JPH0716097Y2 - Bearing support structure for rotating machinery - Google Patents
Bearing support structure for rotating machineryInfo
- Publication number
- JPH0716097Y2 JPH0716097Y2 JP1991108409U JP10840991U JPH0716097Y2 JP H0716097 Y2 JPH0716097 Y2 JP H0716097Y2 JP 1991108409 U JP1991108409 U JP 1991108409U JP 10840991 U JP10840991 U JP 10840991U JP H0716097 Y2 JPH0716097 Y2 JP H0716097Y2
- Authority
- JP
- Japan
- Prior art keywords
- bearing
- elastic force
- ring
- force ring
- peripheral portion
- 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 - Lifetime
Links
Description
【０００１】[0001]
【産業上の利用分野】本考案はポンプや攪拌機などの回
転機械に用いられる回転軸等を回転自在に支持する回転
機械用軸受の支持構造に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a bearing structure for a rotary machine that rotatably supports a rotary shaft used in a rotary machine such as a pump or a stirrer.
【０００２】[0002]
【従来の技術】回転機械の回転軸を支持する軸受は耐摩
擦性及び耐摩耗性を向上させるために、近年では、素材
にセラミックス等の新素材を多く使用するようになって
きている。図１０に従来の軸受構造を表す断面、図１１
に図１０のＡ−Ａ断面を示す。2. Description of the Related Art In recent years, many new materials such as ceramics have been used as materials for the bearings that support the rotating shafts of rotating machines in order to improve their wear resistance and wear resistance. FIG. 10 is a cross section showing a conventional bearing structure, and FIG.
FIG. 10 shows a cross section taken along the line AA of FIG.
【０００３】図１０及び図１１に示すように、ポンプな
どの回転機械において、回転軸１０１は外周部にスリー
ブ１０２が装着され、このスリーブ１０２は外周部が所
定の隙間Ｓをあけてセラミックス性の軸受１０３によっ
て回転自在に支持されている。そして、軸受１０３は外
周部が衝撃緩衝作用を有する片当たり防止用のゴムリン
グ１０４を介してハウジング１０５によって支持されて
いる。更に、ハウジング１０５はケーシング１０６に取
付けられている。なお、回転軸１０１の下端部には図示
しない回転羽根が装着されている。As shown in FIGS. 10 and 11, in a rotary machine such as a pump, a sleeve 102 is mounted on an outer peripheral portion of a rotary shaft 101, and the outer peripheral portion of the sleeve 102 is made of a ceramic material with a predetermined gap S therebetween. It is rotatably supported by the bearing 103. The outer periphery of the bearing 103 is supported by the housing 105 via a rubber ring 104 having a shock absorbing function for preventing uneven contact. Further, the housing 105 is attached to the casing 106. A rotary blade (not shown) is attached to the lower end of the rotary shaft 101.
【０００４】而して、回転軸１０１が回転すると、軸受
１０３はこれを支持し、このとき、回転羽根によって水
などの流体Ｗの一部がスリーブ１０２と軸受１０３との
間の隙間Ｓに流入し、回転軸１０１の上部に設けられた
図示しない吐出口から排出される。従って、この流体に
よって軸受１０３の耐摩擦性及び耐摩耗性が維持され、
且つ、冷却作用効果も奏することができる。When the rotary shaft 101 rotates, the bearing 103 supports it, and at this time, a part of the fluid W such as water flows into the gap S between the sleeve 102 and the bearing 103 by the rotary vanes. Then, it is discharged from a discharge port (not shown) provided on the upper part of the rotating shaft 101. Therefore, this fluid maintains the friction resistance and wear resistance of the bearing 103,
In addition, the cooling effect can be achieved.
【０００５】[0005]
【考案が解決しようとする課題】上述した従来のセラミ
ックス性の軸受の支持構造にあっては、以下に示すよう
な問題がある。即ち、セラミックス性の軸受１０３は弾
性体であるゴムリング１０４によって外周部を巻かれる
ことで、取付時や製作時の誤差等で生じる偏心片当たり
によって軸受１０３に作用する片当たり力を緩和してい
る。The conventional ceramic bearing support structure described above has the following problems. That is, the ceramic bearing 103 has its outer peripheral portion wound by the rubber ring 104, which is an elastic body, so that the one-sided contact force acting on the bearing 103 due to the eccentric piece contact caused by an error during mounting or manufacturing can be alleviated. There is.
【０００６】ところが、ゴムリング１０４は全長にわた
って軸受１０３の荷重を支承するために必要な高い剛性
の均一な弾性力をもっている。そのため、取付時の僅か
な片当たり偏心が発生したときも、軸受１０３の上部及
び下部においては主にこの片当たり力を支承している。
しかし、このとき、ゴムリング１０４は取付時の僅かな
片当たり偏心によって軸受１０３に高い軸受面圧を作用
させてしまい、取付時の偏心片当たり力を十分に緩和す
ることができないという問題があった。However, the rubber ring 104 has a uniform elastic force of high rigidity necessary to support the load of the bearing 103 over the entire length. For this reason, even if a slight eccentricity is generated at the time of mounting, the urging force is mainly supported in the upper part and the lower part of the bearing 103.
However, at this time, there is a problem that the rubber ring 104 exerts a high bearing surface pressure on the bearing 103 due to a slight eccentricity of the eccentric piece contact at the time of mounting, and the eccentric piece contact force at the time of mounting cannot be sufficiently relaxed. It was
【０００７】本考案はこのような問題を解決するもので
あって、軸受の高面圧化を防止して支持の安定化を図っ
た回転機械用軸受の支持構造を提供することを目的とす
る。The present invention solves such a problem, and an object of the present invention is to provide a support structure for a bearing for a rotary machine, which prevents the bearing from having a high surface pressure and stabilizes the support. .
【０００８】[0008]
【課題を解決するための手段】上述の目的を達成するた
めの本考案の回転機械用軸受の支持構造は、回転軸を支
持する軸受の支持構造において、前記軸受の外周部を筒
状のハウジングの内周部に装着された複数の小弾性力リ
ングによって支持すると共に該ハウジングの外周部を複
数の大弾性力リングによって支持し、前記軸受とハウジ
ングとの間に前記小弾性力リングの弾性変位が前記軸受
の取付偏心量と同等となる隙間を設けたことを特徴とす
るものである。According to the present invention, there is provided a bearing support structure for a rotary machine, comprising: a bearing structure for supporting a rotating shaft; Is supported by a plurality of small elastic force rings mounted on the inner peripheral portion of the housing and the outer peripheral portion of the housing is supported by a plurality of large elastic force rings, and the elastic displacement of the small elastic force ring is provided between the bearing and the housing. Is provided with a gap equal to the mounting eccentricity of the bearing.
【０００９】また、本考案の回転機械用軸受の支持構造
は、回転軸を支持する軸受の支持構造において、前記軸
受の外周部を筒状のハウジングの内周部に装着された複
数の小弾性力リング及び該ハウジングの内周部に前記小
弾性力リングと並設された複数の大弾性力リングによっ
て支持し、前記小弾性力リングを前記軸受側に突設させ
ることで該小弾性力リングと前記大弾性力リングとに取
付内径差を設けたことを特徴とするものである。Also, the bearing support structure for a rotary machine of the present invention is the bearing support structure for supporting a rotating shaft, wherein a plurality of small elastic members in which an outer peripheral portion of the bearing is attached to an inner peripheral portion of a cylindrical housing are provided. Supported by a plurality of large elastic force rings arranged side by side with the small elastic force ring on the inner periphery of the force ring and the housing, and the small elastic force ring is projected on the bearing side.
Therefore, a mounting inner diameter difference is provided between the small elastic force ring and the large elastic force ring.
【００１０】[0010]
【作用】軸受をハウジング内周部の小弾性力リングによ
って支持すると共にハウジングを大弾性力リングによっ
て支持して軸受とハウジングとの間に隙間を設けるか、
あるいは軸受をハウジング内周部の小弾性力リングと取
付内径差を設けた大弾性力リングによって支持するよう
にしたことで、強制変位に伴う軸受取付時及び製作時の
静的偏心量は小弾性力リングによって吸収され、回転軸
駆動時の軸受の動的変動荷重・変位は大弾性力リングに
よって吸収される。The bearing is supported by the small elastic force ring on the inner peripheral portion of the housing and the housing is supported by the large elastic force ring to provide a gap between the bearing and the housing.
Alternatively, the bearing is supported by a small elastic force ring on the inner circumference of the housing and a large elastic force ring with a mounting inner diameter difference, so that the static eccentricity at the time of bearing mounting and manufacturing due to forced displacement is small elastic. The force ring absorbs the dynamic fluctuating load and displacement of the bearing when the rotary shaft is driven, and the large elastic force ring absorbs it.
【００１１】[0011]
【実施例】以下、本考案を実施例を図面に基づいて詳細
に説明する。Embodiments of the present invention will now be described in detail with reference to the drawings.
【００１２】図１に本考案の一実施例に係る回転機械用
軸受の支持構造を表す断面、図２に軸受取付時の平行偏
心変位状態を表す断面、図３に軸受取付時の傾斜偏心変
位状態を表す断面、図４に弾性リングによる偏心変位に
対する軸受面圧を表すグラフ、図５及び図６に変形例に
係る回転機械用軸受の支持構造を表す断面を示す。FIG. 1 is a sectional view showing a supporting structure of a bearing for a rotary machine according to an embodiment of the present invention, FIG. 2 is a sectional view showing a parallel eccentric displacement state when the bearing is mounted, and FIG. 3 is a tilted eccentric displacement when the bearing is mounted. A cross section showing a state, FIG. 4 is a graph showing bearing surface pressure with respect to eccentric displacement due to an elastic ring, and FIGS. 5 and 6 are cross sections showing a supporting structure of a rotary machine bearing according to a modification.
【００１３】図１に示すように、回転軸１１は外周部に
スリーブ１２が装着される一方、セラミックス性の軸受
１３はリテーナ１４の内周面に嵌装し、スリーブ１２の
外周部を回転自在に支持している。そして、リテーナ１
４は外周部が筒状のハウジング１５の内周部に上下に並
んで装着された複数の小弾性力リング１６によって支持
されている。更に、このハウジング１５の外周部は上下
に並んで装着された複数の大弾性力リング１７によって
支持され、この複数の大弾性力リング１７はケーシング
１８の内周部に支持されている。As shown in FIG. 1, a sleeve 12 is mounted on the outer peripheral portion of the rotary shaft 11, while a ceramic bearing 13 is fitted on the inner peripheral surface of the retainer 14 so that the outer peripheral portion of the sleeve 12 is rotatable. Support. And retainer 1
The outer peripheral portion 4 is supported by a plurality of small elastic force rings 16 mounted vertically on the inner peripheral portion of a cylindrical housing 15. Further, the outer peripheral portion of the housing 15 is supported by a plurality of large elastic force rings 17 mounted vertically side by side, and the plurality of large elastic force rings 17 are supported on an inner peripheral portion of a casing 18.
【００１４】大弾性力リング１７は小弾性力リング１６
に比べて高弾性力を有するゴム材で製造され、リテーナ
１４とハウジング１５との間には弾性変位の隙間δ
0 が、ハウジング１５とケーシング１８との間には弾性
変位の隙間δ1 がそれぞれ形成されている。そして、ば
ね定数の低い小弾性力リング１６の弾性変位の隙間δ0
は大弾性力リング１７の弾性変位の隙間δ1 よりも小さ
く設定され、その値は軸受１３の取付時の偏心量とほぼ
同等の値となっている。The large elastic force ring 17 is a small elastic force ring 16.
It is made of a rubber material having a higher elasticity than that of, and a gap δ of elastic displacement is provided between the retainer 14 and the housing 15.
0, a gap [delta] 1 of the elastic displacement are formed between the housing 15 and the casing 18. Then, the elastic displacement gap δ 0 of the small elastic force ring 16 having a low spring constant.
Is set to be smaller than the elastic displacement gap δ 1 of the large elastic force ring 17, and its value is almost the same as the eccentricity amount when the bearing 13 is mounted.
【００１５】また、小弾性力リング１６は大弾性力リン
グ１７よりも弾性力を小さく設定しており、この弾性力
Ｆは、リング線径をａ、ゴム硬度をＨS 、リング数をＮ
とすると、 Ｆ∝ａ1.2 ・ＨS 4.5 ・Ｎ で求めることができ、本実施例ではリング線径ａを変え
ることで小弾性力リング１６と大弾性力リング１７との
弾性力を相違させている。Further, the elastic force of the small elastic force ring 16 is set to be smaller than that of the large elastic force ring 17, and the elastic force F is such that the ring wire diameter is a, the rubber hardness is H S , and the number of rings is N.
Then, F ∝a 1.2 · H S 4.5 · N can be obtained. In this embodiment, the elastic force of the small elastic force ring 16 and the large elastic force ring 17 are made different by changing the ring wire diameter a. There is.
【００１６】而して、図２に示すように、軸受１３が取
付時に平行偏心変位たとき、その取付偏心量をδS をす
る。また、図３に示すように、軸受１３が取付時に角度
θ傾斜偏心変位したとき、その取付偏心量をδS をす
る。この場合、図４に示すように、従来の弾性力リング
のばね定数をＫとすると、軸受は高い弾性力のみによる
支持となり、取付初期よりこの軸受に高面圧が作用して
焼付の原因となってしまう。Then, as shown in FIG. 2, when the bearing 13 is displaced in parallel eccentricity during mounting, the mounting eccentricity amount is set to δ S. Further, as shown in FIG. 3, when the bearing 13 is displaced by an angle θ inclined eccentricity at the time of mounting, the mounting eccentricity amount is δ S. In this case, as shown in FIG. 4, assuming that the spring constant of the conventional elastic force ring is K, the bearing is supported only by a high elastic force, and a high surface pressure acts on this bearing from the initial stage of mounting to cause seizure. turn into.
【００１７】一方、小弾性力リング１６のばね定数をＫ
1 、大弾性力リング１７のばね定数をＫ2 とすると、こ
の小弾性力リング１６によって強制変位に伴う軸受１３
の取付時及び製作時の静的偏心量δS が吸収され、その
後、従来の弾性力リングのばね定数Ｋと同様のばね定数
を有する大弾性力リング１７によって回転軸駆動時の軸
受１３の動的変動荷重・変位が高剛性で支持、吸収され
る。従って、軸受としての性能を失わずに偏心による軸
受１３の高面圧化を防止できる。On the other hand, the spring constant of the small elastic force ring 16 is K
1 , and assuming that the spring constant of the large elastic force ring 17 is K 2 , the bearing 13 associated with the forced displacement by the small elastic force ring 16
The static eccentricity δ S during mounting and manufacturing is absorbed, and thereafter, the large elastic force ring 17 having a spring constant similar to the spring constant K of the conventional elastic ring causes the movement of the bearing 13 when the rotating shaft is driven. Highly rigid support and absorption of statically fluctuating loads and displacements. Therefore, it is possible to prevent the bearing 13 from increasing in surface pressure due to eccentricity without losing the performance as a bearing.
【００１８】なお、上述の実施例において、小弾性力リ
ング１６は大弾性力リング１７よりも弾性力が小さく設
定されており、リング線径ａを変えることで小弾性力リ
ング１６と大弾性力リング１７との弾性力を相違させて
いるが、これに限定されるものではない。即ち、図５に
示すように、小弾性力リング１６ａを２つ設けてリング
数Ｎを２とする一方、大弾性力リング１７ａを４つ設け
てリング数Ｎを４とすることで総合的な両者の弾性力を
相違させてもよい、また、図６に示すように、小弾性力
リング１６ｂの断面形状を円形とする一方、大弾性力リ
ング１７ｂの断面形状を四角形とし、この各弾性力リン
グの形状を変えることで両者の弾性力を相違させてい
る。In the above embodiment, the small elastic force ring 16 is set to have an elastic force smaller than that of the large elastic force ring 17, and the small elastic force ring 16 and the large elastic force are changed by changing the ring wire diameter a. Although the elastic force with respect to the ring 17 is different, the elastic force is not limited to this. That is, as shown in FIG. 5, two small elastic force rings 16a are provided to set the ring number N to two, while four large elastic force rings 17a are provided to set the ring number N to four. The elastic forces of the two may be different. Further, as shown in FIG. 6, the cross-sectional shape of the small elastic force ring 16b is circular while the cross-sectional shape of the large elastic force ring 17b is quadrangular. The elastic forces of the two are made different by changing the shape of the ring.
【００１９】図７に本考案の他の実施例に係る回転機械
用軸受の支持構造を表す断面、図８に軸受取付時の平行
偏心変位状態を表す断面、図９に弾性リングによる偏心
変位に対する軸受面圧を表すグラフを示す。なお、上述
の実施例と同様の機能を有する部材には同一の符号を付
して重複する説明は省略する。FIG. 7 is a cross section showing a support structure of a bearing for a rotary machine according to another embodiment of the present invention, FIG. 8 is a cross section showing a parallel eccentric displacement state when the bearing is mounted, and FIG. The graph which shows bearing surface pressure is shown. The members having the same functions as those in the above-described embodiment are designated by the same reference numerals, and the duplicated description will be omitted.
【００２０】図７に示すように、回転軸１１のスリーブ
１２を回転自在に支持する複数の小弾性力リング２１と
複数の大弾性力リング２２が回転軸１１の軸方向に交互
に並んで位置し、この状態で筒状のハウジング２３の内
周部に装着されている。そして、小弾性力リング２１と
大弾性力リング２２とは取付内径差が設けられている。
即ち、小弾性力リング２１の内周面はリテーナ１４に接
触しているが、大弾性力リング２２の内周面とリテーナ
１４との間には弾性変位の隙間δ3 が形成されている。As shown in FIG. 7, a plurality of small elastic force rings 21 and a plurality of large elastic force rings 22 that rotatably support the sleeve 12 of the rotating shaft 11 are arranged alternately in the axial direction of the rotating shaft 11. Then, in this state, it is mounted on the inner peripheral portion of the cylindrical housing 23. Further, there is a mounting inner diameter difference between the small elastic force ring 21 and the large elastic force ring 22.
That is, the inner peripheral surface of the small elastic force ring 21 is in contact with the retainer 14, but an elastic displacement gap δ 3 is formed between the inner peripheral surface of the large elastic force ring 22 and the retainer 14.
【００２１】而して、図８に示すように、軸受１３が取
付時に隙間δ3 だけ平行偏心変位すると、図９に示すよ
うに、従来の弾性力リングのばね定数Ｋとすると、軸受
は、前述したように、高い弾性力のみによる支持とな
り、取付初期よりこの軸受に高面圧が作用して焼付の原
因となる。As shown in FIG. 8, when the bearing 13 is displaced in parallel eccentricity by a gap δ 3 during mounting, the spring constant K of the conventional elastic force ring is taken as shown in FIG. As described above, the bearing is supported only by a high elastic force, and a high surface pressure acts on this bearing from the initial stage of mounting, which causes seizure.
【００２２】一方、小弾性力リング２１のばね定数をＫ
1 、大弾性力リング２２のばね定数をＫ2 とすると、こ
の小弾性力リング２１によって強制変位に伴う軸受１３
の取付時及び製作時の静的偏心量が吸収され、大弾性力
リング２２の内周面がリテーナ１４に接触したときに、
大弾性力リング２１によって回転軸駆動時の軸受１３の
動的変動荷重・変位が高剛性で支持、吸収される。On the other hand, the spring constant of the small elastic force ring 21 is K
1 and the spring constant of the large elastic force ring 22 is K 2 , the small elastic force ring 21 causes the bearing 13
When the static eccentricity at the time of mounting and manufacturing is absorbed and the inner peripheral surface of the large elastic force ring 22 comes into contact with the retainer 14,
The large elastic force ring 21 supports and absorbs the dynamic fluctuating load / displacement of the bearing 13 at the time of driving the rotating shaft with high rigidity.
【００２３】[0023]
【考案の効果】以上、実施例を挙げて詳細に説明したよ
うに本考案の回転機械用軸受の支持構造によれば、軸受
を筒状のハウジングの内周部に装着された複数の小弾性
力リングによって支持すると共にハウジングの外周部を
複数の大弾性力リングによって支持し、軸受とハウジン
グとの間に小弾性力リングの弾性変位が軸受の取付偏心
量と同等となる隙間を設けたので、強制変位に伴う軸受
取付時及び製作時の静的偏心量を小弾性力リングによっ
て吸収し、回転軸駆動時の軸受の動的変動荷重・変位を
大弾性力リングによって吸収することができる。As described above in detail with reference to the embodiments, according to the bearing supporting structure for a rotary machine of the present invention, the bearings are mounted on the inner peripheral portion of the cylindrical housing. Since the support is supported by the force ring and the outer peripheral portion of the housing is supported by the plurality of large elastic force rings, a gap is provided between the bearing and the housing so that the elastic displacement of the small elastic force ring is equal to the mounting eccentricity of the bearing. The small elastic force ring can absorb the amount of static eccentricity at the time of bearing mounting and manufacturing due to the forced displacement, and the large elastic force ring can absorb the dynamic fluctuating load / displacement of the bearing when the rotating shaft is driven.
【００２４】また、軸受を筒状のハウジングの内周部に
装着された複数の小弾性力リング及び小弾性力リングと
並設された複数の大弾性力リングによって支持し、小弾
性力リングを軸受側に突設させることでこの小弾性力リ
ングと大弾性力リングとに取付内径差を設けたので、前
述と同様に軸受の静的偏心量を小弾性力リングで、動的
変動荷重・変位を大弾性力リングによって吸収すること
ができる。その結果、軸受の高面圧化を防止してこの軸
受の支持の安定化を図ることができる。Moreover, supported by tubular plurality of small elastic force ring and small elastic force ring and juxtaposed plurality of large elastic force ring attached to an inner periphery of the housing bearing, small bullet
This small elastic force relief is provided by projecting the force ring on the bearing side.
Since the mounting inner diameter difference is provided between the ring and the large elastic force ring, the static eccentricity of the bearing can be absorbed by the small elastic force ring, and the dynamic fluctuating load / displacement can be absorbed by the large elastic force ring, as described above. . As a result, it is possible to prevent the bearing from having a high surface pressure and stabilize the support of the bearing.
【図１】本考案の一実施例に係る回転機械用軸受の支持
構造を表す断面図である。FIG. 1 is a cross-sectional view showing a support structure of a bearing for a rotary machine according to an embodiment of the present invention.
【図２】軸受取付時の平行偏心変位状態を表す断面図で
ある。FIG. 2 is a cross-sectional view showing a parallel eccentric displacement state when a bearing is attached.
【図３】軸受取付時の傾斜偏心変位状態を表す断面図で
ある。FIG. 3 is a sectional view showing a tilted eccentric displacement state when a bearing is attached.
【図４】弾性リングによる偏心変位に対する軸受面圧を
表す関係図である。FIG. 4 is a relationship diagram showing bearing surface pressure with respect to eccentric displacement due to an elastic ring.
【図５】本考案の一実施例の変形例に係る回転機械用軸
受の支持構造を表す断面図である。FIG. 5 is a cross-sectional view showing a support structure of a bearing for a rotary machine according to a modified example of the embodiment of the present invention.
【図６】本考案の一実施例の変形例に係る回転機械用軸
受の支持構造を表す断面図である。FIG. 6 is a cross-sectional view showing a supporting structure of a bearing for a rotary machine according to a modified example of the embodiment of the present invention.
【図７】本考案の他の実施例に係る回転機械用軸受の支
持構造を表す断面図である。FIG. 7 is a cross-sectional view showing a support structure for a rotary machine bearing according to another embodiment of the present invention.
【図８】軸受取付時の変位状態を表す断面図である。FIG. 8 is a cross-sectional view showing a displacement state when the bearing is attached.
【図９】弾性リングによる偏心変位に対する軸受面圧を
表す関係図である。FIG. 9 is a relationship diagram showing bearing surface pressure with respect to eccentric displacement due to an elastic ring.
【図１０】従来の回転機械用軸受の支持構造を表す断面
図である。FIG. 10 is a cross-sectional view showing a conventional bearing support structure for a rotary machine.
【図１１】図１０のＡ−Ａ断面図である。11 is a cross-sectional view taken along the line AA of FIG.
【符号の説明】 １１ 回転軸 １３ 軸受 １４ リテーナ １５ ハウジング １６，２１ 小弾性力リング １７，２２ 大弾性力リング １８ ケーシング[Explanation of reference numerals] 11 rotating shaft 13 bearing 14 retainer 15 housing 16,21 small elastic force ring 17,22 large elastic force ring 18 casing
───────────────────────────────────────────────────── フロントページの続き (56)参考文献 実開 昭63−75627（ＪＰ，Ｕ) 実開 昭61−139314（ＪＰ，Ｕ) ─────────────────────────────────────────────────── ─── Continuation of the front page (56) Bibliography Sho 63-75627 (JP, U) Sho 61-139314 (JP, U)
Claims (2)
て、前記軸受の外周部を筒状のハウジングの内周部に装
着された複数の小弾性力リングによって支持すると共に
該ハウジングの外周部を複数の大弾性力リングによって
支持し、前記軸受とハウジングとの間に前記小弾性力リ
ングの弾性変位が前記軸受の取付偏心量と同等となる隙
間を設けたことを特徴とする回転機械用軸受の支持構
造。1. A support structure for a bearing supporting a rotating shaft, wherein the outer peripheral portion of the bearing is supported by a plurality of small elastic force rings mounted on the inner peripheral portion of a cylindrical housing, and the outer peripheral portion of the housing is supported. A bearing for a rotary machine, wherein the bearing is supported by a plurality of large elastic force rings, and a gap is provided between the bearing and the housing such that the elastic displacement of the small elastic force ring is equal to the mounting eccentric amount of the bearing. Support structure.
て、前記軸受の外周部を筒状のハウジングの内周部に装
着された複数の小弾性力リング及び該ハウジングの内周
部に前記小弾性力リングと並設された複数の大弾性力リ
ングによって支持し、前記小弾性力リングを前記軸受側
に突設させることで該小弾性力リングと前記大弾性力リ
ングとに取付内径差を設けたことを特徴とする回転機械
用軸受の支持構造。2. A support structure for a bearing that supports a rotating shaft, wherein a plurality of small elastic force rings are mounted on an inner peripheral portion of a cylindrical housing and an outer peripheral portion of the bearing is formed on the inner peripheral portion of the housing. It is supported by a plurality of large elastic force rings arranged in parallel with the elastic force ring, and the small elastic force ring is attached to the bearing side.
A support structure for a bearing for a rotary machine, characterized in that a mounting inner diameter difference is provided between the small elastic force ring and the large elastic force ring by being protruded .
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1991108409U JPH0716097Y2 (en) | 1991-12-05 | 1991-12-05 | Bearing support structure for rotating machinery |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1991108409U JPH0716097Y2 (en) | 1991-12-05 | 1991-12-05 | Bearing support structure for rotating machinery |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0550149U JPH0550149U (en) | 1993-07-02 |
| JPH0716097Y2 true JPH0716097Y2 (en) | 1995-04-12 |
Family
ID=14484027
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1991108409U Expired - Lifetime JPH0716097Y2 (en) | 1991-12-05 | 1991-12-05 | Bearing support structure for rotating machinery |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0716097Y2 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5496239B2 (en) * | 2012-03-30 | 2014-05-21 | 株式会社クボタ | Sliding bearing device and pump device |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS61139314U (en) * | 1985-02-18 | 1986-08-29 | ||
| JPS6375627U (en) * | 1986-11-07 | 1988-05-20 |
-
1991
- 1991-12-05 JP JP1991108409U patent/JPH0716097Y2/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0550149U (en) | 1993-07-02 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| EXPY | Cancellation because of completion of term |