CN1191433C - Method and device for the indirect cooling of a flow regime in radial slits formed between the rotors and stators of turbomachines - Google Patents
Method and device for the indirect cooling of a flow regime in radial slits formed between the rotors and stators of turbomachines Download PDFInfo
- Publication number
- CN1191433C CN1191433C CNB998169625A CN99816962A CN1191433C CN 1191433 C CN1191433 C CN 1191433C CN B998169625 A CNB998169625 A CN B998169625A CN 99816962 A CN99816962 A CN 99816962A CN 1191433 C CN1191433 C CN 1191433C
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- China
- Prior art keywords
- cooling fluid
- cooling
- radial gap
- stator component
- air
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- Expired - Fee Related
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Classifications
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- 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
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- 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
- F04D29/584—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps cooling or heating the machine
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- 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
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/284—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors
Abstract
The present invention relates to method for improving cooling effect, which is used for cooling airflow in a sagittal gap formed between a turbine rotor and a stator. In addition, the present invention also provides a simple, cheap and firm device for implementing the method. According to requirements of the present invention, water is used as cooling liquid (29) to cool a stator member adjacent to the sagittal gap (24); thus, at least one empty slot (26) can be formed in the stator member (20) adjacent to the sagittal gap (24), or at least one cavity (38) is arranged on the stator member (20). The empty slot (26) or the cavity (38) is connected with an input duct (27) used for the cooling liquid (29), and an output duct (27).
Description
Technical field
The present invention relates to be used for cooling indirectly at a method and a device of the air-flow that is formed at the radial gap between turbine rotor and stator, as the technical field of preamble section qualification before preamble section before the claim 1 and the claim 7; But be used for especially cooling off indirectly at the compressor wheels of a centrifugal compressor and the air-flow of the radial gap between the housing.
Background technique
In order to seal the system of rotation, contactless sealing configuration, especially labyrinth sealing in the turbo machine manufacturing, have been developed widely.Separate slot because the flow boundary layer that forms then produces a high friction horsepower what be arranged in fluid flow between rotation and static member.This just causes to the heating that separates the fluid in the slot with therefore to separating the slot heating of member on every side.The result that this high material temperature causes is the decline in working life of this respective members.
The centrifugal compressor that the sealing geometric features is not set in separating slot of a simple structure has been disclosed among the DE 19548852A1.And wherein, because the frictional heat that the mobile shear layer on the back side wall of compressor wheels produces causes the heating of compressor wheels and its operating life is descended.
Disclose a kind of cooling structure that is used for centrifugal compressor in EP 0518027B1, this cooling structure has the sealing geometry on a kind of dorsal surface that is positioned at compressor wheels.For this reason at the annular chamber that constitutes between the single seal element on the additional shell body wall side that is positioned at centrifugal compressor.Import a kind of gas of cooling in this ring cavity, it has the higher pressure of pressure that reaches than the outlet port at compressor wheels.This air effect that is transfused to is cooled off as impact type.It separately and mainly radially flows toward interior and past other places in sealing area.Realize also that in addition a prevention flows through the effect of this separation slot from the hot compressed air of the outlet of compressor wheels.But the frictional loss that the air that is blown in this way also causes thrust to increase and add in flow boundary layer.
Except this direct cooling a kind of also to disclose among the external DE 19652754A1 indirectly to the cooling of the back side wall of compressor wheels or to by separating the cooling of the mobile medium of slot.For this reason on housing structure body or be arranged in the housing structure of settling on the dorsal surface input and a dispensing device that is connected with the lubrication system of turbosupercharger is set with constitute separating slot with it.Used this oil as lubricant oil as cooling medium, the lubrication oil circulation of this turbosupercharger is branched setting for this reason.A defective of this cooling is high relatively oily demand and the heat that adds discharging from oil cooler.This will cause the structural volume of an increasing of cooler.In addition, under a kind of failure condition that has damaged corresponding construction spare, there is the fire and explosive risks that increases.
A kind of water cooling of bearing housing of turbosupercharger is also disclosed by US 4815184.Yet this cooling is to be used for eliminating in the stop carbon distribution danger of lubricant oil that the back leaves in its bearing housing of turbosupercharger.Therefore opposite with the solution of prior art recited above, the input of this cooling medium not need carry out during the continuous operation but more specifically say under the shut-down situation in turbosupercharger just essential.The type of cooling of the bearing housing of this form can not provide any with reference to indication to a kind of scheme of the air-flow of cooling ' in the radial gap that is formed between turbine rotor and stator it ' indirectly thus.In addition, this solution is not also studied the cooling structure of midfeather clearly.
Disclose a kind of indirect cooling scheme to Diffuser in US 2384251, wherein a cooling medium is pumped by a ring cavity that surrounds this Diffuser.Yet this document is not studied the cooling of midfeather yet, so any reference indication about the air-flow of indirect cooling in the radial gap that is formed between turbine rotor and stator is not provided yet.
Summary of the invention
The present invention attempts to avoid all these above-mentioned defectives.The invention task is to create a kind of improved method of its cooling action that makes to be used for cooling off the air-flow being formed at the radial gap between turbine rotor and stator.In addition, can also provide a kind of simple, with low cost and firm being used to implement the device of described method.
By the invention requirement, this task is so realized, on a method basis that limits according to preamble section before the claim 1, water is applied as cooling fluid to be used for the stator component adjacent with radial gap.
This glassware for drinking water that is used as cooling medium has density and a specific heat that about twice big higher slightly than known lubricant oil.Because the hot-fluid by cooling medium discharging is directly proportional in the product of density and specific heat, when answering water, obtain significantly better than oil cooled advantage.Therefore under identical mass flow and identical coolant-temperature gage situation, just can from the medium that flows through radial gap, dissipate a lot of heats by stator component to be cooled.Become big at rotor adjacent to the cooling effectiveness on the zone of this radial gap is same thus.By inference inversely, for discharge with the lubricant oil situation under the identical then essential less cooling water quality stream of heat, the input and output device that therefore is used for cooling medium just can by corresponding reduce the size setting.
Within the stator component adjacent, constitute at least one dead slot for this reason or at least one cavity is set on stator component with radial gap.This dead slot or this cavity not only are connected to be used for this cooling fluid with an input pipeline but also with an output pipeline.By these pipelines cooling fluid is imported or derives again again.In view of the wall thickness of rotor-side should keep thinly as far as possible, can be by within stator component, realizing the cooling action that improves with the water water conservancy diversion of radial gap direct neighbor.If but replace the dead slot in the stator component that the above-mentioned cavity on stator component is set, just can under same good cooling action prerequisite, realize a kind of manufacturing simple and with low cost.
In a system that forms by an internal-combustion engine and a charger-air cooler and an exhaust-gas turbocharger, both can use from the fresh water outside the system or also preferably in the application system existing water as cooling fluid.Just used the cooling water in the cooling water circulation that is present in this charger-air cooler under latter instance, its upstream at charger-air cooler is branched and forms for this reason.Should fixing stator component be exactly a housing structure of centrifugal compressor wherein, it be taken turns with respect to rotor that is with respect to the rotation compressor of an exhaust-gas turbocharger and has defined this radial gap.
As the dead slot of stator component is an integrated poured pipe that goes out in stator component, has therefore formed a simple and firm cooling unit.Replaceable mode to this is that at least one groove is set in stator component, wherein design and at least one pipe fitting as dead slot of casting in each groove.More simply yes during fabrication in addition, and a stator component has at least one corresponding, as to be poured into a mould core body, and it is removed in order to form this dead slot.
Additional advantage is so to realize: this cooling fluid was applied to cooling off indirectly the main air flow that trip under this branch in leakage flow admits working medium before the water cooling stator component adjacent with radial gap Diffuser with this with respect to the bearing housing gauge Diffuser plate of this Diffuser.Therefore also can in the zone that this is settled later, realize the cooling of effective material to turbo machine.In addition, also therefore make from the heat flow minimizing of Diffuser to the stator component that is adjacent to radial gap.
Except this water cooling, particularly preferably be and use second cooling fluid and be imported in this radial gap, wherein as preferably using air.Because this dual-cooled, this radial gap just can be so that this temperature that is subjected to the rotor of strong thermal load be further reduced.This is provided with at least one input channel and a tapping equipment to be used for second cooling fluid on radial gap.
By to ground, the input part of second cooling fluid or fully interrupt, this cooling action just simply mode be adapted to condition desired when turbo machine moves or also can be adapted to this actual temperature conditions.
Description of drawings
By an exhaust-gas turbocharger that is connected with internal-combustion engine several embodiments of the present invention have been described in the accompanying drawings.It shows:
Fig. 1 is one of exhaust-gas turbocharger of being connected with internal-combustion engine schematic representation;
Fig. 2 is the partial section by the centrifugal compressor of this exhaust-gas turbocharger;
Fig. 3 is corresponding to Fig. 2 but is second embodiment's partial section;
Fig. 4 is corresponding to Fig. 2 but is the 3rd embodiment's partial section;
Fig. 5 is corresponding to Fig. 2 but is the 4th embodiment's partial section;
Fig. 6 is corresponding to Fig. 2 but is other embodiment's partial section;
Fig. 7 is corresponding to Fig. 2 but is another embodiment's partial section;
Only understand the important element of the present invention at this and made mark for those.The flow direction of working medium is represented with arrow.
Embodiment
Fig. 1 with schematic representation represented one with an exhaust-gas turbocharger 2 that is configured to internal-combustion engine 1 cooperating of diesel engine.This exhaust-gas turbocharger comprises a centrifugal compressor 3 and an exhaust gas turbine 4, and they have a common axle 5.Exhaust gas turbine 4 is connected with internal-combustion engine 1 by an exhaust duct 7 this centrifugal compressor 3 by a pressurized air pipeline 6.In pressurized air pipeline 6 that is between centrifugal compressor 3 and internal-combustion engine 1, settle a charger-air cooler 8.This cooler 8 has a cooling water circulation 9 that has unshowned input and output structure.
Compressor housing 10 of these centrifugal compressor 3 equipments wherein, settles one to be constructed to rotor 11 compressor wheels and that be connected with axle 5.This compressor wheels 11 has a wheel hub 13 with a plurality of rotor blades 12.Structure one mobile passage 14 between wheel hub 13 and compressor housing 10.Connect one in the downstream of rotor blade 12 and on flow channel 14 and radially settle, the Diffuser 15 of blade is housed, himself feed again in the volute 16 of this centrifugal compressor 3.This compressor housing 10 comprises that mainly an air enters 17, one air of housing and discharges 18, one Diffuser plates 19 of housing and a stator component 20 (Fig. 2) that is constructed to the midfeather of one of relative this exhaust-gas turbocharger 2 bearing housing 21.
This wheel hub 13 tightens up shaft coupling 23 what turbo-side had that a back side wall 22 and one is used for axle 5.This tightens up the midfeather 20 that shaft coupling 23 is compressed engine housing 10 and takes up.Can certainly select a kind of suitable in addition compressor wheels-axle-linkage structure for use.It also is feasible similarly using a Diffuser that is unkitted blade.
Exist one to separate slot inevitably between the fixing midfeather 20 of rotation compressor wheel 11 that is its back side wall 22 and this compressor housing 10, it is constructed to radial gap 24 under a centrifugal compressor 3 situations.This slot 24 is installed in the labyrinth seal structure 25 of relative bearing housing 21 seal compression engine housings 10.In the midfeather 20 of compressor housing 10 one of structure around dead slot 26 and with the input and the output pipeline 27,28 be connected (Fig. 2,3) that are used for a cooling fluid 29.In order to realize a high as far as possible cooling action on adjacent compressor wheels 11, midfeather 20 is configured to thin as much as possible in the compressor wheels side of dead slot 26.Pour into a mould pipe fitting 30 thin-walled and that seal two ends when making this midfeather 20, its inner chamber has just formed this dead slot 26 (Fig. 2) for this reason.
This compressor wheels 11 just aspirates surrounding atmosphere as working medium 31 when exhaust-gas turbocharger 2 operations, it arrives in this volute 16 by flow channel 14 and Diffuser 15 as a main air flow 32, is further compressed and finally be applied to by pressurized air pipeline 6 super charge of this internal-combustion engine 1 that is connected with exhaust-gas turbocharger 2 herein.But, in charger-air cooler 8, realize a corresponding cooling action before this to heated working medium 31 in compression process.
From flow channel 14 to Diffuser on 15 the path, working medium 31 heated main air flow 32 in centrifugal compressor 3 also enters into radial gap 24 as leakage flow 33 at it, and therefore, this compressor wheels 11 is additionally heated.But because operating temperature is the highest in the perimeter of compressor wheels 11, so produce a huge material load especially herein.In the dead slot 26 of the midfeather of settling with this key area direct neighbor 20, imported the cooling water that branch comes out from the water cooling circulation 9 of charger-air cooler 8 as cooling fluid 29.Therefore, formed one to the indirect cooling of the leakage current 33 of existence in the slot 24 radially and also cooled off this compressor wheels 11 according to this indirectly.Wherein the branch of this cooling fluid 29 occurs in the upstream of charger-air cooler 8, thereby can realize effective cooling action with colder cooling water.After this cooling procedure, this after this heated cooling fluid 29 is sent back in this cooling water circulation 29 (Fig. 1) in the downstream of charger-air cooler 8 by output pipeline 28.Certainly not be used in existing cooling water in the system that forms by internal-combustion engine 1, charger-air cooler 8 and exhaust-gas turbocharger 2 and outside this system, import fresh water as cooling fluid 29 (not shown).
In a second embodiment, this radial gap 24 is not by a labyrinth sealing 25, but it is sealed at the seal ring 34 that tightens up arrangement between shaft coupling 23 and the midfeather 20 with one, the formation of dead slot 26 then realizes that by a core body that is cast in this midfeather 20 this core body must be eliminated (Fig. 3) again then.
According to the 3rd embodiment, groove 35 of structure in midfeather 20.The design and two pipe fittings 36 of casting in this groove 35, wherein these two pipe fittings 36 have a connecting tube 37.According to this, the inner chamber of this pipe fitting 36 has just constituted dead slot 26 (Fig. 4).Certainly in groove 35, also can only settle single pipe fitting 36.Two or more grooves 35 similarly can be set in midfeather 20, and it also can be installed in plural pipe fitting 36 (not shown).
As to the alternative of the dead slot in the midfeather 20 26 and a cavity 38 is set on this midfeather 20 in the 4th embodiment, it is sealed (Fig. 5) in that side of turbine by a cover plate 39.As dead slot 26, this cavity 38 also is connected with an input pipeline that is used for cooling fluid 29 and an output pipeline 27,28.Adopting this flexible program just can make for the necessary manufacturing of the cooling that realizes compressor wheels 11 spends is advantageously reduced.This cover plate 39 and this cavity 38 can certainly be arranged in the compressor side (not shown) of midfeather 20 with identical effect.
In this last mentioned embodiment, should be in radial gap 24 leakage flow 33 that exist indirect cooling and therefore the cooling of this compressor wheels 11 is also arranged is to realize in the mode that is substantially similar to the process that first embodiment describes.
In a further embodiment, this midfeather 20 is radially prolonged ground outward, and therefore, it has covered the main region of Diffuser 5.For this reason, this midfeather 20 has a corresponding outer shroud 43.Constitute in the inside of this outer shroud 43 one around cavity 44.This input pipeline 27 that is used for cooling fluid 29 is connected on the outer shroud 43 and is passed into its cavity 44, and this cavity 44 is connected (Fig. 6) in the other end with the cavity 26 of midfeather 20.
In this solution, this cooling fluid 29 at first is directed to the cavity 44 of outer shroud 43 from input pipeline 27 beginnings, and it is used for cooling off indirectly Diffuser 15 or Diffuser plate 19 herein.After this just take place cooling fluid 29 is imported in the dead slot 26 of midfeather 20.Wherein then carry out the indirect cooling that the front has been described to leakage flow 33.The recirculation of this cooling fluid 29 in cooling water circulation 9 realizes by output pipeline 29 equally.
Certainly, this midfeather 20 also can be positioned in (not shown) in the Diffuser plate 19 as transitting directly in the Diffuser plate 19 and being somebody's turn to do the cavity 44 that be connected with the dead slot 26 of midfeather 20 among the US 4815184.
In next embodiment, except the indirect cooling of describing so far, a direct cooling to leakage flow 33 is set.Be provided with a plurality of back side wall 22 with respect to compressor wheels 11 for tangentially being passed into input channel 40 in the radial gap 24 to be used for second cooling fluid 14 and not only to run through this bearing housing 21 but also run through this Diffuser plate 19 (Fig. 7) for this reason.This input channel 40 is connected with pressurized air pipeline 6 in the downstream of pressurized air cooling part device 8, so that the pressurized air that application has been cooled is as second cooling fluid 41 (Fig. 1).
Tangential importing by second cooling fluid 41 has realized a pure diaphragm type cooling to the whole back side wall 22 of compressor wheels 11.This second cooling fluid 41 has just substituted hot leakage flow 33, and therefore the boundary layer that forms on the back side wall 22 of compressor wheels 11 has just at first constituted by the pressurized air that has been cooled from the outset.The discharge subsequently of this second cooling fluid 41 is when installing in the partition 20 among compressor housing 10 by one, and the output unit 42 that does not further describe is finished.This have a special cooling action with the assembled scheme that directly cools off indirectly, because its effect of these two types of cooling is additional mutually and so provide the temperature of a very high compressor wheels 11 to descend.Certainly, also can use other cooling medium as second cooling fluid 41, one of them outside pressure air input also is possible (not shown).
Fig. 1 also additionally shows in the input channel 40 that is used for second cooling fluid 41 and has disposed a modulating valve 45.By this modulating valve 45, just can control the input of the suitable quantity of this second cooling fluid 41, therefore just can when the operation of exhaust-gas turbocharger 2, make cooling action be adapted on the desired condition or also be adapted on the temperature conditions of reality.Wherein this modulating valve 45 can also can be operated by a unshowned measurement and control unit with handling equally.Possible measurement parameter is exactly the temperature of this pressurized air after charger-air cooler 8 or the temperature itself that also has this midfeather 20.Certainly, the input that just can make this second cooling fluid 41 in this way not only partly but also can fully be prevented from.Only exist one to cool off indirectly that is a water cooling yet a situation is next afterwards.
Certainly, these above-mentioned cooling structure schemes can at random be made up mutually, and with whether settled a labyrinth seal structure 25 in radial gap 24 have nothing to do.Using under the midfeather cooling situation singlely, any increase of compressor thrust and in the bearing housing 21 of exhaust-gas turbocharger 2 any increase of air leakage just avoided immediately.
Reference numeral
1 internal combustion engine
2 exhaust-driven turbo-charger exhaust-gas turbo chargers
3 centrifugal compressors
4 exhaust gas turbines
5 axles
6 charge air ducts
7 discharge ducts
8 charger-air coolers
9 cooling water circulations
10 compressor housings
11 rotors, compressor wheels
12 rotor blades
13 wheel hubs
14 flow channels
15 Diffusers
16 helix structures
17 air enter housing
18 air are discharged housing
19 Diffuser plates
20 stator components, midfeather
21 bearing housinges
22 back side wall
23 tighten up shaft coupling
24 radial gap are separated slot
25 labyrinth sealings
26 dead slots
27 input pipelines
28 output pipelines
29 cooling fluids
30 pipe fittings
31 working mediums
32 main air flows
33 leakage flow
34 seal rings
35 grooves
36 pipe fittings
37 connecting tubes
38 cavitys
39 cover plates
40 input channels
41 second cooling fluids, pressurized air
42 output units
43 outer shrouds
44 cavitys
45 modulating valve
Claims (10)
1. be used for cooling off indirectly method, wherein from one of the working medium (31) of turbo machine main air flow (32), branch out a leakage current (33) and flow in the radial gap (24) at the air-flow that is formed at the radial gap between turbine rotor and stator; In the method, a cooling fluid (29) is applied on the stator component adjacent to radial gap (24) (20); It is characterized in that:
The main air flow (32) of this working medium (31) swum under the branch of leakage current (33) import in the Diffuser (15); This cooling fluid (29) is applied to the stator component (20) adjacent with this radial gap (24) at it upward before is applied to cool off indirectly this Diffuser (15) and a Diffuser plate (19); Wherein, answer water as cooling fluid (29); And, second cooling fluid (41) is imported in the radial gap (24).
2. by the method for claim 1, it is characterized in that:
Ground, the input part of this second cooling fluid (41) stopped and preferably application of air as second cooling fluid.
3. by the method for claim 1 or 2, it is characterized in that:
Import first cooling fluid (29) in the dead slot (26) that in stator component (20), constitutes or import one and go up in the cavity (38) of setting at stator component (20).
4. by the method for claim 3, it is characterized in that:
A kind of fresh water of the system outside of being made up of internal-combustion engine (1), charger-air cooler (8) and exhaust-gas turbocharger (2) is applied as first cooling fluid (29).
5. by the method for claim 3, it is characterized in that:
To in a system that forms by internal-combustion engine (1), charger-air cooler (8) and exhaust-gas turbocharger (2), be applied as first cooling fluid (29) by existing water.
6. by the method for claim 5, it is characterized in that:
To in the cooling water circulation (9) of this charger-air cooler (8), be applied as first cooling fluid (29) by existing cooling water; With the upstream branch of this cooling fluid in charger-air cooler (8).
7. be used to implement the device of the method for claim 1, wherein, a fixing stator component (20) is placed to such an extent that defined this radial gap (24) with respect to rotor (11), it is characterized in that: constituting at least one dead slot (26) within the stator component (20) or at least one cavity (38) is set on stator component (20); This dead slot (26) or cavity (38) not only are connected with an input pipeline (27) that is used for a cooling fluid (29) but also are connected with an output pipeline (28); At least one input channel (40) and an output unit (42) are set to be used for second cooling fluid (41) on radial gap (24).
8. by the device of claim 7, it is characterized in that:
In stator component (20), settle at least one closed pipe fitting (30).
9. by the device of claim 7, it is characterized in that:
At least one groove (35) is set in stator component (20); The design and at least one pipe fitting (36) of casting in each groove (35).
10. by the device of claim 7, it is characterized in that:
The stator component (20) that should fix is configured to the constituent element of the compressor housing (10) of a centrifugal compressor (3); One of its relative exhaust-gas turbocharger (2) rotation compressor wheel (11) has defined this radial gap (24).
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/CH1999/000497 WO2001029426A1 (en) | 1999-10-20 | 1999-10-20 | Method and device for the indirect cooling of a flow regime in radial slits formed between the rotors and stators of turbomachines |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1375042A CN1375042A (en) | 2002-10-16 |
| CN1191433C true CN1191433C (en) | 2005-03-02 |
Family
ID=4551727
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB998169625A Expired - Fee Related CN1191433C (en) | 1999-10-20 | 1999-10-20 | Method and device for the indirect cooling of a flow regime in radial slits formed between the rotors and stators of turbomachines |
Country Status (7)
| Country | Link |
|---|---|
| EP (1) | EP1222400B1 (en) |
| JP (1) | JP2003525377A (en) |
| KR (1) | KR100607424B1 (en) |
| CN (1) | CN1191433C (en) |
| AU (1) | AU6075899A (en) |
| DE (1) | DE59913001D1 (en) |
| WO (1) | WO2001029426A1 (en) |
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| JP2008223673A (en) * | 2007-03-14 | 2008-09-25 | Ihi Corp | Turbocharger |
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| DE102009024679B4 (en) | 2009-06-12 | 2016-04-07 | Man Diesel & Turbo Se | Compressor impeller and thus equipped centrifugal compressor |
| DE102010037356B8 (en) * | 2010-09-06 | 2014-05-22 | Kompressorenbau Bannewitz Gmbh | Verdichterradkühlung |
| JP5700999B2 (en) * | 2010-10-06 | 2015-04-15 | 三菱重工業株式会社 | Centrifugal compressor |
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| ITFI20130237A1 (en) * | 2013-10-14 | 2015-04-15 | Nuovo Pignone Srl | "SEALING CLEARANCE CONTROL IN TURBOMACHINES" |
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| DE19548852A1 (en) | 1995-12-27 | 1997-07-03 | Asea Brown Boveri | Radial compressor for exhaust gas turbo-supercharger |
| DE19652754A1 (en) | 1996-12-18 | 1998-06-25 | Asea Brown Boveri | Exhaust gas supercharger |
-
1999
- 1999-10-20 EP EP99947181A patent/EP1222400B1/en not_active Expired - Lifetime
- 1999-10-20 CN CNB998169625A patent/CN1191433C/en not_active Expired - Fee Related
- 1999-10-20 KR KR1020027003433A patent/KR100607424B1/en not_active IP Right Cessation
- 1999-10-20 DE DE59913001T patent/DE59913001D1/en not_active Expired - Fee Related
- 1999-10-20 WO PCT/CH1999/000497 patent/WO2001029426A1/en active IP Right Grant
- 1999-10-20 JP JP2001531987A patent/JP2003525377A/en active Pending
- 1999-10-20 AU AU60758/99A patent/AU6075899A/en not_active Abandoned
Also Published As
| Publication number | Publication date |
|---|---|
| EP1222400A1 (en) | 2002-07-17 |
| KR100607424B1 (en) | 2006-08-01 |
| WO2001029426A1 (en) | 2001-04-26 |
| JP2003525377A (en) | 2003-08-26 |
| EP1222400B1 (en) | 2005-12-28 |
| DE59913001D1 (en) | 2006-02-02 |
| KR20020041438A (en) | 2002-06-01 |
| CN1375042A (en) | 2002-10-16 |
| AU6075899A (en) | 2001-04-30 |
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| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C17 | Cessation of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20050302 Termination date: 20091120 |