリッド軸受の隙間円を示してい
る。In FIG. 2 , 25 is a gap circle due to the working curvature of the bearing pad, 26 is a gap circle due to the working curvature of the sleeve bearing, and A is a gap circle of the hybrid bearing according to the present invention determined by the gap circles 25 and 26. Is shown.
【００２５】本実施例は、軸受パッド１をもつ分割軸受
と、通常オフセット加工して構成する２円弧軸受の片側
の部分円弧軸受としてのスリーブ軸受メタル７を組み合
せたハイブリッド軸受である。The present embodiment is a hybrid bearing in which a split bearing having a bearing pad 1 and a sleeve bearing metal 7 as a partial arc bearing on one side of a two-arc bearing usually formed by offset machining.
【００２６】ここで、分割軸受は軸受パッド１に生じる
動圧効果で軸受荷重を支持するものであり、部分円弧軸
受としてのスリーブ軸受メタル７は軸受負荷面も兼ねる
が主目的は部分円弧軸受に生じる油膜圧力により、軸を
反対方向に押しつける荷重を得るためのものである。Here, the split bearing supports the bearing load by a dynamic pressure effect generated in the bearing pad 1. The sleeve bearing metal 7 as a partial arc bearing also serves as a bearing load surface, but its main purpose is to use a partial arc bearing. The purpose is to obtain a load for pressing the shaft in the opposite direction by the generated oil film pressure.
【００２７】この結果、本実施例のハイブリッド軸受で
は安定性が問題となる軽荷重域が出来ないので軸系の安
定性を著しく高めることが出来る。As a result, in the hybrid bearing of the present embodiment, a light load region where stability is a problem cannot be formed, so that the stability of the shaft system can be significantly improved.
【００２８】この第１実施例の軸受の作用について更に
説明する。起動時は無負荷であるので軸受荷重は下向き
にロータ自重のみを受ける。但し、軸受１０はロータ自
重よりもはるかに大きい上向きの噛み上げ反力を想定し
た設計を行うので下向き荷重を支持する部分円弧軸受と
してのスリーブ軸受メタル７は十分な余裕を持って下向
き荷重に対応できる。また楕円率が大きくなるよう部分
円弧軸受としてのスリーブ軸受メタル７を組み込むこと
で下向き荷重に対する軸受安定性を確保できる。The operation of the bearing of the first embodiment will be further described. Since there is no load at startup, the bearing load receives only the rotor's own weight in the downward direction. However, since the bearing 10 is designed on the assumption of an upward biting reaction force much larger than the rotor's own weight, the sleeve bearing metal 7 as a partial arc bearing that supports a downward load has a sufficient margin to cope with the downward load. it can. In addition, by incorporating the sleeve bearing metal 7 as a partial arc bearing so as to increase the ellipticity, the bearing stability against a downward load can be secured.
【００２９】回転数を定格まで上昇・下降させる段階で
噛み上げ反力がロータ自重とバランスし、有効な軸受荷
重がゼロになる領域あるいは低負荷領域でコンプレッサ
ーが運用される場合には、従来の軸受では非常に不安定
となる。When the compressor is operated in a region where the effective bearing load is zero or in a low load region, the conventional countermeasures are taken when the rotational speed is raised or lowered to the rated value, and the reaction force is balanced with the rotor's own weight. The bearing is very unstable.
【００３０】これに対して、本実施例の軸受では偏心率
の小さい、つまり軽荷重時に限って部分円弧軸受である
スリーブ軸受メタル７に油膜圧力が発生して軸をティル
パッド側に押し付ける作用が生じる。On the other hand, in the bearing of this embodiment, an oil film pressure is generated on the sleeve bearing metal 7 which is a partial arc bearing only when the eccentricity is small, that is, only when the load is light, so that the shaft is pressed against the tilt pad side. Occurs.
【００３１】これによって、軸１３の平衡点が中心より
ずれ分割軸受としての軸受パッド１にとっては、等価な
軸受荷重が作用した状況となるので分割軸受の安定性能
を確保できる。As a result, the equilibrium point of the shaft 13 deviates from the center, and the bearing pad 1 as a split bearing is in a state where an equivalent bearing load is applied, so that the stable performance of the split bearing can be ensured.
【００３２】また、定格荷重で荷重が上向きの時におけ
る部分円弧に生じる油膜圧力の悪影響は無い。この状態
では部分円弧側の軸受すきまが大きいので油膜圧力が小
さく、ほとんど影響を与えない。Further, there is no adverse effect of the oil film pressure generated in the partial arc when the load is upward at the rated load. In this state, since the bearing clearance on the partial arc side is large, the oil film pressure is small and has little effect.
【００３３】（実施例２） 図５、図６において、図１と同様の部分には図１と同一
の符号を付してあり、本軸受も図３、図４に示す歯車駆
動方式によるコンプレッサーの軸１３の軸受１０に使用
する場合を考える。[0033] (Embodiment 2) FIG. 5, 6, the same parts as FIG. 1 are denoted by the same reference numerals as in FIG. 1, the present bearing 3, the compressor according to the gear driving system shown in FIG. 4 The case where the shaft 13 is used for the bearing 10 of the shaft 13 will be considered.
【００３４】３５はスリーブ軸受メタル７に設けた中央
溝、３６は同中央溝３５の圧力ダムである。Reference numeral 35 denotes a central groove provided in the sleeve bearing metal 7, and reference numeral 36 denotes a pressure dam of the central groove 35.
【００３５】本実施例では高速域の安定性を確保する意
味で荷重を受ける側には分割軸受としての軸受パッド１
を配置し、高速域で軸受荷重が軽くなり分割軸受でも不
安定となり得る領域に対して、分割軸受の反対側にオフ
セット加工した圧力型軸受としてのスリーブ軸受メタル
７を配置することで安定性を高める。In this embodiment, a bearing pad 1 as a split bearing is provided on the side receiving a load in order to secure stability in a high speed range.
In a region where the bearing load is reduced in the high-speed range and the split bearing may become unstable, the sleeve bearing metal 7 as a pressure bearing is machined to the opposite side of the split bearing to improve stability. Enhance.
【００３６】一般にスリーブ軸受の場合には中・低速の
回転数で比較的に軸受荷重の大きいものに用いられるが
安定作動域が狭い。これに対して、分割軸受では軸受荷
重が小さく高速回転域を除けばほぼ全域で軸系安定性を
確保できる。In general, in the case of a sleeve bearing, it is used for bearings having a relatively large bearing load at medium and low speeds, but has a narrow stable operation range. On the other hand, in the case of the split bearing, the bearing load is small, and the shaft system stability can be secured in almost the entire region except the high-speed rotation region.
【００３７】従って、本実施例の軸受構造によれば中央
溝３５を設けたスリーブ軸受メタル７からなる圧力型軸
受の中央溝３５の圧力ダム３６のせき止め油膜圧力によ
り軸を押し上げることで強制的に分割軸受側に作用する
等価荷重を大きくして、軸系安定性を向上させる。Therefore, according to the bearing structure of this embodiment, the shaft is forcibly pushed up by the damping oil film pressure of the pressure dam 36 in the central groove 35 of the pressure type bearing formed of the sleeve bearing metal 7 having the central groove 35. The equivalent load acting on the split bearing side is increased to improve the shaft system stability.
【００３８】すなわち、中央溝３５と圧力ダム３６を設
けたスリーブ軸受メタル７は、軸受負荷面も兼ねるが主
目的はこの圧力型軸受の中央溝３５のせき止め部に相当
する圧力ダム３６に発生する油膜圧力により、軸１３を
反対方向に押しつける荷重を得るためのものである。That is, the sleeve bearing metal 7 provided with the central groove 35 and the pressure dam 36 also serves as a bearing load surface, but the main purpose is generated in the pressure dam 36 corresponding to the dam portion of the central groove 35 of this pressure type bearing. This is for obtaining a load for pressing the shaft 13 in the opposite direction by the oil film pressure.
【００３９】この結果、本実施例のハイブリッド軸受で
は安定性が問題となる軽荷重域が出来ないので軸系の安
定性を著しく高めることが出来る。以下これを説明す
る。As a result, in the hybrid bearing of this embodiment, a light load region where stability is a problem cannot be formed, so that the stability of the shaft system can be remarkably enhanced. This will be described below.
【００４０】起動時は、無負荷であるので軸受荷重は下
向きにロータ自重のみを受ける。但し、軸受１０はロー
タ自重よりもはるかに大きい上向きの噛み上げ反力を想
定した設計を行うので下向き荷重を支持する圧力型軸受
としてのスリーブ軸受メタル７は十分な余裕を持って下
向き荷重に対応できる。At the time of starting, since there is no load, the bearing load receives only the rotor's own weight in the downward direction. However, since the bearing 10 is designed on the assumption of an upward biting reaction force much larger than the rotor's own weight, the sleeve bearing metal 7 as a pressure type bearing that supports a downward load has a sufficient margin to cope with the downward load. it can.
【００４１】回転数を定格まで上昇・下降させる段階で
噛み上げ反力がロータ自重とバランスし、有効な軸受荷
重がゼロになる領域あるいは低負荷領域でコンプレッサ
ーが運用される場合には、従来の軸受では非常に不安定
となる。When the compressor is operated in a region where the effective bearing load is zero or in a low load region, the conventional reaction force balances with the rotor's own weight at the stage of raising and lowering the rotation speed to the rated value. The bearing is very unstable.
【００４２】これに対して、本実施例では偏心率の小さ
い、つまり軽荷重時に限ってスリーブ軸受メタルの中央
溝３５の圧力ダム３６に生じる油膜圧力により軸１３を
ティルパッド側に押し付ける作用が生じる。On the other hand, in this embodiment, the oil film pressure generated in the pressure dam 36 in the central groove 35 of the sleeve bearing metal has an effect of pressing the shaft 13 toward the tilt pad only when the eccentricity is small, that is, only when the load is light. .
【００４３】これによって、軸１３の平衡点が中心より
ずれ分割軸受にとっては、等価な軸受荷重が作用した状
況となるので分割軸受の安定性能を確保できる。Thus, the equilibrium point of the shaft 13 is deviated from the center, and the equivalent bearing load is applied to the divided bearing, so that the stable performance of the divided bearing can be ensured.
【００４４】また、定格荷重で荷重が上向きの時におけ
るスリーブ軸受メタル７の油膜圧力の悪影響は無い。こ
の状態では軸の平衡点は分割軸受側にあり、スリーブ軸
受メタル７側の軸受すきまが大きいので油膜圧力が小さ
く、ほとんど影響を与えない。There is no adverse effect of the oil film pressure on the sleeve bearing metal 7 when the load is upward at the rated load. In this state, the equilibrium point of the shaft is on the split bearing side and the bearing clearance on the sleeve bearing metal 7 side is large, so that the oil film pressure is small and has little effect.
【００４５】[0045]
【発明の効果】以上具体的に説明したように、本発明で
は、動圧効果を利用する負荷面と、オフセット加工部、
又は圧力ダムつきの中央溝をもつスリーブ軸受を組み合
せるという簡単な手段によって軸系の安定性が悪化する
軽負荷状態を作らないよう軸負荷を調節できるものであ
る。しかも、通常の負荷状態では分割軸受として優れた
軸受安定性を発揮する。As described above specifically, according to the present invention, the present invention, the load surface utilizing a dynamic pressure effect, offset processing unit,
Or combined with sleeve bearing with central groove with pressure dam
This makes it possible to adjust the shaft load so as not to create a light load state in which the stability of the shaft system is deteriorated by simple means of causing the shaft load to deteriorate. In addition, under normal load conditions, the bearing exhibits excellent bearing stability as a split bearing.
【００４６】従って、運転範囲内に軽荷重状態を含むよ
うな重荷重から軽荷重状態までの広い運転範囲の回転機
械に対し安定性の良い軸受として作動できるのである。Therefore, it is possible to operate as a stable bearing for a rotating machine in a wide operation range from a heavy load to a light load state including a light load state within the operation range.
【図１】本発明の１実施例による軸受の縦断面図。FIG. 1 is a longitudinal sectional view of a bearing according to one embodiment of the present invention.
【図２】図１に示す軸受における隙間円を示す図面。[Figure 2] illustrates the clearance circle of the bearing shown in Figure 1.
【図３】本発明による軸受を適用するコンプレッサーの
軸系を示す系統図。FIG. 3 is a system diagram showing a shaft system of a compressor to which the bearing according to the present invention is applied.
【図４】図３におけるホイールとピニオンの噛み合い状
態を示す側面図。FIG. 4 is a side view showing an engaged state between the wheel and the pinion in FIG. 3 ;
【図５】本発明の他の実施例による軸受の縦断面図。FIG. 5 is a longitudinal sectional view of a bearing according to another embodiment of the present invention.
【図６】図５に示す軸受におけるスリーブ軸受メタルの
展開図。FIG. 6 is a development view of a sleeve bearing metal in the bearing shown in FIG. 5 ;
【図７】従来の軸受を示す部分的断面図。FIG. 7 is a partial sectional view showing a conventional bearing.
【図８】従来の他の軸受を示す部分的断面図。FIG. 8 is a partial sectional view showing another conventional bearing.
１ 軸受パッド ２ パッド支持ピボット ３ 軸受裏金 ４ 給油穴 ７ スリーブ軸受メタル １０ ハイブリッド軸受 １３ 回転軸 ３５ 中央溝 ３６ 圧力ダム DESCRIPTION OF SYMBOLS 1 Bearing pad 2 Pad supporting pivot 3 Bearing back metal 4 Oil supply hole 7 Sleeve bearing metal 10 Hybrid bearing 13 Rotation shaft 35 Central groove 36 Pressure dam
───────────────────────────────────────────────────── フロントページの続き (72)発明者 後藤 充成 長崎市飽の浦町１番１号 三菱重工業株 式会社長崎造船所内 (72)発明者 伊高 英彦 長崎市飽の浦町１番１号 三菱重工業株 式会社長崎造船所内 (72)発明者 成末 繁利 長崎市飽の浦町１番１号 三菱重工業株 式会社長崎造船所内 (56)参考文献 特開 平１−255718（ＪＰ，Ａ) 実開 昭56−17414（ＪＰ，Ｕ) (58)調査した分野(Int.Cl.7，ＤＢ名) F16C 32/00 - 32/06 F16C 17/00 - 17/26 F16C 33/00 - 33/28 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Mitsunari Goto 1-1, Akunoura-cho, Nagasaki-shi Mitsubishi Heavy Industries, Ltd. Inside Nagasaki Shipyard (72) Inventor Hidehiko Itaka 1-1-1, Akunoura-cho, Nagasaki-shi Mitsubishi Heavy Industries, Ltd. In Nagasaki Shipyard, Ltd. (72) Inventor Shigetoshi Arisue 1-1, Akunouracho, Nagasaki-shi In Nagasaki Shipyard, Mitsubishi Heavy Industries, Ltd. (56) References JP-A-1-255718 (JP, A) 17414 (JP, U) (58) Fields investigated (Int. Cl. 7 , DB name) F16C 32/00-32/06 F16C 17/00-17/26 F16C 33/00-33/28
Claims (2)
転軸の回転に伴う油膜の動圧効果を利用する分割軸受形
の負荷面及び前記回転軸を定められた方向に強制的に偏
心させる力を生じるオフセット加工部をもつスリーブ軸
受面を有することを特徴とするハイブリッド軸受。1. A bearing for supporting a rotating shaft, a split bearing type load surface utilizing a dynamic pressure effect of an oil film accompanying rotation of the rotating shaft, and a force for forcibly eccentricizing the rotating shaft in a predetermined direction. A hybrid bearing having a sleeve bearing surface having an offset machined portion that causes the occurrence of the above.
転軸の回転に伴う油膜の動圧効果を利用する分割軸受形
の負荷面及び前記回転軸を定められた方向に強制的に偏
心させる力を生じさせる圧力ダムをもつ中央溝を形成し
たスリーブ軸受面を有することを特徴とするハイブリッ
ド軸受。2. A bearing for supporting a rotating shaft, a split bearing type load surface utilizing a dynamic pressure effect of an oil film accompanying rotation of the rotating shaft, and a force for forcibly eccentricizing the rotating shaft in a predetermined direction. A hybrid bearing having a sleeve bearing surface formed with a central groove having a pressure dam for generating a pressure.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP13692492A JP3233685B2 (en) | 1992-05-28 | 1992-05-28 | Hybrid bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP13692492A JP3233685B2 (en) | 1992-05-28 | 1992-05-28 | Hybrid bearing |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH05332359A JPH05332359A (en) | 1993-12-14 |
| JP3233685B2 true JP3233685B2 (en) | 2001-11-26 |
Family
ID=15186759
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP13692492A Expired - Fee Related JP3233685B2 (en) | 1992-05-28 | 1992-05-28 | Hybrid bearing |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3233685B2 (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6729763B2 (en) * | 2001-11-16 | 2004-05-04 | Kamatics Corporation | Hybrid bearing system |
| JP7075235B2 (en) | 2018-02-22 | 2022-05-25 | 株式会社日立インダストリアルプロダクツ | Tilting pad journal bearings and rotating machines using them |
| CN113864341A (en) * | 2021-09-24 | 2021-12-31 | 浙江翰翔科技有限公司 | Static and dynamic mixed air-bearing rotor system and operation method |
-
1992
- 1992-05-28 JP JP13692492A patent/JP3233685B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH05332359A (en) | 1993-12-14 |
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|---|---|---|---|
| A01 | Written decision to grant a patent or to grant a registration (utility model) |
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