JPH0652053B2 - Exhaust gas turbine supercharger structure - Google Patents
Exhaust gas turbine supercharger structureInfo
- Publication number
- JPH0652053B2 JPH0652053B2 JP60241253A JP24125385A JPH0652053B2 JP H0652053 B2 JPH0652053 B2 JP H0652053B2 JP 60241253 A JP60241253 A JP 60241253A JP 24125385 A JP24125385 A JP 24125385A JP H0652053 B2 JPH0652053 B2 JP H0652053B2
- Authority
- JP
- Japan
- Prior art keywords
- lubricating oil
- exhaust gas
- head tank
- gas turbine
- journal bearing
- 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
- 239000010687 lubricating oil Substances 0.000 claims description 70
- 239000003921 oil Substances 0.000 claims description 18
- 239000000314 lubricant Substances 0.000 claims 1
- 230000007423 decrease Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 238000001816 cooling Methods 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
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
- 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
- F16C17/24—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load with devices affected by abnormal or undesired positions, e.g. for preventing overheating, for safety
-
- 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
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
- F16C33/06—Sliding surface mainly made of metal
- F16C33/10—Construction relative to lubrication
- F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
- F16C33/103—Construction relative to lubrication with liquid, e.g. oil, as lubricant retained in or near the bearing
-
- 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
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
- F16C33/06—Sliding surface mainly made of metal
- F16C33/10—Construction relative to lubrication
- F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
- F16C33/1045—Details of supply of the liquid to the bearing
-
- 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)
- Chemical & Material Sciences (AREA)
- Oil, Petroleum & Natural Gas (AREA)
- Supercharger (AREA)
Description
【発明の詳細な説明】 産業上の利用分野 本発明は、ガスタービンおよび遠心圧縮機等に適用され
る排気ガスタービン過給機の構造に関する。TECHNICAL FIELD The present invention relates to a structure of an exhaust gas turbine supercharger applied to a gas turbine, a centrifugal compressor and the like.
従来の技術 従来の排気ガスタービン過給機における潤滑油ヘッドタ
ンクは、過給機本体とは別に外部に設置されていた。そ
して、この別置の潤滑油ヘッドタンクから潤滑油を複数
の軸受に供給する場合は、１系統の潤滑油通路から全軸
受に同時に給油されていた。しかし、このような別置の
潤滑油ヘッドタンクは、大容量のタンクになると共に、
該タンクと過給機との間の配管作業を必要とし、船内艤
装コストがかかった。2. Description of the Related Art A conventional lubricating oil head tank in a conventional exhaust gas turbine supercharger has been installed outside the supercharger body. Then, when the lubricating oil is supplied to the plurality of bearings from the separately arranged lubricating oil head tank, the lubricating oil is simultaneously supplied to all the bearings from one system of the lubricating oil passage. However, such a separately installed lubricating oil head tank becomes a large capacity tank,
Piping work was required between the tank and the supercharger, and the outfitting cost for the ship was high.
このため、過給機本体内に潤滑油ヘッドタンクを内蔵し
たものが作られている。そして、この内蔵潤滑油ヘッド
タンクも、共通の、すなわち１系統の潤滑油通路から全
軸受に給油する構造となっている。For this reason, a supercharger body with a built-in lubricating oil head tank is made. This built-in lubricating oil head tank also has a structure in which oil is supplied to all bearings from a common, that is, one system of lubricating oil passage.
発明が解決しようとする課題 ところで、このような排気ガスタービン過給機の内蔵潤
滑油ヘッドタンクでは、危急停止時における潤滑油ヘッ
ドタンクの容量が比較的小さいため、１系統の潤滑油通
路から全軸受に給油すると給油時間が短くなってしま
う。このため、ロータディスクからの熱伝達により、タ
ービン側ジャーナル軸受が熱のダメージを受け、焼損す
る問題があった。特に、最近はディーゼル機関の大幅な
高出力化に伴う排気ガスエネルギの増大により、惰力回
転停止後の排気ガス管内放熱量が増大し、ロータディス
クへの熱伝達も増大しているので、このタービン側ジャ
ーナル軸受の焼損は重要な問題となっている。DISCLOSURE OF THE INVENTION Problems to be Solved by the Invention By the way, in such a built-in lubricating oil head tank of an exhaust gas turbine supercharger, since the capacity of the lubricating oil head tank at the time of emergency stop is relatively small, the entire lubricating oil passage from one system is used. Refueling the bearing shortens the refueling time. Therefore, there is a problem in that the turbine-side journal bearing is damaged by heat due to heat transfer from the rotor disk and burns out. In particular, recently, due to the increase in exhaust gas energy accompanying the drastic increase in output of diesel engines, the amount of heat released in the exhaust gas pipe after coasting has stopped increasing and the heat transfer to the rotor disk also increases. Burnout of turbine side journal bearings has become an important issue.
本発明は、このような従来技術の課題を解決するために
なされたもので、危急停止状態の発生時でもタービン側
ジャーナル軸受の焼損を防止できる排気ガスタービン過
給機の構造を提供することを目的とする。The present invention has been made to solve such a problem of the conventional art, and provides a structure of an exhaust gas turbine supercharger capable of preventing burnout of a turbine side journal bearing even when an emergency stop state occurs. To aim.
課題を解決するための手段 上記の課題を解決するために、本発明は、排気ガスター
ビン過給機本体内に内蔵潤滑油ヘッドタンクを有する排
気ガスタービン過給機の構造において、上記内蔵潤滑油
ヘッドタンクからの潤滑油通路を、上記ヘッドタンク内
の油面が所定以上の油面位置にあるときにのみヘッドタ
ンク内の潤滑油を少なくともタービン側ジャーナル軸受
を含む複数の軸受のすべてに給油可能にされた主潤滑油
通路と、上記油面が少なくとも上記所定油面に達しない
状態のとき上記タービン側ジャーナル軸受のみに給油可
能にされた副潤滑油通路との２系統に分けたものであ
る。Means for Solving the Problems In order to solve the above problems, the present invention relates to a structure of an exhaust gas turbine supercharger having a built-in lubricating oil head tank in an exhaust gas turbine supercharger body, wherein the internal lubricating oil is The lubricating oil passage from the head tank can be filled with lubricating oil in the head tank to all of the bearings including at least the turbine-side journal bearing only when the oil level in the head tank is above the prescribed level. And a sub-lubricating oil passage that can be refueled only to the turbine-side journal bearing when the oil level does not reach at least the predetermined oil level. .
作用 上記の手段によれば、排気ガスタービン過給機の危急停
止状態直後のまだ回転数の高い時には、潤滑油は主潤滑
油通路を通して全軸受に供給されると共に、タービン側
ジャーナル軸受には副潤滑油通路を通しても潤滑油が供
給される。そして、回転数低下後には、主潤滑油通路を
通しての全軸受への供給は行われなくなるが、タービン
側ジャーナル軸受のみには副潤滑油通路を通して潤滑油
が供給し続けられるので、タービン側ジャーナル軸受を
ロータディスクの熱影響から保護し、焼損を防止するこ
とができる。Action According to the above means, when the number of revolutions is still high immediately after the emergency stop state of the exhaust gas turbine supercharger, the lubricating oil is supplied to all the bearings through the main lubricating oil passage, and the turbine side journal bearing is sub-rotated. Lubricating oil is also supplied through the lubricating oil passage. After the number of revolutions drops, the supply of oil to all the bearings through the main lubricating oil passage is stopped, but the lubricating oil continues to be supplied only through the auxiliary lubricating oil passage to the turbine side journal bearing. Can be protected from the thermal influence of the rotor disk, and burnout can be prevented.
実施例 以下、図面を参照して本発明の実施例について詳細に説
明する。Example Hereinafter, an example of the present invention will be described in detail with reference to the drawings.
第１図は本発明に係る排気ガスタービン過給機の一実施
例を示す要部の軸方向断面図、第２図は該軸方向に直交
する断面の一部を示す図であり、第１図は第２図のＩ−
Ｉ線断面である。FIG. 1 is an axial sectional view of an essential part showing an embodiment of an exhaust gas turbine supercharger according to the present invention, and FIG. 2 is a diagram showing a part of a cross section orthogonal to the axial direction. The figure is I- in Figure 2.
It is an I line cross section.
これらの図において、排気ガスタービン過給機のタービ
ン側のタービン翼１３を有するロータディスク１１とロ
ータ軸１０とが連結している。このロータ軸１０は、主
スラスト軸受６、反スラスト軸受７、ブロワ側ジャーナ
ル軸受８およびタービン側ジャーナル軸受９によって支
持されている。また、ロータの内部には、上部に潤滑油
入口管１および空気抜管２（特に第２図を参照）を有す
る内蔵潤滑油ヘッドタンク３を設けてある。In these figures, a rotor disk 11 having turbine blades 13 on the turbine side of an exhaust gas turbine supercharger and a rotor shaft 10 are connected. The rotor shaft 10 is supported by a main thrust bearing 6, an anti-thrust bearing 7, a blower side journal bearing 8 and a turbine side journal bearing 9. Further, inside the rotor, a built-in lubricating oil head tank 3 having a lubricating oil inlet pipe 1 and an air vent pipe 2 (see especially FIG. 2) in the upper part is provided.
そして、この潤滑油ヘッドタンク３の中間部よりやや上
方から、その下方に向かって太い管状の主潤滑油通路４
が配管され、この主潤滑油通路４は全軸受６，７，８，
９にこれらを潤滑するために通じている。さらに、潤滑
油ヘッドタンク３の底部から、細い管状の副潤滑油通路
５が配管され、この副潤滑油通路５はタービン側ジャー
ナル軸受９のみに通じている。The main lubricating oil passage 4 has a tubular shape that is thicker from slightly above the middle portion of the lubricating oil head tank 3 toward the lower side.
The main lubricating oil passage 4 has all the bearings 6, 7, 8,
9 leads to lubricate them. Further, a thin tubular auxiliary lubricating oil passage 5 is piped from the bottom of the lubricating oil head tank 3, and the auxiliary lubricating oil passage 5 communicates only with the turbine-side journal bearing 9.
なお、第１図において、符号１２は過給機のコンプレッ
サを示している。In FIG. 1, reference numeral 12 indicates a compressor of the supercharger.
次に作用について説明する。潤滑油が入口管１より排気
ガスタービン過給機本体に内蔵した潤滑油ヘッドタンク
３に供給されると、潤滑油ヘッドタンク３内の空気は空
気抜管２より外部へ放出される。そして、潤滑油ヘッド
タンク３内には潤滑油が充満し、内部圧力がかかってく
る。これにより、潤滑油は潤滑油ヘッドタンク３内に延
びている主潤滑油通路４を流れ、全軸受すなわち主スラ
スト軸受６、反スラスト軸受７、ブロワ側ジャーナル軸
受８およびタービン側ジャーナル軸受９に供給される。
また、同時に、副潤滑油通路５からも潤滑油がガスター
ビン側ジャーナル軸受９に供給される。このような状態
が通常の給油状態である。Next, the operation will be described. When the lubricating oil is supplied from the inlet pipe 1 to the lubricating oil head tank 3 built in the main body of the exhaust gas turbine supercharger, the air in the lubricating oil head tank 3 is discharged to the outside from the air vent pipe 2. Then, the lubricating oil head tank 3 is filled with the lubricating oil and internal pressure is applied. As a result, the lubricating oil flows through the main lubricating oil passage 4 extending into the lubricating oil head tank 3 and is supplied to all the bearings, that is, the main thrust bearing 6, the anti-thrust bearing 7, the blower side journal bearing 8 and the turbine side journal bearing 9. To be done.
At the same time, the lubricating oil is also supplied from the auxiliary lubricating oil passage 5 to the gas turbine side journal bearing 9. Such a state is a normal refueling state.
さて、このような状態で潤滑油の圧力低下および潤滑油
ポンプ（図示せず）停止等の非常事態が発生した場合、
主機関の作動が停止し、排気エネルギも減少し、過給機
の運転は停止に向かってしまう。このような場合の主機
関トリップの初期段階における過給機には、排気エネル
ギが残存しまた高回転時の回転慣性力があるので、危急
停止時の初期段階（はじめの１〜２分程度）は、まだ全
軸受６，７，８，９に潤滑油を共通に供給する必要があ
る。この時、油面は潤滑油ヘッドタンク３の上部（天
井）から主潤滑油通路４の上端部まで下がり、全軸受に
潤滑油は共通に供給されている。Now, in such a situation, if an emergency situation such as a decrease in lubricating oil pressure or a stop of the lubricating oil pump (not shown) occurs,
The operation of the main engine stops, the exhaust energy also decreases, and the operation of the supercharger tends to stop. In such a case, the exhaust gas energy remains in the supercharger in the initial stage of the main engine trip and there is a rotational inertia force at high revolutions, so the initial stage during emergency stop (about 1 to 2 minutes at the beginning) Needs to supply lubricating oil to all bearings 6, 7, 8 and 9 in common. At this time, the oil level drops from the upper portion (ceiling) of the lubricating oil head tank 3 to the upper end portion of the main lubricating oil passage 4, and the lubricating oil is commonly supplied to all the bearings.
しかし、油面が主潤滑油通路４の上端部まで下がる間
に、過給機の回転数は低回転となり、スラストおよびジ
ャーナルの各軸受とも軸受負荷が極力軽減するので、通
常あるいは多量の潤滑油を必要としない。したがって、
ブロワ側に位置する低温部の主スラスト軸受６、反スラ
スト軸受７およびブロワ側ジャーナル軸受８には給油不
要で、これらの軸受は残り油で十分その潤滑機能を果た
す。However, while the oil level falls to the upper end of the main lubricating oil passage 4, the rotation speed of the supercharger becomes low, and the bearing load on each of the thrust and journal bearings is reduced as much as possible. Does not need Therefore,
It is not necessary to supply oil to the main thrust bearing 6, the anti-thrust bearing 7 and the blower side journal bearing 8 at the low temperature portion located on the blower side, and these bearings sufficiently perform their lubricating function with the remaining oil.
一方、過給機の回転低下後のロータ軸１０を介してのロ
ータディスク１１からの熱伝達によりタービン側ジャー
ナル軸受９が熱のダメージを受けることを防止すべく、
このタービン側ジャーナル軸受９を潤滑油で冷却する必
要が生じてくる。そこで、潤滑油ヘッドタンク３内の油
面が主潤滑油通路４の上端部より低くなった後は、潤滑
油を、副潤滑油通路５を通してタービン側ジャーナル軸
受９のみ供給する。これにより、タービン側ジャーナル
軸受９には長時間（約２０〜３０分程度）冷却すべく潤
滑油が供給されるので、過給機危急停止時でもロータデ
ィスク１０からの熱影響をタービン側ジャーナル軸受９
は受けることはなく、したがって該軸受の焼損を防止す
ることができる。On the other hand, in order to prevent the turbine-side journal bearing 9 from being damaged by heat due to heat transfer from the rotor disk 11 via the rotor shaft 10 after the rotation of the supercharger is reduced,
It becomes necessary to cool the turbine side journal bearing 9 with lubricating oil. Therefore, after the oil level in the lubricating oil head tank 3 becomes lower than the upper end portion of the main lubricating oil passage 4, the lubricating oil is supplied only to the turbine side journal bearing 9 through the auxiliary lubricating oil passage 5. As a result, the lubricating oil is supplied to the turbine-side journal bearing 9 for cooling for a long time (about 20 to 30 minutes). 9
Therefore, it is possible to prevent burning of the bearing.
発明の効果 以上述べたように、本発明によれば、排気ガスタービン
過給機の危急停止状態発生時には、副潤滑油通路を通し
て潤滑油をタービン側ジャーナル軸受に他の軸受よりも
長い時間供給するようにしているので、タービン側ジャ
ーナル軸受をロータディスクの熱影響から保護し、焼損
を防止することができ、したがって過給機の安全かつ円
滑な運転を達成して、信頼性を向上させることができ
る。As described above, according to the present invention, when an emergency stop state of the exhaust gas turbine supercharger occurs, the lubricating oil is supplied to the turbine side journal bearing for a longer time than the other bearings through the auxiliary lubricating oil passage. Therefore, it is possible to protect the turbine-side journal bearing from the thermal influence of the rotor disk and prevent burnout, thus achieving safe and smooth operation of the supercharger and improving reliability. it can.
また、潤滑油の主・副循環油通路への切換えは、切換弁
ではなくて、内蔵潤滑油ヘッドタンク内の主・副循環油
通路へ通じる開口部のヘッド差で行れるので、構造が簡
単でコストが安く、かつ損傷する部品がなくて信頼性を
一層向上させることができる。Also, switching the lubricating oil to the main / sub circulation oil passage can be done by the head difference of the opening that leads to the main / sub circulation oil passage in the built-in lubricating oil head tank, not by the switching valve. Therefore, the cost is low, and there are no parts to be damaged, so that the reliability can be further improved.
なお、本発明においても、潤滑油ヘッドタンクは排気ガ
スタービン過給機本体に内蔵されている型式であるの
で、別置の潤滑油ヘッドタンクの場合よりもタンク容量
を減少し、かつ配管を省略して、艤装コストを大幅に節
減できることは勿論である。In the present invention as well, since the lubricating oil head tank is a type built in the exhaust gas turbine supercharger main body, the tank capacity is reduced and piping is omitted as compared with the case of the lubricating oil head tank installed separately. And, of course, the outfitting cost can be greatly reduced.
第１図は本発明に係る排気ガスタービン過給機の一実施
例を示す要部の軸方向断面図、第２図は該軸方向に直交
する断面の一部を示す図であり、第１図は第２図のＩ−
Ｉ線断面である。 １……潤滑油入口管、２……空気抜管、３……潤滑油ヘ
ッドタンク、４……主潤滑油通路、５……副潤滑油通
路、６……主スラスト軸受、７……反スラスト軸受、８
……ブロワ側ジャーナル軸受、９……タービン側ジャー
ナル軸受、１０……ロータ軸、１１……ロータディス
ク、１２……コンプレッサ、１３……タービン翼。FIG. 1 is an axial sectional view of an essential part showing an embodiment of an exhaust gas turbine supercharger according to the present invention, and FIG. 2 is a diagram showing a part of a cross section orthogonal to the axial direction. The figure is I- in Figure 2.
It is an I line cross section. 1 ... Lubricating oil inlet pipe, 2 ... Air vent pipe, 3 ... Lubricating oil head tank, 4 ... Main lubricating oil passage, 5 ... Sub-lubricating oil passage, 6 ... Main thrust bearing, 7 ... Anti-thrust Bearing, 8
...... Blower side journal bearing, 9 ...... Turbine side journal bearing, 10 ...... Rotor shaft, 11 ...... Rotor disk, 12 ...... Compressor, 13 ...... Turbine blade.
Claims (1)
油ヘッドタンクを有する排気ガスタービン過給機の構造
において、上記内蔵潤滑油ヘッドタンクからの潤滑油通
路を、上記ヘッドタンク内の油面が所定以上の油面位置
にあるときにのみヘッドタンク内の潤滑油を少なくとも
タービン側ジャーナル軸受を含む複数の軸受のすべてに
給油可能にされた主潤滑油通路と、上記油面が少なくと
も上記所定油面に達しない状態のとき上記タービン側ジ
ャーナル軸受のみに給油可能にされた副潤滑油通路との
２系統に分けたことを特徴とする排気ガスタービン過給
機の構造。1. A structure of an exhaust gas turbine supercharger having a built-in lubricating oil head tank in an exhaust gas turbine supercharger main body, wherein a lubricating oil passage from the built-in lubricating oil head tank is provided with oil in the head tank. A main lubricating oil passage that is capable of supplying lubricating oil in the head tank to all of the plurality of bearings including at least the turbine-side journal bearing only when the surface is at a predetermined oil level position or more, and the oil level is at least the above A structure of an exhaust gas turbine supercharger, characterized in that it is divided into two systems, a sub-lubricant oil passage capable of supplying oil only to the turbine side journal bearing when it does not reach a predetermined oil level.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP60241253A JPH0652053B2 (en) | 1985-10-30 | 1985-10-30 | Exhaust gas turbine supercharger structure |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP60241253A JPH0652053B2 (en) | 1985-10-30 | 1985-10-30 | Exhaust gas turbine supercharger structure |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS62101837A JPS62101837A (en) | 1987-05-12 |
| JPH0652053B2 true JPH0652053B2 (en) | 1994-07-06 |
Family
ID=17071487
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP60241253A Expired - Lifetime JPH0652053B2 (en) | 1985-10-30 | 1985-10-30 | Exhaust gas turbine supercharger structure |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0652053B2 (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19925779B4 (en) * | 1999-06-05 | 2014-01-23 | Abb Turbo Systems Ag | Exhaust gas turbocharger with a emergency oil tank |
| WO2008023067A1 (en) * | 2006-08-24 | 2008-02-28 | Abb Turbo Systems Ag | Emergency oil tank |
| JP6523655B2 (en) * | 2014-10-28 | 2019-06-05 | 三菱重工業株式会社 | Turbocharger and engine equipped with the same |
| DE102017114609A1 (en) * | 2017-06-30 | 2019-01-03 | Man Diesel & Turbo Se | Exhaust gas turbocharger with chambered oil distribution chamber |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS4112481Y1 (en) * | 1964-04-07 | 1966-06-13 | ||
| JPS60114240U (en) * | 1984-01-10 | 1985-08-02 | 三菱重工業株式会社 | Turbocharger lubrication system |
-
1985
- 1985-10-30 JP JP60241253A patent/JPH0652053B2/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| JPS62101837A (en) | 1987-05-12 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| EXPY | Cancellation because of completion of term |