JP2934530B2 - Centrifugal compressor - Google Patents
Centrifugal compressorInfo
- Publication number
- JP2934530B2 JP2934530B2 JP3143231A JP14323191A JP2934530B2 JP 2934530 B2 JP2934530 B2 JP 2934530B2 JP 3143231 A JP3143231 A JP 3143231A JP 14323191 A JP14323191 A JP 14323191A JP 2934530 B2 JP2934530 B2 JP 2934530B2
- Authority
- JP
- Japan
- Prior art keywords
- impeller
- air
- pressure
- temperature
- centrifugal compressor
- 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
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/08—Sealings
- F04D29/16—Sealings between pressure and suction sides
- F04D29/161—Sealings between pressure and suction sides especially adapted for elastic fluid pumps
- F04D29/162—Sealings between pressure and suction sides especially adapted for elastic fluid pumps of a centrifugal flow wheel
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/58—Cooling; Heating; Diminishing heat transfer
- F04D29/582—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps
- F04D29/5846—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps cooling by injection
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B3/00—Engines characterised by air compression and subsequent fuel addition
- F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Supercharger (AREA)
- Turbine Rotor Nozzle Sealing (AREA)
Description
【０００１】[0001]
【産業上の利用分野】本発明は、例えばエンジンの過給
機の圧縮機等に適用される遠心圧縮機に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention
The present invention relates to a centrifugal compressor applied to a compressor of a compressor.
【０００２】[0002]
【従来の技術】図３は従来の遠心圧縮機の構造説明図、
図４はラビリンスシール部を拡大した作用説明図であ
る。図において、本遠心圧縮機の羽根車１背面にはケー
シング１２との間にラビリンスパッキン５が配設され、
羽根車１出口と羽根車１背部に形成されたシール空間７
との間をシールしている。シール空間７は放風孔８を介
して外部と導通しており、ラビリンスパッキン５を通過
してシール空間７へ入る若干量の空気を外部へ放出して
シール空間７の圧力を低下させる。これにより、羽根車
１出口における高圧の空気が羽根車１背面に入ってロー
タ軸２を羽根車１入口の方向に押す推力の発生が阻止さ
れ、主スラスト軸受３の面圧を低下させて主スラスト軸
受３の負担を低減している。１１はスラストカラー、４
は反スラスト軸受である。2. Description of the Related Art FIG. 3 is a structural explanatory view of a conventional centrifugal compressor.
FIG. 4 is an operation explanatory view in which the labyrinth seal portion is enlarged . In the drawing, a labyrinth packing 5 is disposed between a casing 12 and a rear surface of an impeller 1 of the centrifugal compressor,
Impeller 1 seal space 7 formed at the outlet and the impeller 1 back portion
The seal is between. The seal space 7 communicates with the outside through the air discharge holes 8, and discharges a small amount of air that passes through the labyrinth packing 5 and enters the seal space 7 to reduce the pressure in the seal space 7. This prevents high-pressure air at the outlet of the impeller 1 from entering the back of the impeller 1 and prevents the generation of thrust for pushing the rotor shaft 2 toward the inlet of the impeller 1, and the surface pressure of the main thrust bearing 3. And the load on the main thrust bearing 3 is reduced. 11 is the thrust color, 4
Is an anti-thrust bearing.
【０００３】[0003]
【発明が解決しようとする課題】上記のような従来の遠
心圧縮機において、羽根車１出口における空気の温度は
遠心圧縮機の圧力比に応じて高くなっており、例えば常
温の空気を吸込んだ場合でも圧力比が約４．０程度であ
ると羽根車１出口における空気の温度は２００℃以上に
達する。この高温の空気がラビリンスパッキン５を通過
すると、ラビリンスパッキン５及び羽根車１のフィンの
相対回転によって生じた摩擦熱によって上記空気がさら
に昇温し、かかる高熱によって羽根車１背面が加熱され
る。通常、このような大気を吸込む単段型の遠心圧縮機
においては、羽根車の材料としてアルミ合金が用いられ
ているが、羽根車１背面の空気により加熱されると、羽
根車１は、その温度が上昇して材料の強度が低下する。
このため、羽根車１がアルミ合金製の場合は高圧力比を
確保することが困難となる。また、羽根車１の温度上昇
は空気の温度上昇を招き、圧縮機効率が低下する要因と
なる。In the conventional centrifugal compressor as described above, the temperature of the air at the outlet of the impeller 1 is increased in accordance with the pressure ratio of the centrifugal compressor. Even in this case, when the pressure ratio is about 4.0, the temperature of the air at the outlet of the impeller 1 reaches 200 ° C. or more. When the air of high temperature passes through the labyrinth packing 5, the air is further heated by the frictional heat generated by the relative rotation of the fins of the labyrinth packing 5 and the impeller 1, impeller 1 back is heated by such high heat. Normally, in such a single-stage centrifugal compressor that sucks air, an aluminum alloy is used as a material of the impeller. However, when heated by air behind the impeller 1, the impeller 1 As the temperature increases, the strength of the material decreases.
For this reason, when the impeller 1 is made of an aluminum alloy, it is difficult to secure a high pressure ratio. Further, a rise in the temperature of the impeller 1 causes a rise in the temperature of the air, which causes a reduction in compressor efficiency.
【０００４】[0004]
【課題を解決するための手段】本発明に係る遠心圧縮機
は上記課題の解決を目的にしており、羽根車の背部に環
状多重に配設され、上記羽根車の出口と羽根車の背部に
形成される空間との間をシールするシール機構を備えた
遠心圧縮機において、上記シール機構の中間部に、上記
羽根車出口の圧力よりも高圧の冷気体を供給する供給口
を開口し、上記冷気体を上記供給口から上記シール機構
の外周側及び内周側へと流すように構成したことを特徴
としている。 SUMMARY OF THE INVENTION A centrifugal compressor according to the present invention has an object to solve the above-mentioned problems, and has a ring at the back of an impeller.
Arranged at the outlet of the impeller and the back of the impeller
Equipped with a seal mechanism to seal between the space formed
In the centrifugal compressor, the intermediate part of the sealing mechanism
Supply port for supplying cold gas higher in pressure than the impeller outlet pressure
And the sealing mechanism through the supply port for the cold gas.
Characterized in that it is configured to flow to the outer and inner peripheral sides of the
And
【０００５】[0005]
【作用】即ち、本発明に係る遠心圧縮機においては、羽
根車の背部にシール機構が環状多重に配設されて羽根車
出口と羽根車背面の空間との間をシールするとともに、
該シール機構の中間部に冷気体の供給口を開口し、該供
給口から羽根車出口における圧力よりも高圧の冷気体が
供給されるように構成しているので、高圧の冷気体は上
記シール機構に沿って、外周の羽根車出口側及び内周の
空間内に分流して流れる。この際において、上記冷気体
の圧力は羽根車出口における圧力よりも高圧であるの
で、羽根車出口の高温の気体がシール機構を経て冷気体
の供給口側へ流れることは無く、冷気体はシール機構に
沿って羽根車出口側へと抵抗なく流れて上記 高温の気体
をシールするとともに、羽根車背面を冷却する。 また、
上記冷気体はシール機構に沿って、内周側の空間へと流
れて気体のシールを行なうとともに、羽根車の内周側背
面を冷却する。これにより、上記供給口からシール機構
に供給される冷気体によって、羽根車出口側の気体のシ
ールが確実になされるとともに、羽根車背面が羽根車出
口における高温の気体で加熱されることがなく、上記供
給口から供給される冷気体により冷却され、羽根車の温
度上昇が抑制される。 That is, in the centrifugal compressor according to the present invention, a seal mechanism is arranged in a ring multiplex on the back of the impeller to seal between the impeller outlet and the space behind the impeller,
A cold gas supply port is opened in the middle of the seal mechanism,
Since the inlet is configured to supply cold gas at a pressure higher than the pressure at the impeller outlet, the high-pressure cold gas is
Along the seal mechanism, the outer periphery of the impeller exit side and the inner periphery
It shunts into the space and flows . At this time, the cold gas
Pressure is higher than the pressure at the impeller outlet
The hot gas at the impeller outlet passes through the sealing mechanism
Does not flow to the supply port side of the
High-temperature gas flowing along the impeller exit side without resistance
And cool the back of the impeller. Also,
The cold gas flows along the seal mechanism to the inner space.
To seal the gas, and the inner circumference of the impeller.
Cool the surface. This allows the sealing mechanism to be
The cold gas supplied to the
With Lumpur is made reliably, without the impeller back is heated at a high temperature of the gas at the impeller outlet, the test
Cooled by cold gas supplied from the inlet , the temperature of the impeller
The degree rise is suppressed.
【０００６】[0006]
【実施例】図１は本発明の一実施例に係る遠心圧縮機の
構造説明図、図２は作用説明図である。図において、本
実施例に係る遠心圧縮機はエンジンの過給機の圧縮機と
して使用されるものであり、図１に示すように、ロータ
軸２に固定された羽根車１の背面には、ケーシング１２
との間にラビリンスパッキン１５が半径方向において多
重に配設されている。そしてこのラビリンスパッキン１
５は、羽根車１出口と、羽根車１の背部に形成されたシ
ール空間７との間をシールしている。上記シール空間７
は放風孔８によって外部と導通しており、上記ラビリン
スパッキン１５を通過して該シール空間７へ入る若干量
の空気を外部へ放出して該シール空間７の圧力を低下さ
せるようになっている。これにより、羽根車１出口にお
ける高圧の空気が羽根車１背面に入って、ロータ軸２を
羽根車１入口の方向に押す推力を発生するのを阻止し、
これによって主スラスト軸受３の面圧を低下させ、同主
スラスト軸受３の負担を低減している。尚、１１はスラ
ストカラー、４は反スラスト軸受である。FIG. 1 is a structural explanatory view of a centrifugal compressor according to one embodiment of the present invention, and FIG. 2 is an operational explanatory view. In the figure, the centrifugal compressor according to the present embodiment is intended to be used in <br/> with the engine turbocharger compressor, as shown in FIG. 1, the rotor
On the back of the impeller 1 fixed to the shaft 2 , a casing 12
Between the labyrinth packing 15 in the radial direction.
It is arranged heavily . And this labyrinth packing 1
Numeral 5 seals between the impeller 1 outlet and a seal space 7 formed in the back of the impeller 1. The seal space 7
Is communicated with the outside through the air discharge holes 8, discharges a small amount of air that passes through the labyrinth packing 15 and enters the seal space 7 to the outside, and lowers the pressure in the seal space 7. I have. This prevents high-pressure air at the exit of the impeller 1 from entering the back of the impeller 1 and generating a thrust for pushing the rotor shaft 2 toward the entrance of the impeller 1 .
Thereby, the surface pressure of the main thrust bearing 3 is reduced, and the burden on the main thrust bearing 3 is reduced. In addition, 11 is a thrust collar, and 4 is an anti-thrust bearing.
【０００７】羽根車１出口における空気の温度は遠心圧
縮機の圧力比に応じて高くなっており、例えば常温の空
気を吸込んだ場合でも圧力比が約４．０程度であると羽
根車１出口における空気の温度は２００℃以上に達す
る。この高熱により羽根車１背面が加熱されるのを防止
するため、この実施形態に係る遠心圧縮機におけるラビ
リンスパッキン１５はフィンが外側と内側の２群に分け
られ、その間つまりラビリンスパッキン１５の中間部に
環状空間６が形成されている。９は上記環状空間６に連
通される空気通路であり、該空気通路９には、低温で羽
根車１出口における圧力Ｐ1 よりも高い圧力Ｐ2 の空気
が外部から供給されるようになっている。この空気即ち
冷気体としては、例えば過給機から空気冷却器を経てエ
ンジンへ供給される低温高圧力の圧縮空気などのよう
に、羽根車１出口における空気の圧力Ｐ1 よりも高く、
かつ低温の空気を用い、かかる冷却空気を羽根車１背面
のラビリンスパッキン１５へ導くようにする。[0007] The temperature of the air at the outlet of the impeller 1 is increased in accordance with the pressure ratio of the centrifugal compressor. For example, even if air at normal temperature is sucked, if the pressure ratio is about 4.0, the outlet of the impeller 1 The temperature of the air at 200 ° C. or higher. An intermediate portion of this for high heat by the impeller 1 rear is prevented from being heated, labyrinth packing 15 of the centrifugal compressor according to this embodiment the fins are divided into two groups of outside and inside, between words labyrinth packing 15 An annular space 6 is formed. 9 is connected to the annular space 6
The air passage 9 is configured such that air at a low temperature and a pressure P 2 higher than the pressure P 1 at the outlet of the impeller 1 is supplied from outside. This air
The cold gas is higher than the air pressure P 1 at the exit of the impeller 1, such as low-temperature high-pressure compressed air supplied to the engine from the supercharger via the air cooler , for example.
And using a low temperature air, to direct such cooling air to the impeller 1 the back of the labyrinth packing 15.
【０００８】上記のように構成された遠心圧縮機におい
て、過給機で高圧に加圧され空気冷却器にて冷却された
空気等の低温高圧の空気（冷気体）は、空気通路９から
環状空間６に入る。該環状空間６内に入った空気は環状
空間９から外周側と内周側の２方向に分かれてラビリン
スパッキン１５を流れる。 この際において、上記空気の
圧力Ｐ 2 は羽根車１出口の圧力Ｐ 1 よりも高い圧力を有
するので、羽根車１出口の高温の気体がラビリンスパッ
キン１５に流入することは無く、ラビリンスパッキン１
５には上記環状空間６を経た低温空気が流れ、この低温
空気によって羽根車１背部が冷却される。一方、上記環
状空間６から内周側へ分流した低温空気はラビリンスパ
ッキン１５の内周側部分を流れて羽根車１背部を冷却す
る。従来の遠心圧縮機における羽根車背面のラビリンス
パッキンでは、内側のシール空間内の空気を放出して圧
力を下げているので、羽根車出口における空気は若干量
がラビリンスパッキンを通過する。これに対して、この
実施形態に係る遠心圧縮機におけるラビリンスパッキン
１５はフィンが外側と内側との２群に分かれており、そ
のフィン分割部にある環状空間６に、上記のように、低
温で、羽根車１出口における圧力Ｐ1 よりも高い圧力Ｐ
2 の空気が供給される。供給された低温空気は羽根車１
出口における圧力Ｐ1 よりも高い圧力Ｐ2 を有している
ので、上記のように、羽根車１出口における高温空気が
ラビリンスパッキン１５を通って環状空間６に流れるこ
とはなく、逆に環状空間６に供給された低温空気が羽根
車１出口側へ流れる。従って、この実施形態によれば、
羽根車１背面に高温の羽根車１出口における空気が流れ
込んで羽根車１背面が上記高温空気で加熱されることが
なく、空気通路９を介して外部から供給される低温空気
で冷却されることとなる。これにより、羽根車１の温度
上昇を抑えることができ、この温度上昇による羽根車１
の強度低下が防止される。なお、羽根車１の背部のシー
ル空間７と環状空間６との間はラビリンスパッキン１５
によりシールされているが、シール空間７へ若干量の上
記低温空気が流れ込むことがあっても、放風孔８からこ
の空気を放出してシール空間７内の圧力Ｐ3 を下げてい
る。これにより、従来の遠心圧縮機と同様にスラスト力
がバランスすることとなり、主スラスト軸受３の負荷が
増大することはない。In the centrifugal compressor configured as described above,
And pressurized to high pressure with a supercharger and cooled with an air cooler
Low-temperature and high-pressure air (cold gas) such as air flows from the air passage 9
It enters the annular space 6. The air entering the annular space 6 is annular
Labyrin divided from space 9 into two directions, outer and inner
It flows through the sparkkin 15. At this time, the air
The pressure P 2 are have a pressure higher than the pressure P 1 of the impeller 1 outlet
High temperature gas at the exit of impeller 1
It does not flow into the kin 15 and the labyrinth packing 1
The low-temperature air flowing through the annular space 6 flows through the low-temperature
The air cools the back of the impeller 1 . On the other hand,
Low-temperature air diverted from the inner space 6 to the inner peripheral side
To flow through the inner peripheral side of the chuck 15 to cool the back of the impeller 1
You. In the labyrinth packing on the back side of the impeller in the conventional centrifugal compressor, since the pressure in the inner seal space is released to reduce the pressure, a small amount of air at the impeller outlet passes through the labyrinth packing. In contrast, this
Labyrinth packing 15 of the centrifugal compressor according to the embodiment is divided into two groups of fins between outside and inside, the annular space 6 in the fin dividing unit, as described above, at low temperatures, in the impeller 1 outlet Pressure P higher than pressure P 1
2 air is supplied. The supplied low-temperature air is impeller 1
Because it has a higher pressure P 2 than the pressure P 1 at the outlet, as described above, it does not flow into the annular space 6 the hot air in the impeller 1 exit through the labyrinth packing 15, the annular space conversely The low-temperature air supplied to 6 flows to the impeller 1 exit side. Therefore, according to this embodiment,
The air at the outlet of the high-temperature impeller 1 flows into the back of the impeller 1 and the back of the impeller 1 is not heated by the high-temperature air, but is cooled by low-temperature air supplied from outside through the air passage 9. Becomes Thereby, the temperature rise of the impeller 1 can be suppressed, and the impeller 1
Is prevented from decreasing in strength. A labyrinth packing 15 is provided between the seal space 7 at the back of the impeller 1 and the annular space 6.
, But a little over the seal space 7
Even if the serial low-temperature air flows, this from Hokazeana 8
It has reduced the pressure P 3 of the sealing space 7 by releasing the air
You. This makes it possible to thrust force as in the conventional centrifugal compressors are balanced, load on the main thrust bearing 3 is not increased.
【０００９】[0009]
【発明の効果】本発明に係る遠心圧縮機は前記のように
構成されており、羽根車の背部に設けられたシール機構
の中間部に気体供給口から供給されて外周側及び内周側
へ分流する冷気体によって羽根車背面が冷却されるの
で、羽根車背面が羽根車出口からの高温気体で加熱され
ることがなく、羽根車の温度上昇が防止される。これに
より、羽根車の強度低下が防止され、該羽根車がアルミ
合金製の場合でも高圧力比を確保することができるとと
もに、羽根車により圧縮される気体の温度が降下するこ
とにより、圧縮機効率が向上する。The centrifugal compressor according to the present invention is constructed as described above, and has a seal mechanism provided at the back of the impeller.
Is supplied from the gas supply port to the middle part of the
The backside of the impeller is cooled by the cold gas
Therefore , the rear surface of the impeller is not heated by the high-temperature gas from the impeller outlet, and the temperature of the impeller is prevented from rising. to this
This prevents a decrease in the strength of the impeller, ensures a high pressure ratio even when the impeller is made of an aluminum alloy , and reduces the temperature of the gas compressed by the impeller .
Thus , the compressor efficiency is improved.
【図１】図１は本発明の一実施例に係る遠心圧縮機の断
面図である。FIG. 1 is a sectional view of a centrifugal compressor according to one embodiment of the present invention.
【図２】図２はその作用説明図である。FIG. 2 is an explanatory diagram of the operation.
【図３】図３は従来の遠心圧縮機の断面図である。FIG. 3 is a sectional view of a conventional centrifugal compressor.
【図４】図４はその作用説明図である。FIG. 4 is an explanatory diagram of the operation.
１ 羽根車 ２ ロータ軸 ３ 主スラスト軸受 ４ 反スラスト軸受 ６ 環状空間 ７ シール空間 ８ 放風孔 ９ 空気通路 １１ スラストカラー １２ ケーシング １５ ラビリンスパッキン1 impeller 2 rotor shaft 3 main thrust bearing 4 anti-thrust bearing 6 annular space 7 seal space 8 Hokazeana 9 air communication path 11 thrust collar 12 casing 15 labyrinth packing
───────────────────────────────────────────────────── フロントページの続き (72)発明者 田川 正義 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 昭61−112737（ＪＰ，Ａ) 特開 平２−245496（ＪＰ，Ａ) 特開 昭50−208（ＪＰ，Ａ) 実開 昭61−130726（ＪＰ，Ｕ) 実開 昭57−32258（ＪＰ，Ｕ) (58)調査した分野(Int.Cl.6，ＤＢ名) F04D 29/08 F01D 5/08 F02B 39/00 F04D 29/58 ──────────────────────────────────────────────────続 き Continuation of the front page (72) Inventor Masayoshi Tagawa 1-1, Akunouracho, Nagasaki City Inside Nagasaki Shipyard, Mitsubishi Heavy Industries, Ltd. (56) References JP-A-61-112737 (JP, A) JP-A-2 JP-A-50-208 (JP, A) JP-A-61-130726 (JP, U) JP-A-57-32258 (JP, U) (58) Fields investigated (Int. . 6, DB name) F04D 29/08 F01D 5/08 F02B 39/00 F04D 29/58
Claims (1)
羽根車の出口と羽根車の背部に形成される空間との間を
シールするシール機構を備えた遠心圧縮機において、上
記シール機構の中間部に、上記羽根車出口の圧力よりも
高圧の冷気体を供給する供給口を開口し、上記冷気体を
上記供給口から上記シール機構の外周側及び内周側へと
流すように構成したことを特徴とする遠心圧縮機。1. An annular multiplex arrangement is provided on the back of an impeller.
Between the exit of the impeller and the space formed at the back of the impeller
In centrifugal compressors equipped with a sealing mechanism for sealing,
In the middle of the seal mechanism, the pressure at the impeller outlet
Open the supply port for supplying high-pressure cold gas, and
From the supply port to the outer and inner peripheral sides of the seal mechanism
A centrifugal compressor characterized by being configured to flow .
Priority Applications (6)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3143231A JP2934530B2 (en) | 1991-06-14 | 1991-06-14 | Centrifugal compressor |
| EP92106288A EP0518027B1 (en) | 1991-06-14 | 1992-04-10 | Centrifugal compressor |
| DE69203293T DE69203293T2 (en) | 1991-06-14 | 1992-04-10 | Centrifugal compressors. |
| FI921758A FI921758A (en) | 1991-06-14 | 1992-04-21 | CENTRIFUGALKOMPRESSOR |
| US07/897,794 US5251576A (en) | 1991-06-14 | 1992-06-12 | System and method for feeding fuel to a fine-particle-mixed fuel burning diesel engine |
| KR1019920010196A KR950006873B1 (en) | 1991-06-14 | 1992-06-12 | Centrifugal compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3143231A JP2934530B2 (en) | 1991-06-14 | 1991-06-14 | Centrifugal compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH04365997A JPH04365997A (en) | 1992-12-17 |
| JP2934530B2 true JP2934530B2 (en) | 1999-08-16 |
Family
ID=15333954
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP3143231A Expired - Lifetime JP2934530B2 (en) | 1991-06-14 | 1991-06-14 | Centrifugal compressor |
Country Status (5)
| Country | Link |
|---|---|
| EP (1) | EP0518027B1 (en) |
| JP (1) | JP2934530B2 (en) |
| KR (1) | KR950006873B1 (en) |
| DE (1) | DE69203293T2 (en) |
| FI (1) | FI921758A (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007162683A (en) * | 2005-12-14 | 2007-06-28 | Hamilton Sundstrand Corp | Design of acm cooling flow passage and thrust load |
| WO2014087966A1 (en) | 2012-12-05 | 2014-06-12 | 三菱重工業株式会社 | Centrifugal compressor, supercharger with same, and method for operating centrifugal compressor |
| WO2016059866A1 (en) * | 2014-10-17 | 2016-04-21 | 三菱重工業株式会社 | Labyrinth seal, centrifugal compressor, and supercharger |
| US11002291B2 (en) | 2016-03-30 | 2021-05-11 | Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. | Compressor impeller |
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| US4810599A (en) | 1987-03-27 | 1989-03-07 | Japan Synthetic Rubber Co., Ltd. | Structure suitable for solid electrochemical elements |
| DE59709283D1 (en) * | 1997-12-23 | 2003-03-13 | Abb Turbo Systems Ag Baden | Method and device for contactless sealing of a separation gap formed between a rotor and a stator |
| DE19845375A1 (en) | 1998-10-02 | 2000-04-06 | Asea Brown Boveri | Indirect cooling process for flow in gap between turbine rotor and stator, involving use of water to cool stator part adjacent to gap |
| DE59809867D1 (en) | 1998-05-25 | 2003-11-13 | Abb Turbo Systems Ag Baden | centrifugal compressors |
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| CN1191433C (en) * | 1999-10-20 | 2005-03-02 | Abb涡轮系统有限公司 | Method and device for the indirect cooling of a flow regime in radial slits formed between the rotors and stators of turbomachines |
| EP1222399B1 (en) * | 1999-10-20 | 2003-08-13 | ABB Turbo Systems AG | Method and device for cooling the flow in the radial gaps formed between rotors and stators of turbine-type machines |
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| US7252474B2 (en) * | 2003-09-12 | 2007-08-07 | Mes International, Inc. | Sealing arrangement in a compressor |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE249336C (en) * | 1900-01-01 | |||
| FR379125A (en) * | 1907-06-21 | 1907-10-25 | Wilhelm Heinrich Eyermann | axial pressure balancing in turbines, rotary pumps and compressors |
| US3650634A (en) * | 1970-11-06 | 1972-03-21 | Carrier Corp | Centrifugal refrigeration compressor |
-
1991
- 1991-06-14 JP JP3143231A patent/JP2934530B2/en not_active Expired - Lifetime
-
1992
- 1992-04-10 EP EP92106288A patent/EP0518027B1/en not_active Expired - Lifetime
- 1992-04-10 DE DE69203293T patent/DE69203293T2/en not_active Expired - Fee Related
- 1992-04-21 FI FI921758A patent/FI921758A/en not_active Application Discontinuation
- 1992-06-12 KR KR1019920010196A patent/KR950006873B1/en not_active IP Right Cessation
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007162683A (en) * | 2005-12-14 | 2007-06-28 | Hamilton Sundstrand Corp | Design of acm cooling flow passage and thrust load |
| JP4583358B2 (en) * | 2005-12-14 | 2010-11-17 | ハミルトン・サンドストランド・コーポレイション | ACM cooling flow path and thrust load design |
| WO2014087966A1 (en) | 2012-12-05 | 2014-06-12 | 三菱重工業株式会社 | Centrifugal compressor, supercharger with same, and method for operating centrifugal compressor |
| WO2016059866A1 (en) * | 2014-10-17 | 2016-04-21 | 三菱重工業株式会社 | Labyrinth seal, centrifugal compressor, and supercharger |
| JP2016079904A (en) * | 2014-10-17 | 2016-05-16 | 三菱重工業株式会社 | Labyrinth seal, centrifugal compressor and supercharger |
| CN108026938A (en) * | 2014-10-17 | 2018-05-11 | 三菱重工业株式会社 | Labyrinth, centrifugal compressor and supercharger |
| CN108026938B (en) * | 2014-10-17 | 2019-12-24 | 三菱重工业株式会社 | Labyrinth seal, centrifugal compressor, and supercharger |
| US11002291B2 (en) | 2016-03-30 | 2021-05-11 | Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. | Compressor impeller |
Also Published As
| Publication number | Publication date |
|---|---|
| KR950006873B1 (en) | 1995-06-23 |
| JPH04365997A (en) | 1992-12-17 |
| EP0518027B1 (en) | 1995-07-05 |
| FI921758A (en) | 1992-12-15 |
| KR930000807A (en) | 1993-01-15 |
| EP0518027A1 (en) | 1992-12-16 |
| FI921758A0 (en) | 1992-04-21 |
| DE69203293T2 (en) | 1996-01-25 |
| DE69203293D1 (en) | 1995-08-10 |
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