JPH0138335Y2 - - Google Patents
Info
- Publication number
- JPH0138335Y2 JPH0138335Y2 JP1983080236U JP8023683U JPH0138335Y2 JP H0138335 Y2 JPH0138335 Y2 JP H0138335Y2 JP 1983080236 U JP1983080236 U JP 1983080236U JP 8023683 U JP8023683 U JP 8023683U JP H0138335 Y2 JPH0138335 Y2 JP H0138335Y2
- Authority
- JP
- Japan
- Prior art keywords
- receiving member
- pressure
- pressure receiving
- thrust force
- 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.)
- Expired
Links
Landscapes
- Sliding-Contact Bearings (AREA)
- Support Of The Bearing (AREA)
Description
【考案の詳細な説明】
第１図は回転機械に一般に用いられているスラ
スト軸受の断面図である。この軸受はロータ０１
に設けられたスラストカラー０２を両側より挟む
受圧部材０３，０５と、それを支持するケーシン
グ０６より構成され、潤滑剤は図示されていない
給油口よりケーシング内に供給され、受圧部材０
３，０５を潤滑した後、排油口０７より外部に放
出される。[Detailed Description of the Invention] Fig. 1 is a sectional view of a thrust bearing commonly used in rotating machines. This bearing is rotor 01
It is composed of pressure receiving members 03 and 05 that sandwich a thrust collar 02 provided on both sides, and a casing 06 that supports them. Lubricant is supplied into the casing from an oil supply port (not shown), and the pressure receiving member 0
After lubricating oil 3 and 05, it is discharged to the outside from the oil drain port 07.
今、仮にロータ０１に矢印の方向にスラスト力
Ｆが作用したとすると、それに見合つた油膜圧力
を発生させるべく、ロータ０１はスラスト力が掛
つた方向と同方向に移動し、受圧部材０３との間
に狭い隙間ｈを形成する。スラスト力Ｆと隙間ｈ
との関係は第２図のように表わされ、スラスト力
が大きいとこの隙間は極端に狭くなり、更に狭く
なつて受圧部材０３とスラストカラー０２とが直
接接触するようなことになれば、致命的な損傷事
故に至る虞れがある。 Now, if a thrust force F is applied to the rotor 01 in the direction of the arrow, the rotor 01 moves in the same direction as the direction in which the thrust force is applied to generate an oil film pressure commensurate with the thrust force, and the rotor 01 moves in the same direction as the thrust force applied, and the rotor 01 moves in the same direction as the direction in which the thrust force is applied. A narrow gap h is formed between them. Thrust force F and clearance h
The relationship with There is a risk of fatal accident.
そのため、スラスト力が大きい場合には受圧部
材０３を大きくする必要があり、外径を大きくせ
ざるを得ない。外径が大きくなれば周速度が高く
なり、摩擦損失の増大と高い温度上昇を招く。 Therefore, when the thrust force is large, it is necessary to increase the size of the pressure receiving member 03, and the outer diameter must be increased. As the outer diameter increases, the circumferential speed increases, leading to increased friction loss and high temperature rise.
したがつてスラスト力の大きい場合を重視する
ことにより、スラスト力が小さい時でも大きな受
圧部材０３を有していることはそれだけ摩擦損失
と温度上昇が大きく、前者は回転機械の効率を下
げ、後者は受圧部材の強度や潤滑油の劣化といつ
た点で好ましくなかつた。 Therefore, by focusing on cases where the thrust force is large, having a large pressure receiving member 03 even when the thrust force is small will result in greater friction loss and temperature rise, and the former will reduce the efficiency of the rotating machine, while the latter will This was not desirable in terms of deterioration of the strength of the pressure-receiving member and the lubricating oil.
そこで本考案はこの欠点を改善すべく、受圧部
材を適当な直径上で内外２つに分け、スラスト力
が小さい時は一方の受圧部材だけで負荷を担い、
スラスト力が大きくなると他方の受圧部材も加担
するようなスラスト軸受を得ることを目的とする
ものである。 Therefore, in order to improve this drawback, the present invention divides the pressure-receiving member into two parts, an inner and an outer part, on an appropriate diameter, and when the thrust force is small, only one pressure-receiving member carries the load.
The object of the present invention is to obtain a thrust bearing in which when the thrust force becomes large, the other pressure receiving member also takes part in the thrust force.
本考案はこの目的を達成するために提案された
もので、回転軸に取付けられたスラストカラーに
対峙し、スラスト力を受ける受圧部材をケーシン
グに取付けてなるスラスト軸受において、前記受
圧部材を環状に２分割し、同分割された受圧部材
のいずれか一方の背面を弾性部材を介してケーシ
ングに取付けてなることを特徴とするスラスト軸
受を提供せんとするものである。 The present invention was proposed to achieve this objective, and includes a thrust bearing in which a pressure receiving member is attached to a casing that faces a thrust collar attached to a rotating shaft and receives thrust force, and the pressure receiving member is arranged in an annular shape. It is an object of the present invention to provide a thrust bearing characterized in that the pressure receiving member is divided into two parts, and the back surface of one of the divided pressure receiving members is attached to a casing via an elastic member.
以下本考案の実施例を図面について説明する
と、第３図及び第４図は本考案の実施例を示し、
第３図はスラスト力が小さい場合、第４図はスラ
スト力が大きい場合の作動状態を示している。 Embodiments of the present invention will be described below with reference to the drawings. FIGS. 3 and 4 show embodiments of the present invention,
FIG. 3 shows the operating state when the thrust force is small, and FIG. 4 shows the operating state when the thrust force is large.
第３図及び第４図では軸受の構成及び潤滑法は
第１図にほぼ準ずるが、スラスト力Ｆが掛る方向
の受圧面は適当な直径上で、外側受圧部材３と内
側受圧部材４とに分けられる。外側受圧部材３は
従来どおりケーシング６に直接支持されるが、内
側受圧部材４はケーシング６との間に弾性体８を
介して支持され、内側受圧部材４と対向するケー
シング側面には凸状のストツパ９が設けられてい
る。 In FIGS. 3 and 4, the structure of the bearing and the lubrication method are almost the same as in FIG. Can be divided. The outer pressure receiving member 3 is directly supported by the casing 6 as before, but the inner pressure receiving member 4 is supported with an elastic body 8 interposed between it and the casing 6, and the side surface of the casing facing the inner pressure receiving member 4 has a convex shape. A stopper 9 is provided.
さてスラスト力Ｆが小さい場合は、弾性体８に
より内側受圧部材４は外側受圧部材３よりもロー
タ１のスラストカラー２に近い位置にあり、（即
ち、隙間h1＜隙間h2）、スラスト力Ｆは内側受圧
部材４だけで受け持ち、且つ摩擦損失も内側受圧
部材４だけによるものであり小さい。スラスト力
が大きくなるにつれ、内側受圧部材４を支える弾
性体８は縮み、隙間h2と隙間h1との差が小さくな
るにつれ、外側受圧部材３も負荷を分担するよう
になる。 Now, when the thrust force F is small, the inner pressure receiving member 4 is located closer to the thrust collar 2 of the rotor 1 than the outer pressure receiving member 3 due to the elastic body 8, (i.e., gap h 1 < gap h 2 ), and the thrust force F is borne only by the inner pressure receiving member 4, and the friction loss is also caused only by the inner pressure receiving member 4 and is small. As the thrust force increases, the elastic body 8 supporting the inner pressure receiving member 4 contracts, and as the difference between the gap h 2 and the gap h 1 becomes smaller, the outer pressure receiving member 3 also begins to share the load.
そして最後は内側受圧部材４のケーシング６と
対向する面がストツパ９に接触し、内側受圧部材
４と外側受圧部材３のスラストカラー２と対向す
る面が同じ平面上になり（即ち、隙間h1＝隙間
h2）、両受圧部材でもつて大きなスラスト力Ｆを
担うようになる。 Finally, the surface of the inner pressure-receiving member 4 facing the casing 6 contacts the stopper 9, and the surfaces of the inner pressure-receiving member 4 and the outer pressure-receiving member 3 facing the thrust collar 2 are on the same plane (that is, the gap h 1 = gap
h 2 ), both pressure-receiving members bear a large thrust force F.
このようにスラスト力の大きさによつて受圧部
材の大きさを変えることにより、スラスト力の小
さい時には小さな受圧部材で作動することが可能
となり、不必要な摩擦損失の発生と、それによる
温度上昇を防ぐことが出来る。なお、以上説明し
た実施例では、受圧部材４は半径方向内側に設け
た場合を示したが、これは半径方向外側に設けた
場合でも、本考案の目的を達成することができ
る。 By changing the size of the pressure-receiving member depending on the magnitude of the thrust force in this way, it is possible to operate with a smaller pressure-receiving member when the thrust force is small, resulting in unnecessary friction loss and resulting temperature rise. can be prevented. In the embodiment described above, the pressure receiving member 4 is provided on the radially inner side, but the object of the present invention can be achieved even when the pressure receiving member 4 is provided on the radially outer side.
以上詳細に説明した如く本考案は、受圧部材を
環状に２分割し、その分割された受圧部材のいず
れか一方の背面を弾性部材を介してケーシングに
取付けるようにしたので、スラスト力が小さい場
合には小さな受圧部材で受け持ち、その結果軸受
油膜部で発生する摩擦損失を小さくすることがで
きる。摩擦損失ＨはD4／ｈ（Ｄ：軸受直径、ｈ：
油膜厚さ）に比例するため、軸受直径が大きくな
ると、摩擦損失が飛躍的に大きくなるものであ
る。 As explained in detail above, in the present invention, the pressure receiving member is divided into two in an annular shape, and the back surface of one of the divided pressure receiving members is attached to the casing via an elastic member, so that when the thrust force is small, This is handled by a small pressure-receiving member, and as a result, the friction loss generated in the bearing oil film can be reduced. Friction loss H is D 4 /h (D: bearing diameter, h:
Friction loss increases dramatically as the bearing diameter increases.
また本考案は受圧部材を環状に２分割、即ち径
方向に２例配置となつているので、軸方向スペー
スは通常の軸受並に小さくてよい。一般に本考案
のようなスラスト軸受（受圧部材）を有する回転
機械にとつて、軸方向スペースが大きくなること
は、軸振動上好ましくなく、かつ機械全長が長く
なる欠点がある。この点本考案の場合は、軸方向
スペースが小さいため、軸振動上で何らの問題も
なく、機械全長が長くなる等の欠点もない。 Further, in the present invention, the pressure receiving member is annularly divided into two parts, that is, arranged in two cases in the radial direction, so that the axial space may be smaller than that of a normal bearing. In general, for a rotating machine having a thrust bearing (pressure receiving member) such as the present invention, an increase in the axial space is unfavorable in terms of shaft vibration, and has the drawback of increasing the overall length of the machine. In this regard, in the case of the present invention, since the space in the axial direction is small, there is no problem with shaft vibration, and there are no drawbacks such as an increase in the overall length of the machine.
第１図は従来のスラスト軸受の１例を示す側断
面図、第２図は第１図の軸受におけるスラスト力
Ｆと隙間ｈとの関係を示す線図、第３図及び第４
図は本考案の実施例を示すスラスト軸受の夫々作
動状態を異にする側断面図である。
図の主要部分の説明、１……ロータ、２……ス
ラストカラー、３……外側受圧部材、４……内側
受圧部材、６……ケーシング、８……弾性体。
Fig. 1 is a side sectional view showing an example of a conventional thrust bearing, Fig. 2 is a diagram showing the relationship between thrust force F and clearance h in the bearing shown in Fig. 1, and Figs.
The figures are side sectional views of thrust bearings in different operating states according to embodiments of the present invention. Explanation of the main parts of the figure, 1... Rotor, 2... Thrust collar, 3... Outer pressure receiving member, 4... Inner pressure receiving member, 6... Casing, 8... Elastic body.
Claims (1)
し、スラスト力を受ける受圧部材をケーシングに
取付けてなるスラスト軸受において、前記受圧部
材を環状に２分割し、同分割された受圧部材のい
ずれか一方の背面を弾性部材を介してケーシング
に取付けてなることを特徴とするスラスト軸受。 In a thrust bearing in which a pressure-receiving member is attached to a casing and faces a thrust collar attached to a rotating shaft and receives thrust force, the pressure-receiving member is divided into two parts in an annular shape, and the back surface of one of the divided pressure-receiving members is A thrust bearing characterized in that it is attached to a casing via an elastic member.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8023683U JPS59185413U (en) | 1983-05-30 | 1983-05-30 | thrust bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8023683U JPS59185413U (en) | 1983-05-30 | 1983-05-30 | thrust bearing |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS59185413U JPS59185413U (en) | 1984-12-10 |
| JPH0138335Y2 true JPH0138335Y2 (en) | 1989-11-16 |
Family
ID=30210228
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP8023683U Granted JPS59185413U (en) | 1983-05-30 | 1983-05-30 | thrust bearing |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS59185413U (en) |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2481361A1 (en) * | 1980-04-24 | 1981-10-30 | Neyrpic | PROPELLER WHEEL WITH ORIENTABLE BLADES FOR TURBINES |
| JPS6030491Y2 (en) * | 1980-12-17 | 1985-09-12 | 株式会社小松製作所 | Thrust bearing device |
-
1983
- 1983-05-30 JP JP8023683U patent/JPS59185413U/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS59185413U (en) | 1984-12-10 |
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