JPH05125951A - Exhaust gas turbine supercharger - Google Patents
Exhaust gas turbine superchargerInfo
- Publication number
- JPH05125951A JPH05125951A JP3284919A JP28491991A JPH05125951A JP H05125951 A JPH05125951 A JP H05125951A JP 3284919 A JP3284919 A JP 3284919A JP 28491991 A JP28491991 A JP 28491991A JP H05125951 A JPH05125951 A JP H05125951A
- Authority
- JP
- Japan
- Prior art keywords
- turbine
- bearing
- shaft
- compressor
- exhaust gas
- 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.)
- Pending
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C21/00—Combinations of sliding-contact bearings with ball or roller bearings, for exclusively rotary movement
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/12—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load
- F16C17/18—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load with floating brasses or brushing, rotatable at a reduced speed
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
- F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
- F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2360/00—Engines or pumps
- F16C2360/23—Gas turbine engines
- F16C2360/24—Turbochargers
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Supercharger (AREA)
Abstract
Description
【0001】[0001]
【産業上の利用分野】本発明は、排気ガスタービン過給
機に関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an exhaust gas turbine supercharger.
【0002】[0002]
【従来の技術】排気ガスタービン過給機(ターボチャー
ジャ)は、内燃機関から出る排ガスエネルギを利用して
過給する装置としてよく知られている。その構成は、タ
ービンのホイール(翼車)とコンプレッサのインペラと
が共通の回転軸により連結されて成り、排ガスをホイー
ルに当てることで同軸上のコンプレッサを回転させて空
気を圧縮し、これを内燃機関の燃焼室に供給するように
なっている。そしてこの回転体は、回転軸に適宜配設さ
れた軸受を介して所定形状の軸受ハウジングに支持され
ている。2. Description of the Related Art An exhaust gas turbine supercharger (turbocharger) is well known as a device for supercharging exhaust gas energy emitted from an internal combustion engine. The structure consists of a turbine wheel (impeller) and a compressor impeller connected by a common rotating shaft. By applying exhaust gas to the wheel, the coaxial compressor is rotated to compress air, which is then transferred to the internal combustion engine. It is designed to be supplied to the combustion chamber of the engine. The rotating body is supported by a bearing housing having a predetermined shape via a bearing that is appropriately arranged on the rotating shaft.
【0003】[0003]
【発明が解決しようとする課題】ところでその軸受とし
ては、転がり軸受或いはすべり軸受(浮動ブッシュ軸受
など)が使用されている。転がり軸受は、低摩擦である
ためにメカニカルロスが小さく、また給油量が少なくて
済むので、排気ガスタービン過給機の軸受として最も望
ましい。しかしながら転がり軸受は一般に寿命が短く、
特に排ガスによりタービンが高温となるために、材料に
良質なものを使用してもその耐久性には限界があった。
このため従来トラックなどにおいては、耐久性のあるす
べり軸受を採用しており、メカニカルロス及び給油量の
点は妥協せざるを得なかった。By the way, a rolling bearing or a sliding bearing (floating bush bearing, etc.) is used as the bearing. Rolling bearings are the most desirable as bearings for exhaust gas turbine superchargers, because they have low friction and therefore have a small mechanical loss and require a small amount of oil supply. However, rolling bearings generally have a short life,
In particular, since the temperature of the turbine becomes high due to exhaust gas, even if a high quality material is used, its durability is limited.
For this reason, in conventional trucks and the like, durable sliding bearings have been adopted, and there has been no choice but to compromise in terms of mechanical loss and refueling amount.
【0004】そこで本発明は、上記事情に鑑み、耐久性
があり、しかもメカニカルロス及び給油量を少なくでき
る排気ガスタービン過給機を提供すべく創案されたもの
である。Therefore, in view of the above circumstances, the present invention was devised to provide an exhaust gas turbine supercharger which is durable and can reduce mechanical loss and oil supply.
【0005】[0005]
【課題を解決するための手段】本発明は、コンプレッサ
とタービンとを連結する回転軸のコンプレッサ側に転が
り軸受を、タービン側にすべり軸受を配設したものであ
る。According to the present invention, a rolling bearing is arranged on the compressor side of a rotary shaft connecting a compressor and a turbine, and a sliding bearing is arranged on the turbine side.
【0006】また上記回転軸は、転がり軸受の位置の軸
径をすべり軸受の位置の軸径よりも小さく形成されるこ
とが望ましい。Further, it is desirable that the rotary shaft is formed so that the shaft diameter at the position of the rolling bearing is smaller than the shaft diameter at the position of the sliding bearing.
【0007】[0007]
【作用】上記構成によって、転がり軸受は比較的低温な
コンプレッサ側で、すべり軸受は高温なタービン側でそ
れぞれ回転軸を軸支する。With the above construction, the rolling bearing supports the rotary shaft on the compressor side, which has a relatively low temperature, and the sliding bearing supports the turbine shaft, which has a high temperature.
【0008】また回転軸が異なる軸径で形成された構成
によって、転がり軸受の負担が軽減される。Further, since the rotary shafts are formed with different shaft diameters, the load on the rolling bearing is reduced.
【0009】[0009]
【実施例】以下、本発明の実施例を添付図面に従って説
明する。Embodiments of the present invention will be described below with reference to the accompanying drawings.
【0010】図1は、本発明に係わる排気ガスタービン
過給機の一実施例を示したものである。この排気ガスタ
ービン過給機は、コンプレッサ1のインペラ2とタービ
ン3のホイール4とを連結する回転軸たるタービン軸5
に、そのコンプレッサ側に転がり軸受たるボールベアリ
ング6が、タービン側にすべり軸受たるフローティング
メタル(浮動ブッシュ軸受)7が配設されて構成されて
いる。FIG. 1 shows an embodiment of an exhaust gas turbine supercharger according to the present invention. This exhaust gas turbine supercharger includes a turbine shaft 5 that is a rotating shaft that connects an impeller 2 of a compressor 1 and a wheel 4 of a turbine 3.
The ball bearing 6 serving as a rolling bearing is disposed on the compressor side, and the floating metal (floating bush bearing) 7 serving as a sliding bearing is disposed on the turbine side.
【0011】タービン軸5はタービンホイール4の軸心
に一体的に延出され、他端がコンプレッサ1のインペラ
2の軸心を貫通してその先端部でナット8により締結さ
れている。そしてボールベアリング6の位置よりもコン
プレッサ側のタービン軸5が縮径され、その段部9にボ
ールベアリング6の内輪10が嵌合されている。すなわ
ち、ボールベアリング6の位置の軸径aが、フローティ
ングメタル7の位置の軸径bよりも小さくなるように形
成されている。なおこのボールベアリング6の内輪10
とタービン軸5とはスキマ嵌めとして、トルクを軸方向
の締付力で保持するようになっている。なお高負荷時の
回転領域などにおいて生ずるスラスト力は、ボールベア
リング6により受けることになる。The turbine shaft 5 extends integrally with the shaft center of the turbine wheel 4, and the other end penetrates the shaft center of the impeller 2 of the compressor 1 and is fastened by a nut 8 at its tip. The diameter of the turbine shaft 5 closer to the compressor than the position of the ball bearing 6 is reduced, and the inner ring 10 of the ball bearing 6 is fitted to the step portion 9 thereof. That is, the shaft diameter a at the position of the ball bearing 6 is formed to be smaller than the shaft diameter b at the position of the floating metal 7. The inner ring 10 of this ball bearing 6
The turbine shaft 5 and the turbine shaft 5 are loosely fitted to each other so that the torque is held by the tightening force in the axial direction. The ball bearing 6 receives the thrust force generated in the rotating region under high load.
【0012】そしてボールベアリング6及びフローティ
ングメタル7と軸受ハウジング11との間には共通のブ
ッシュ(スリーブ)12が設けられており、これら軸受
(6,7)を所定位置に保持するようになっている。ま
たブッシュ12とボールベアリング6とは焼嵌め又は圧
入で嵌合されていると共に、この位置でのブッシュ12
の内径は拡大されてボールベアリング6の外輪13が取
り付けられ、軸方向の位置出しが容易にできるように形
成されている。A common bush (sleeve) 12 is provided between the ball bearing 6 and the floating metal 7 and the bearing housing 11, and these bearings (6, 7) are held at predetermined positions. There is. Further, the bush 12 and the ball bearing 6 are fitted by shrink fitting or press fitting, and the bush 12 at this position
The inner diameter of is expanded and the outer ring 13 of the ball bearing 6 is attached to the inner surface of the inner surface of the outer ring so that the axial positioning can be easily performed.
【0013】また軸受ハウジング11内には給油路14
が形成され、ブッシュ12に形成された油孔15を介し
てフローティングメタル7に給油できるようになってい
る。そしてボールベアリング6には給油路14が配設さ
れておらず、フローティングメタル7側の油雰囲気によ
り給油(ミスト給油)が行われるようになっている。In the bearing housing 11, an oil supply passage 14 is provided.
Is formed, and oil can be supplied to the floating metal 7 through the oil hole 15 formed in the bush 12. The ball bearing 6 is not provided with the oil supply passage 14, and oil is supplied (mist oil supply) by the oil atmosphere on the floating metal 7 side.
【0014】このほか、ボールベアリング6とコンプレ
ッサ1との間には、油切りのためのリング16が設けら
れている。In addition, a ring 16 for removing oil is provided between the ball bearing 6 and the compressor 1.
【0015】このように構成したことで、フローティン
グメタル7が高温なタービン側においてタービン軸5を
軸支し、ボールベアリング6が比較的低温なコンプレッ
サ側で軸支することとなり、それぞれの軸受の利点が適
切に発揮されて、耐久性があり、しかもメカニカルロス
及び給油量を少なくできる排気ガスタービン過給機が得
られる。With this structure, the floating metal 7 pivotally supports the turbine shaft 5 on the high temperature side of the turbine, and the ball bearing 6 pivotally supports on the compressor side of relatively low temperature, which is an advantage of each bearing. It is possible to obtain an exhaust gas turbine supercharger that is properly exhibited, has durability, and can reduce mechanical loss and oil supply amount.
【0016】そしてボールベアリング6の位置のタービ
ン軸5を縮径したことで、軸受の寿命を決定する要素を
低減(DN 値を低下)させることができ、その耐久性を
確保することができる。By reducing the diameter of the turbine shaft 5 at the position of the ball bearing 6, it is possible to reduce the factors that determine the life of the bearing (reduce the D N value) and ensure its durability. .
【0017】またボールベアリング6への給油をミスト
給油としたことで、給油機構のコストダウンに寄与でき
る。さらにボールベアリング6がブッシュ12とは焼嵌
め又は圧入で嵌合され、タービン軸5とはスキマ嵌めで
嵌合させるので、ボールベアリング6をカセット状に取
り扱うことができ、部品組立て性を向上させることがで
きる。Further, since the ball bearing 6 is supplied with mist, the cost of the oil supply mechanism can be reduced. Further, since the ball bearing 6 is fitted with the bush 12 by shrink fitting or press fitting, and is fitted with the turbine shaft 5 by clearance fitting, the ball bearing 6 can be handled like a cassette and the assemblability of parts is improved. You can
【0018】なお本実施例にあっては、すべり軸受を回
転自在なフローティングメタルとしたが、ピンなどによ
って回転が拘束される半浮動ブッシュ軸受を構成しても
よい。またブッシュ12と軸受ハウジング11との間に
所定の間隙Sを形成し、油膜によりダンパの機能が付加
されるようにしてもよい。さらに転がり軸受として、ボ
ールベアリングを軸方向に二重に並設するようにしても
よい。又ブッシュ12と軸受ハウジング11との間を全
て、間隙を持たせ、軸方向位置決めをブッシュ12に段
付きを設けるなどして行ってもよい。In this embodiment, the sliding bearing is a rotatable floating metal, but it may be a semi-floating bush bearing whose rotation is restricted by a pin or the like. Further, a predetermined gap S may be formed between the bush 12 and the bearing housing 11 so that the function of the damper is added by the oil film. Further, as rolling bearings, ball bearings may be doubly arranged side by side in the axial direction. Alternatively, a gap may be provided between the bush 12 and the bearing housing 11, and axial positioning may be performed by providing a step on the bush 12.
【0019】[0019]
【発明の効果】以上要するに本発明によれば、次のよう
な優れた効果を発揮する。In summary, according to the present invention, the following excellent effects are exhibited.
【0020】(1) 請求項1記載の構成によれば、所望の
耐久性が得られ、しかもメカニカルロス及び給油量を少
なくできる。(1) According to the configuration of claim 1, desired durability can be obtained, and further, mechanical loss and oil supply amount can be reduced.
【0021】(2) 請求項2記載の構成によれば、さらに
転がり軸受の耐久性向上が達成される。(2) According to the configuration of claim 2, the durability of the rolling bearing is further improved.
【図1】本発明に係わる排気ガスタービン過給機の一実
施例を示した側断面図である。FIG. 1 is a side sectional view showing an embodiment of an exhaust gas turbine supercharger according to the present invention.
1 コンプレッサ 3 タービン 5 タービン軸(回転軸) 6 ボールベアリング(転がり軸受) 7 フローティングメタル(すべり軸受) 1 Compressor 3 Turbine 5 Turbine shaft (rotary shaft) 6 Ball bearing (rolling bearing) 7 Floating metal (sliding bearing)
Claims (2)
転軸の上記コンプレッサ側に転がり軸受を、上記タービ
ン側にすべり軸受を配設したことを特徴とする排気ガス
タービン過給機。1. An exhaust gas turbine supercharger characterized in that a rolling bearing is arranged on the compressor side of a rotary shaft connecting a compressor and a turbine, and a slide bearing is arranged on the turbine side.
軸径を上記すべり軸受の位置の軸径よりも小さく形成さ
れた請求項1記載の排気ガスタービン過給機。2. The exhaust gas turbine supercharger according to claim 1, wherein the rotary shaft is formed such that a shaft diameter at a position of the rolling bearing is smaller than a shaft diameter at a position of the sliding bearing.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP3284919A JPH05125951A (en) | 1991-10-30 | 1991-10-30 | Exhaust gas turbine supercharger |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP3284919A JPH05125951A (en) | 1991-10-30 | 1991-10-30 | Exhaust gas turbine supercharger |
Publications (1)
Publication Number | Publication Date |
---|---|
JPH05125951A true JPH05125951A (en) | 1993-05-21 |
Family
ID=17684760
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP3284919A Pending JPH05125951A (en) | 1991-10-30 | 1991-10-30 | Exhaust gas turbine supercharger |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPH05125951A (en) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2011143079A2 (en) * | 2010-05-14 | 2011-11-17 | Borgwarner Inc. | Exhaust-gas turbocharger |
JP2013245663A (en) * | 2012-05-29 | 2013-12-09 | Ihi Corp | Supercharger |
WO2017199695A1 (en) * | 2016-05-20 | 2017-11-23 | 株式会社Ihi | Bearing structure for supercharger, and supercharger |
CN109519237A (en) * | 2018-12-25 | 2019-03-26 | 天津北方天力增压技术有限公司 | A kind of ball-bearing turbocharger with high performance |
-
1991
- 1991-10-30 JP JP3284919A patent/JPH05125951A/en active Pending
Cited By (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2011143079A2 (en) * | 2010-05-14 | 2011-11-17 | Borgwarner Inc. | Exhaust-gas turbocharger |
WO2011143079A3 (en) * | 2010-05-14 | 2012-04-19 | Borgwarner Inc. | Exhaust-gas turbocharger |
CN102859122A (en) * | 2010-05-14 | 2013-01-02 | 博格华纳公司 | Exhaust-gas turbocharger |
US9638059B2 (en) | 2010-05-14 | 2017-05-02 | Borgwarner Inc. | Exhaust-gas turbocharger |
JP2013245663A (en) * | 2012-05-29 | 2013-12-09 | Ihi Corp | Supercharger |
WO2017199695A1 (en) * | 2016-05-20 | 2017-11-23 | 株式会社Ihi | Bearing structure for supercharger, and supercharger |
JPWO2017199695A1 (en) * | 2016-05-20 | 2018-10-11 | 株式会社Ihi | Turbocharger bearing structure and turbocharger |
US10927759B2 (en) | 2016-05-20 | 2021-02-23 | Ihi Corporation | Bearing structure for turbocharger and turbocharger |
CN109519237A (en) * | 2018-12-25 | 2019-03-26 | 天津北方天力增压技术有限公司 | A kind of ball-bearing turbocharger with high performance |
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