CN1375041A - Method and device for cooling in the radial gaps formed between the rotors and stators of turbomachines - Google Patents
Method and device for cooling in the radial gaps formed between the rotors and stators of turbomachines Download PDFInfo
- Publication number
- CN1375041A CN1375041A CN99816961A CN99816961A CN1375041A CN 1375041 A CN1375041 A CN 1375041A CN 99816961 A CN99816961 A CN 99816961A CN 99816961 A CN99816961 A CN 99816961A CN 1375041 A CN1375041 A CN 1375041A
- Authority
- CN
- China
- Prior art keywords
- cooling fluid
- cooling
- radial gap
- stator component
- air
- 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.)
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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
-
- 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
-
- 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
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Supercharger (AREA)
Abstract
The aim of the invention is to provide a method for cooling the flow in the radial gaps formed between rotors and stators of turbine-type machines which is improved in terms of the cooling effect; and a simple, economical and robust device for carrying out this method. To this end, the invention provides that a stator part that is adjacent to the radial gap is subjected to the effects of a first cooling fluid and that a second, gaseous cooling fluid is guided into the radial gap. At least one recess is configured inside the stator part that is adjacent to the radial gap or at least one cavity is provided on the stator part to this end. The recess or cavity is connected to a delivery line and to a discharge line for the first cooling fluid. At least one delivery channel and a discharge device for the second cooling fluid are also located on the radial gap.
Description
Technical field
The present invention relates to as claim 1 preamble and claim 7 a kind of method and apparatus that is used for cooling off at the air-flow that is formed at the radial gap between turbine rotor and stator as described in the preamble, but be used for the air-flow of cooling especially in ' between the compressor wheels of a centrifugal compressor and housing ' radial gap.
Background technique
In order to seal the system of rotation, in the turbo machine structure, contactless sealing configuration, particularly labyrinth sealing have been adopted widely.A high friction horsepower then appears in the flow boundary layer air owing to formation in the separation slot that the fluid between rotation and static member passes through.This will cause one to the heat effect of fluid in this separation slot and according to this also with the member of heat packs round this separation slot.This high material temperature just causes the reduction in the working life of this respective members.
A centrifugal compressor that is not formed on the simple configuration of separating the sealing geometry in the slot is disclosed among the DE 19548852A1.And wherein this because frictional heat of producing on the back side wall of compressor wheels of air-flow shear layer causes one to the heating of compressor wheels with therefore cause the reduction that makes its operating life.
A cooling unit is used for having a sealing geometry on the dorsal surface of compressor wheels centrifugal compressor is disclosed in EP 0518027B1.For this reason in the additional annular chamber that constitutes between the single sealing component on the shell body wall side at centrifugal compressor.Import a kind of cold gas in this ring cavity, it has will high pressure in the outlet of a ratio piston compressor wheel.This air that is transfused to is as the washdown type cooling.Wherein, air separately also mainly radially reaches inwardly towards the other places in sealing area and flows.Therefore also intention realizes that additionally a kind of hot compressed air of the outlet to compressor wheels flows through the interception of this separation slot.
But attainable in this way cooling action is restricted based on a plurality of factors.For example, the drum of this air send and will cause the raising of pressure and thrust, so bearing load increases.In addition, the temperature of this stand-by air has also been played the part of a factor that plays restriction.Especially under the compressor wheels of fast operation and high pressure ratio, as they in the turbocharger configuration in modern times general exist like that, it is enough so such type of cooling to occur.
Except this direct cooling, also in DE 19652754A1, disclose a kind of to the back side wall of compressor wheels or to this indirect cooling scheme by the mobile medium of separation slot.For this reason, on this housing structure or on back side wall, settle and constitute with this back side wall an input and a dispensing device that is connected with the lubricating oil system of turbosupercharger be set in this housing structure that separates slot.Used this as cooling medium and be used to the oil of bearing lubrication, therefore, the lubrication oil circulation of this turbosupercharger is by tap.The shortcoming of this cooling is higher relatively oily demand and the additional heat that distributes of the device that is cooled.This just causes the bigger structural volume of cooler.In addition, the explosion risk that under the failure condition of respective members damage, has a kind of increase.Similarly as described in the direct cooling situation this during in cooling indirectly attainable cooling action also be restricted, to this, except the temperature of available cooling fluid in practice, this available small construction volume should be confirmed to be reason especially.
Summary of the invention
The present invention attempts all these defectives are avoided.Task of the present invention is, creates a method of improving its cooling effect, and it is used for cooling off the air-flow being formed at the radial gap between turbine rotor and stator.A kind of device of implementing described method simply, cheaply with firm being used to can also be provided in addition.
By the invention requirement, this task so realizes: on a method basis that limits according to preamble section before the claim 1, not only first cooling fluid is applied on the stator component adjacent to this radial gap, and second gaseous state cooling fluid imports in this radial gap.
Since use first cooling fluid be used for cooling off indirectly this turbo machine working medium the part air-flow that enters radial gap and additionally use second cooling fluid and be used for directly cooling off this part air-flow and just can realize obvious improved cooling action and improved cooling effectiveness.Therefore thisly at first just can realize to the dual-cooled of slot radially that this further temperature that is subjected to strong thermal load rotor descends and also drop on the temperature range that can not reach always with traditional cooling structure scheme.
For this reason, at least one dead slot of cage structure or at least one cavity is set on stator component within this is adjacent to the stator component of radial gap.This dead slot or cavity are not only to be connected with an input pipeline that is used for this first cooling fluid but also with a discharge conduit.Settle at least one input channel and a discharger to be used for second cooling fluid on this external radial gap.
Particularly preferred mode make water as first cooling fluid, and application of air is as second cooling fluid.
Glassware for drinking water has density and the about twice big specific heat higher slightly than known lubricant oil.Because should be proportional to the product of density and specific heat by the heat flow that cooling medium row looses, so when answering water, just obtain an obvious advantage better than oil cooling as first cooling fluid.Be pulled away more heat by the stator component that will be cooled the medium of this radial gap of under identical mass flow and identical coolant-temperature gage situation, just can flowing through according to this from that.Therefore the cooling effect with on the radial gap adjacent domain to rotor is bigger equally.By reverse inference, in order to discharge the then cooling water of a less mass flow of needs for lubricant oil of identical heat, according to this, the input and output device that is used for this cooling fluid can be corresponding less with regard to size.
According to this rotation wall thickness that should be provided with for a short time as far as possible, just can pass through within stator component to the radially cooling action of the water guiding realization improvement of the direct neighbor of slot.If but replace in the stator component dead slot and on stator component during the described cavity of structure, just can the easier manufacturing cheaper of realization under same good cooling action prerequisite with cost.
Application of air has proved when especially advantage being arranged as second cooling fluid, because it is not only around in the environment but also can both be with enough quantity in turbo machine itself, enough pressure and suitable low temperature provide use.
In a system that forms by an internal-combustion engine, a charger-air cooler and an exhaust-gas turbocharger, both can use the fresh water that outside system, provides or preferably the application system existing water as first cooling fluid.What use in the situation of back is the cooling water that exists in the circulation of one of charger-air cooler cooling water, and its upstream end at charger-air cooler is branched formation.Wherein, this fixing stator component is the housing member of a centrifugal compressor, and it has defined this radial gap with respect to the rotary compressor wheel of a rotor that is an exhaust-gas turbocharger.
If use oil during as first cooling fluid on the contrary, oil is branch from existing lubricating oil system the bearing housing of turbo machine preferably just.Thereby just can make a simple relatively device with low cost in this way.If when first cooling fluid related to a gaseous medium, then this medium both can be used for direct cooling and also can be used for indirect cooling.
Using helium or can realize good especially cooling action when for example the gas formed of liquid nitrogen, carbon tetrachloride, benzene nitride is as first and/or second cooling fluid by cryogen.
Description of drawings
By an exhaust-gas turbocharger that is connected with an internal-combustion engine one embodiment of the present of invention are described in the accompanying drawings.It shows:
Fig. 1 is a rough schematic view of this exhaust-gas turbocharger that is connected with internal-combustion engine;
Fig. 2 is the partial section by the centrifugal compressor of this exhaust-gas turbocharger;
Only those are understood the important element of the present invention and done expression.The flow direction of working medium is indicated with arrow.
Embodiment
Fig. 1 with sketch describe mode shown one with an exhaust-gas turbocharger 1 that is configured to internal-combustion engine 1 collaborative work of diesel engine.This pressurized machine 2 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 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 charger-air cooler 8 has one and has a unshowned cooling water circulation 9 that inputs or outputs structure.
This centrifugal compressor 3 is equipped with a compressor housing 10, wherein settles a rotor 11 that is constructed to compressor wheels and is connected with axle 5.This compressor wheels 11 has a wheel hub 13 that is loaded with a plurality of rotor blades 12.Between wheel hub 13 and compressor housing 10, constitute a mobile passage 14.The Diffuser 15 of blade that connected the dress upwards settled in a footpath in the downstream of rotor blade 12 on flow channel 14 itself feeds again in the helix structure 16 of this centrifugal compressor 3.This compressor housing 10 comprises that mainly air imports the stator component 20 (Fig. 2) that 17, one air of housing are discharged partition among 18, one Diffuser plates 19 of housing and the bearing housing 21 that is constructed to relative exhaust-gas turbocharger 2.
This wheel hub 13 has a back side wall 22 and one in turbo-side and tightens up shaft coupling 23 and be used for axle 5.This tightens up the midfeather 20 that 23 on shaft coupling is compressed engine housing 10 and is installed in.Natch, also can select a suitable in addition compressor wheels-axle-linkage structure.Similarly, using one, to be unkitted vaned Diffuser also be possible.
Exist one to separate slot 24 inevitably between the partition 20 among the compressor housing 10 of rotation compressor wheel 1 that is its back side wall 22 and this fixed in position, it is constructed to radial gap 24 in a centrifugal compressor 3.One of these radial gap 24 usefulness are tightening up the seal ring 34 settled between shaft coupling 23 and the midfeather 20 with respect to bearing housing 21 sealings.Natch, this sealing also can realize (not shown) by a labyrinth seal structure of settling in radial gap 24.In the midfeather 20 of compressor housing 10 one of structure around dead slot 26 and not only be connected to be used for first cooling fluid 29 with an input structure but also with an exhaust structure 27,28.In order to realize high as far as possible cooling action under adjacent to compressor wheels 11 situations, this midfeather 20 is constructed to thin walled structures as much as possible in the compressor side of dead slot 26.For this reason, inject a suitable core when making this midfeather 20, it must be eliminated again then.Natch, also can inject a tubular construction thin-walled and that seal two ends in this midfeather 20, its inner chamber just constitutes this dead slot 26 (not shown) then.
When exhaust-gas turbocharger 2 operations, this compressor wheels 11 just aspirates the surrounding atmosphere as working medium 31, it arrives in this helix structure 16 by flow channel 14 and Diffuser 15 as main air flow 32, further is compressed therein and the supercharging that is used to this internal-combustion engine that is connected with exhaust-gas turbocharger 2 at last by pressurized air pipeline 6.But the suitable cooling action to heated working medium 31 in compression process takes place in charger-air cooler 8 before this.
At it from flow channel 14 to Diffuser on 15 the distance, this working medium 31 in centrifugal compressor 3 heated main air flow 32 also as 33 pairs of leakage flow radially slot 24 exert one's influence, therefore, this compressor wheels 11 is additionally heated.But, therefore produce a very big material load especially there because the operating temperature in the perimeter of compressor wheels 11 is the highest.In this dead slot 26 that key area direct neighbor is settled therewith, then be imported into the circulate cooling water of 9 diverted flow of cooling water as cooling fluid 29 from charger-air cooler 8.According to this, just produced one to the leakage flow 33 that in radial gap 24, exists and then to the indirect cooling of compressor wheels 11.Simultaneously, the branch of cooling fluid 29 occurs in the upstream of this charger-air cooler 8, thereby can realize effective cooling action with relative colder cooling water.After this cooling procedure, this this moment, heated cooling fluid 29 was sent back in the cooling water circulation 9 (Fig. 1) in the downstream of charger-air cooler 8 by discharge conduit 28.Certainly, can not be used in existing cooling water in the system that internal-combustion engine 1 is charger-air cooler 8 and exhaust-gas turbocharger 2 and from the system of outside input fresh water as cooling fluid 29 (not shown).
A direct cooling to leakage flow 33 can be set except indirect cooling described so far.For this reason, be provided with input channel 40 that a plurality of back side wall 22 with respect to compressor wheels 11 tangentially feed this radial gap 24, not only run through this bearing housing 21 but also connect this Diffuser plate 19 (Fig. 2) to be used for second cooling fluid 41.This input channel 40 is connected with pressurized air pipeline 6 in the downstream of charger-air cooler 8, and therefore, the pressurized air that has been cooled is used as second cooling fluid 41 (Fig. 1).Obviously, this second cooling fluid 41 also can be directed to (not shown) in this radial gap on other position.
Just realized a pure diaphragm type cooling by tangentially importing this second cooling fluid 41 to the whole back side wall 22 of compressor wheels 11.41 of second cooling fluids have replaced hot leakage flow 33, and therefore the boundary layer that forms on the back side wall 22 of compressor wheels 11 has at first constituted by the pressurized air that has been cooled from the outset.The discharger 42 that the discharge subsequently of this second cooling fluid 41 is provided with in the wall 20 between compressor housing 10 by one, is not further described is realized.This have special cooling effect by cooling off the combination that forms indirectly and directly, because these two cooling schemes have replenished their effect mutually and thereby realized that temperature very big in compressor wheels 11 descends.
Certainly, also can use other cooling medium for example helium or the gas formed by cryogen (as liquid nitrogen, carbon tetrachloride, nitrogenize benzene etc.) as first and second cooling fluids 29,41.
If use oil, so just it can be imported or presses optimal way from the outside and can from existing lubricating oil system the bearing housing 21 of exhaust-gas turbocharger 2, branch supply with (not shown) as first cooling fluid 29.Just can realize this same suitable cooling fluid of input simple relatively and therefore with low cost in this way.56 pressurized air pipelines of Ref. No. table 1 internal-combustion engine 2 exhaust-gas turbocharger 3 centrifugal compressors, 4 exhaust gas turbines, 7 exhaust pipings, 8 charger-air coolers, 9 cooling waters, 10 compressor housings, 11 rotors that circulate, compressor wheels 12 rotor blades 13 wheel hubs 14 flow channels 15 Diffusers 16 helix structures 17 air enter housing 18 air and discharge housing 19 Diffuser plates 20 stator components, midfeather 21 bearing housinges 22 back side wall 23 tighten up shaft coupling 24 radial gap, separate slot 25 labyrinth sealings 26 dead slots 27 input pipelines 28 discharge conduits 29 first cooling fluids 31 working mediums 32 main air flows 33 leakage flow 34 seal rings 40 input channels 41 second cooling fluids 42 dischargers
Claims (10)
1. be used for cooling off the method for the air-flow of the radial gap between rotor that is formed at turbo machine and stator, it is characterized in that:
First cooling fluid (29) is applied on the stator component adjacent to this radial gap (24) (20); And second cooling fluid (41) of gaseous state imported in this radial gap (24).
2. by the method for claim 1, it is characterized in that:
Import to this first cooling fluid (29) in the dead slot (26) that in stator component (20), constitutes or import to one and go up in the cavity of arranging at stator component (20).
3. by the method for claim 1 or 2, it is characterized in that:
Water is used as first cooling fluid (29).
4. by the method for claim 3, it is characterized in that:
Fresh water outside the system that will be made up of an internal-combustion engine (1), a charger-air cooler (8) and an exhaust-gas turbocharger (2) is used as first cooling fluid (29).
5. by the method for claim 3, it is characterized in that:
To in a system that forms by an internal-combustion engine (1), a charger-air cooler (8) and an exhaust-gas turbocharger (2), be used as first cooling fluid (29) by existing water.
6. by the method for claim 5, it is characterized in that:
To in a cooling water circulation (9) of charger-air cooler (8), be used as first cooling fluid (29) by existing water; And be that cooling fluid 29 comes out in the upstream branch of charger-air cooler (8) with the latter.
7. by the method for claim 1, it is characterized in that:
With oil, helium or the gas formed by cryogen as first cooling fluid (29).
8. by the method for claim 1, it is characterized in that:
The gas of forming with air, helium or by cryogen is as the second gaseous state cooling fluid (41).
9. be used to implement the device according to the method for claim, wherein, the stator component of a fixed in position (20) has been placed with respect to rotor (1) gauge this radial gap (24); It is characterized in that:
A) at least one dead slot (26) is being set within the stator component (20) or at least one cavity is being set on stator component (20) and this dead slot (26) or this cavity not only are connected with an input pipeline (27) that is used for this first cooling fluid (29) but also are connected with a discharge conduit (28); With
B) at least one input channel (40) and a discharger (42) that is used for this second cooling fluid (41) settled radial gap (24).
10. by the device of claim 9, it is characterized in that:
The stator component (20) that should fix is constructed to the constituent element of one of centrifugal compressor (3) compressor housing (10), and this part has been taken turns (11) gauge this radial gap (24) with respect to a rotation compressor of an exhaust-gas turbocharger (2).
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/CH1999/000496 WO2001029425A1 (en) | 1999-10-20 | 1999-10-20 | Method and device for cooling the flow in the radial gaps formed between rotors and stators of turbine-type machines |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1375041A true CN1375041A (en) | 2002-10-16 |
| CN1258648C CN1258648C (en) | 2006-06-07 |
Family
ID=4551726
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB998169617A Expired - Fee Related CN1258648C (en) | 1999-10-20 | 1999-10-20 | Method and device for cooling in the radial gaps formed between the rotors and stators of turbomachines |
Country Status (7)
| Country | Link |
|---|---|
| EP (1) | EP1222399B1 (en) |
| JP (1) | JP2003515690A (en) |
| KR (1) | KR100637643B1 (en) |
| CN (1) | CN1258648C (en) |
| AU (1) | AU6075799A (en) |
| DE (1) | DE59906615D1 (en) |
| WO (1) | WO2001029425A1 (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104595246A (en) * | 2015-01-05 | 2015-05-06 | 珠海格力电器股份有限公司 | Centrifugal compressor with recooling structure |
| CN104595247A (en) * | 2015-01-05 | 2015-05-06 | 珠海格力电器股份有限公司 | Centrifugal compressor with recooling structure |
| CN105143636A (en) * | 2013-02-21 | 2015-12-09 | 丰田自动车株式会社 | Cooling device of supercharger of internal combustion engine comprising blow-by gas circulation device |
| CN106286338A (en) * | 2015-06-02 | 2017-01-04 | 上海优耐特斯压缩机有限公司 | The structure that the centrifugal compressor leakage air using high-speed electric expreess locomotive is cooled down |
| CN111720331A (en) * | 2020-05-22 | 2020-09-29 | 洛阳瑞华新能源技术发展有限公司 | Single-stage centrifugal pump with liquid collecting and draining flow channel and flow dividing partition plate having at least 2 liquid draining ports |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102005018771B4 (en) * | 2005-04-22 | 2015-06-18 | Man Diesel & Turbo Se | Internal combustion engine |
| DE102007001487B4 (en) * | 2007-01-10 | 2015-07-16 | Caterpillar Energy Solutions Gmbh | Method and device for compressor wheel cooling of a compressor |
| EP2067999A1 (en) * | 2007-12-06 | 2009-06-10 | Napier Turbochargers Limited | Liquid cooled turbocharger impeller and method for cooling an impeller |
| EP2090788A1 (en) | 2008-02-14 | 2009-08-19 | Napier Turbochargers Limited | Impeller and turbocharger |
Family Cites Families (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB191114702A (en) * | 1910-06-22 | 1912-07-22 | Hugo Junkers | Improvements in or relating to Centrifugal or Turbo-compressors. |
| US2384251A (en) * | 1943-01-14 | 1945-09-04 | Wright Aeronautical Corp | Liquid cooled supercharger |
| DE968742C (en) * | 1944-09-22 | 1958-03-27 | Daimler Benz Ag | Multi-stage radial blower, preferably loading blower for aircraft engines |
| US3966351A (en) * | 1974-05-15 | 1976-06-29 | Robert Stanley Sproule | Drag reduction system in shrouded turbo machine |
| JPS61112737A (en) * | 1984-11-08 | 1986-05-30 | Mitsubishi Heavy Ind Ltd | Supercharger |
| JPS6434435A (en) * | 1987-07-06 | 1989-02-03 | Agency Ind Science Techn | Temperature sensitive gel and manufacture thereof |
| JPH0333431A (en) * | 1989-06-30 | 1991-02-13 | Hitachi Ltd | Supercharger for internal combustion engine |
| JP2934530B2 (en) * | 1991-06-14 | 1999-08-16 | 三菱重工業株式会社 | Centrifugal compressor |
| JP2924363B2 (en) * | 1991-09-18 | 1999-07-26 | 石川島播磨重工業株式会社 | Water-cooled bearing housing structure for turbocharger |
| JP2918773B2 (en) * | 1993-11-08 | 1999-07-12 | 株式会社日立製作所 | Centrifugal compressor |
| JPH07208189A (en) * | 1994-01-10 | 1995-08-08 | Hino Motors Ltd | Supercharger cooling device of engine |
| DE19548852A1 (en) | 1995-12-27 | 1997-07-03 | Asea Brown Boveri | Radial compressor for exhaust gas turbo-supercharger |
| JP3606293B2 (en) * | 1996-02-14 | 2005-01-05 | 石川島播磨重工業株式会社 | Exhaust turbine turbocharger |
| DE19652754A1 (en) | 1996-12-18 | 1998-06-25 | Asea Brown Boveri | Exhaust gas supercharger |
-
1999
- 1999-10-20 EP EP99947180A patent/EP1222399B1/en not_active Expired - Lifetime
- 1999-10-20 JP JP2001531986A patent/JP2003515690A/en active Pending
- 1999-10-20 CN CNB998169617A patent/CN1258648C/en not_active Expired - Fee Related
- 1999-10-20 AU AU60757/99A patent/AU6075799A/en not_active Abandoned
- 1999-10-20 KR KR1020027003417A patent/KR100637643B1/en not_active IP Right Cessation
- 1999-10-20 WO PCT/CH1999/000496 patent/WO2001029425A1/en active IP Right Grant
- 1999-10-20 DE DE59906615T patent/DE59906615D1/en not_active Expired - Fee Related
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105143636A (en) * | 2013-02-21 | 2015-12-09 | 丰田自动车株式会社 | Cooling device of supercharger of internal combustion engine comprising blow-by gas circulation device |
| CN105143636B (en) * | 2013-02-21 | 2018-01-09 | 丰田自动车株式会社 | Possesses the cooling device of the booster of the internal combustion engine of blow-by gas circulating device |
| CN104595246A (en) * | 2015-01-05 | 2015-05-06 | 珠海格力电器股份有限公司 | Centrifugal compressor with recooling structure |
| CN104595247A (en) * | 2015-01-05 | 2015-05-06 | 珠海格力电器股份有限公司 | Centrifugal compressor with recooling structure |
| CN106286338A (en) * | 2015-06-02 | 2017-01-04 | 上海优耐特斯压缩机有限公司 | The structure that the centrifugal compressor leakage air using high-speed electric expreess locomotive is cooled down |
| CN111720331A (en) * | 2020-05-22 | 2020-09-29 | 洛阳瑞华新能源技术发展有限公司 | Single-stage centrifugal pump with liquid collecting and draining flow channel and flow dividing partition plate having at least 2 liquid draining ports |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2001029425A1 (en) | 2001-04-26 |
| AU6075799A (en) | 2001-04-30 |
| KR100637643B1 (en) | 2006-10-23 |
| KR20020041437A (en) | 2002-06-01 |
| DE59906615D1 (en) | 2003-09-18 |
| EP1222399A1 (en) | 2002-07-17 |
| EP1222399B1 (en) | 2003-08-13 |
| CN1258648C (en) | 2006-06-07 |
| JP2003515690A (en) | 2003-05-07 |
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