CN101631940A - Compressor for turbocharger and cooling method thereof - Google Patents
Compressor for turbocharger and cooling method thereof Download PDFInfo
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- CN101631940A CN101631940A CN200780045671A CN200780045671A CN101631940A CN 101631940 A CN101631940 A CN 101631940A CN 200780045671 A CN200780045671 A CN 200780045671A CN 200780045671 A CN200780045671 A CN 200780045671A CN 101631940 A CN101631940 A CN 101631940A
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- 238000001816 cooling Methods 0.000 title claims description 29
- 239000012809 cooling fluid Substances 0.000 claims abstract description 39
- 239000011248 coating agent Substances 0.000 claims abstract description 31
- 238000000576 coating method Methods 0.000 claims abstract description 31
- 239000012530 fluid Substances 0.000 claims description 12
- PNEYBMLMFCGWSK-UHFFFAOYSA-N Alumina Chemical compound [O-2].[O-2].[O-2].[Al+3].[Al+3] PNEYBMLMFCGWSK-UHFFFAOYSA-N 0.000 claims description 9
- 238000005524 ceramic coating Methods 0.000 claims description 7
- 230000008676 import Effects 0.000 claims description 6
- RVTZCBVAJQQJTK-UHFFFAOYSA-N oxygen(2-);zirconium(4+) Chemical compound [O-2].[O-2].[Zr+4] RVTZCBVAJQQJTK-UHFFFAOYSA-N 0.000 claims description 4
- 229910001928 zirconium oxide Inorganic materials 0.000 claims description 4
- 239000007787 solid Substances 0.000 claims description 2
- 229910052727 yttrium Inorganic materials 0.000 claims description 2
- VWQVUPCCIRVNHF-UHFFFAOYSA-N yttrium atom Chemical compound [Y] VWQVUPCCIRVNHF-UHFFFAOYSA-N 0.000 claims description 2
- 238000005507 spraying Methods 0.000 claims 1
- 230000005540 biological transmission Effects 0.000 description 10
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 10
- 230000006835 compression Effects 0.000 description 8
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- 238000002485 combustion reaction Methods 0.000 description 6
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- 238000010438 heat treatment Methods 0.000 description 3
- 238000009826 distribution Methods 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 239000012720 thermal barrier coating Substances 0.000 description 2
- 238000007751 thermal spraying Methods 0.000 description 2
- 230000005068 transpiration Effects 0.000 description 2
- 229910000838 Al alloy Inorganic materials 0.000 description 1
- 230000001133 acceleration Effects 0.000 description 1
- 230000009471 action Effects 0.000 description 1
- 230000004888 barrier function Effects 0.000 description 1
- 230000019771 cognition Effects 0.000 description 1
- 238000009795 derivation Methods 0.000 description 1
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- 230000002035 prolonged effect Effects 0.000 description 1
- 239000011253 protective coating Substances 0.000 description 1
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- 238000013396 workstream Methods 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
- F02C6/04—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output
- F02C6/10—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output supplying working fluid to a user, e.g. a chemical process, which returns working fluid to a turbine of the plant
- F02C6/12—Turbochargers, i.e. plants for augmenting mechanical power output of internal-combustion piston engines by increase of charge pressure
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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
- F04D29/02—Selection of particular materials
- F04D29/023—Selection of particular materials especially adapted for elastic fluid pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
- F01D25/08—Cooling; Heating; Heat-insulation
- F01D25/14—Casings modified therefor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
- F01D5/02—Blade-carrying members, e.g. rotors
- F01D5/04—Blade-carrying members, e.g. rotors for radial-flow machines or engines
- F01D5/043—Blade-carrying members, e.g. rotors for radial-flow machines or engines of the axial inlet- radial outlet, or vice versa, type
- F01D5/046—Heating, heat insulation or cooling means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
- F01D5/12—Blades
- F01D5/28—Selecting particular materials; Particular measures relating thereto; Measures against erosion or corrosion
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
- F01D5/12—Blades
- F01D5/28—Selecting particular materials; Particular measures relating thereto; Measures against erosion or corrosion
- F01D5/288—Protective coatings for blades
-
- 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
- F04D29/083—Sealings especially adapted for elastic fluid pumps
-
- 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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- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2220/00—Application
- F05D2220/40—Application in turbochargers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2260/00—Function
- F05D2260/20—Heat transfer, e.g. cooling
- F05D2260/232—Heat transfer, e.g. cooling characterized by the cooling medium
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2300/00—Materials; Properties thereof
- F05D2300/20—Oxide or non-oxide ceramics
- F05D2300/21—Oxide ceramics
- F05D2300/2112—Aluminium oxides
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2300/00—Materials; Properties thereof
- F05D2300/20—Oxide or non-oxide ceramics
- F05D2300/21—Oxide ceramics
- F05D2300/2118—Zirconium oxides
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Materials Engineering (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Chemical Kinetics & Catalysis (AREA)
- General Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
A compressor, in particular a centrifugal compressor, for a turbocharger having a compressor wheel (1), which is rotatably accommodated in a compressor housing, wherein a part (6) of the compressor housing adjacent to the compressor wheel is flowed through by a cooling fluid. The compressor wheel has at least in part a coating (2) that reduces heat input.
Description
[technical field]
The present invention relates to according to claim 1 compressor and the cooling means thereof that is used for turbocharger as described in the preamble.
[technical background]
In turbocharger, working medium is air especially, is compressed to burn in internal-combustion engine by compressor.This compressor is connected with turbo machine, and turbo machine drives by the exhaust of internal-combustion engine.
Compressor impeller by motion and hold the compressor housing of this compressor impeller or working medium between the frictional heat that produces, but at first produce high temperature by the compressor impeller outlet of the compression of working medium own, especially export at compressor impeller.Therefore can for example under a compression ratio of four kinds of gases, be heated to above 200 ℃ from room temperature.
This high temperature shows the huge thermal stress of compressor, especially on compressor impeller, compressor impeller preferably adopt light metal for example aluminum alloy make, to keep less rotating mass and the centrifugal force that therefore occurs, effect of unclamping (Entfestigung) and the life-span of having reduced turbocharger thus can have been caused.Simultaneously, raise (gas) of the firing chamber reduced internal-combustion engine of the temperature of working medium is filled with and has been worsened efficient.
Therefore, EP 0 518 026 A1 teachings a kind of impact type air cooling (Prallluftkuehlung) of compressor impeller rear side, cool air is imported in the radial clearance (Radialspalt) between compressor impeller and the compressor housing therein, and at that impact (beaufschlaegt) compressor impeller rear side.Except this direct cooling, WO 01/29426 Al teaching a kind of indirect cooling, therein, cooling fluid flows by the chamber on the part of the close compressor impeller of compressor housing, and the parts by leakage flow in the radial clearance and compressor housing import the heat of compressor impeller in the cooling fluid into thus.
DE 20 2,005 019 320 U1 relate to a kind of turbo machine that impacts with high-temperature exhaust air, and it suffers higher temperature usually than compressor, thus teaching adopt blade (Schaufel) with thermal-protective coating.
Two teachings can be so that reduce in each comfortable limited range of the temperature that occurs on the blade.In addition, known EP 0,518 026 A1 and the cooling of WO 01/29426 A1 need be supplied with a large amount of cooling fluids, can disperse a large amount of heats.
[summary of the invention]
With reference to WO 01/29426 A1, task of the present invention is, is used for the compressor of turbocharger, therein, and the temperature that occurs on the compressor impeller when using more a spot of cooling fluid can reduce the compression work medium.In order to solve this technical problem, further be configured according to the compressor of claim 1 preamble characteristic by claim 1.Claim 12 has proposed to cool off the method that this compressor makes it to receive protection.
According to the present invention, the compressor that is used for turbocharger comprises compressor impeller, and compressor impeller rotatably is accommodated in the compressor housing.Preferably, it relates to centrifugal compressor, and in centrifugal compressor, axially the working medium that sucks outwards quickens by the blade radial of compressor impeller, thereafter its speed is converted into pressure.In addition diffuser can be installed.
The parts of the close compressor impeller of compressor housing, it is preferably separated by radial clearance and compressor impeller, and be arranged on compressor impeller and main flow working fluid away from a side, the fluid that is cooled flows through.The cooling that cooling fluid is direct or indirect towards the rear side of the compressor impeller of these parts, therefrom drawn heat.
Teaching of the present invention, compressor impeller are provided with the coating that reduces the heat input in addition at least in part.Reduced substantially thus to be compressed in the compressor impeller and the heat input of the working medium of intensification thus, made this more a spot of cooling fluid give out enough heats, guaranteed that the temperature that occurs in the compressor impeller does not exceed the peak of permission.
The less cool stream scale of construction advantageously only need have than minor diameter and/or than the fluid line of minimum velocity.Therefore can make lessly according to compressor of the present invention, because input pipeline in the compressor housing and output pipeline and cooling fluid pipeline can design lessly.Can reduce the total amount of circuit cooling fluid, also just can use less cooling fluid bank.In addition, also can reduce the size of heat exchanger, cooling fluid will import into the surrounding environment once more from the heat that compressor transfers out in this heat exchanger.
Smaller volume flow (Volumenstrom) only needs less power that cooling fluid is circulated and has also improved the efficient of the motor that is equipped with compressor involved in the present invention, and this efficient is relevant with the cool stream scale of construction of use.The life-span that this cool stream scale of construction needs less cooling fluid pipeline and improved compressor.Long under lower flow condition in aforesaid favourable heat exchanger stops also to be implemented in and discharge the heat that obtains when having used less heat exchanger from compressor.This heat has under any circumstance reduced by the coating that reduces the heat input.
Therefore can realize having the smaller volume flow in cooling fluid according in the compressor of the present invention, the temperature of compressor impeller remains in the low scope and has prolonged the compressor life-span thus.On the contrary, the coating that reduces the heat input has only reduced the heat of input, and fluid sheds thereby heat can be cooled.Coating can be made and/or can make than low-intensity by the material of economy, and this advantageously reduces the centrifugal force on rotating mass and the reduction compressor impeller.
Heat input certain in compressor impeller is favourable, thereby because has reduced the temperature and the volumetric efficiency (Fuellungsgrad) that has improved internal-combustion engine of compressed working medium thus.By coating and the suitable adjustment of chilling room of cooling fluid on the one hand in addition that reduces on the one hand the heat input, realized helping the efficient of internal-combustion engine and to the optimization compression between the favourable heat input of compressor life-span.
In a preferred embodiment, compressor impeller comprises compressor wheel hub (Verdichternabe) and at least one compressor blade (Verdichterschaufel).Compressor wheel hub and/or compressor blade can partly be provided with the coating that reduces the heat input separately.Wherein the coating that the minimizing heat is imported in a special preferred embodiment extends to impeller outlet from the inlet edge of partial blade group (Verdichterbeschaufelung).Because the major component of the heat that occurs in the compression, it is overheated and must be shed for fear of compressor impeller, directly especially produces near impeller outlet in compressor blade group zone.In addition, cooling fluid is the zone of cooling compressor impeller especially, owing to exist high rotating speed can simplify cooling, especially simplifies the inflow and the outflow of the cooling fluid of direct impact compress machine impeller herein like this.
In an optional embodiment, the wheel hub of the vane group of whole rotation and the compressor impeller that contacts with working medium is provided with the coating that reduces the heat input, can simplify the production of coating, and this can for example pass through dipping bath (Tauchbaeder) acquisition.In addition, can avoid the localized heat peak value of coating area not and be implemented in that even temperature distributes in the compressor impeller.
In a preferred embodiment of the invention, however the coating that reduces the heat input only be configured in the face of from the surface of the compressor impeller of the main flow of the compression work stream of compressor.The heat that can reduce on the one hand the main flow that derives from compressed working medium thus enters and therefore advantageously reduces the cool stream scale of construction with aforementioned advantages.One side does not hinder the heat of compressor impeller to be distributed to the parts of close compressor housing in addition.Same advantage also has, in the face of thereby the rear side of the compressor impeller of the parts of compressor housing directly is cooled with the cooling fluid impact, also have by the heat conduction in the medium in the gap of separately compressor impeller and compressor housing with from the medium of the parts of these compressor housings and the cooling fluid that flows through and realize cooling indirectly.The coating that reduces the heat input in a preferred embodiment of the invention comprises ceramic coating, and this ceramic coating especially is fit to be applied in the compressor according to its hardness and thermal transmission coefficient.Carry out ceramic coating by thermal spraying, this has allowed to have the coating of the part area of the production of Economy of the uniform coating thick than thin-walled and the vane group especially selected.
Ceramic coating has been proved to be very suitable, and it comprises aluminium oxide and/or zirconium oxide, especially the solid zirconium oxide (Yttrium-stabilisiertes Zirkoniumdioxid) of yttrium.Usually separately as " thermal barriercoating " or " heat barrier coating " thermal barrier coating and known coating can be employed, this coating can reduce heat to be imported in the compressor impeller, equally especially has low thermal transmission coefficient.The technology contents of relevant therewith EP0 211 032 B1 also big volume description and comprise this coating fully.
Chamber in the engine housing of chilled fluid flow overcompression in a preferred embodiment of the invention and therefore indirect cooling compressor impeller.Because exhale the heat of the parts of close compressor impeller on the compressor housing thus.In the gap between compressor impeller and compressor housing, especially the medium in radial clearance is cooled thus, and this cooling fluid has cooled off the rear side that adjoins of compressor impeller.
Especially the leakage flow that can be entered the working medium between compressor impeller and compressor housing of the radial clearance between compressor impeller and compressor housing is passed through.Not cooling, compressor impeller will be subjected to the impact of the working medium of heat to its front end and rear side.In foundation compressor of the present invention, the heat of self importing from leakage flow is discharged to cooling fluid by the parts towards radial clearance in the compressor housing on the one hand, and the heat of compressor impeller is discharged in the leakage flow of cooling off in this way and by leakage flow and is discharged to cooling fluid on the one hand in addition.Here particularly advantageously, the coating that reduces the heat input only is set at towards the front end of the compressor impeller of working medium main flow, and especially the inlet edge from the partial blade group extends to impeller outlet, this is because the heat transfer in the medium of radial clearance and in cooling fluid does not reduce, and therefore cooling is not impacted.
Chamber can extend in the circumferential direction of the parts of compressor housing, has one or more inputs, output pipe.Colder cooling fluid is imported into a plurality of positions that distribute on the circumference, and the cooling fluid of heat is derived a plurality of positions that distribute on the circumference, thereby can average effective ground cooling compressor impeller.For this purpose, chamber can have a plurality of parallel channels between input, output pipe, to absorb heat as much as possible.In addition, chamber has the geometrical shape of eddy current rising (turbulenzerhoehend), to improve the eddy current and the thermal absorption thereof of chilled fluid flow.
As described indirect cooling replenish or select, cooling fluid can import in the radial clearance, advantageously meets with the rear side of compressor impeller herein, can directly cool off thereby absorb heat from it.If the leakage flow of working medium enters in the radial clearance, the cooling fluid that imports in the radial clearance is identical with working medium so, and wherein advantageously cooling fluid under high pressure is imported into and impacts the rear side of (prallen) compressor impeller.
After the cooling fluid of compressor impeller rear side absorbs heat, the cooling fluid leakage flow that flow in the main flow of working fluid and reduce not expect in the gap between compressor impeller and the compressor housing advantageously.This has further reduced the heat of deriving and the cool stream scale of construction that needs thus, because compressor impeller no longer or is only impacted by hot workflow slightly at rear side.
Have two cooling principles to be employed jointly, indirectly the cooling fluid of the cooling fluid of cooling and directly cooling is identical, cool air for example, its preferably extraction from the charger-air cooler (Ladeluftkuehler) of turbocharger.The simplification that this is favourable the input and output pipeline of cooling fluid.Equally also can use different cool stream.For example the water that preferably extracts from the cold circulation of internal-combustion engine during air flows into the rear side of compressor impeller by an independent input pipeline, can flow through chamber and indirect thus cooling compressor impeller in the compressor housing.Can realize thus, under various conditions, that is to say the inflow of one side compressor impeller and replace only separately fluid by the thermal transpiration of transmission of heat and convection current on the other hand.
Especially in the application of described indirect cooling, the parts of the close radial clearance of compressor housing have and are used for transmission of heat and go into the radiating fin of cooling fluid and arrange (Rippenanordnung).Advantageously enlarge heat transfer area thus and improved thermal transpiration.This radiating fin is arranged and has advantageously been stirred cooling fluid and amplified its cooling action in directly cooling off.
In a preferred embodiment, the parts of the close radial clearance of compressor housing have labyrinth type seal (Labyrinthdichtung) and flow with seal leakage.Between the compressor impeller of compressor housing and rotation therein, adopted low friction sealed thus on the one hand, this is still low-loss and low safeguard not, especially also be not produce frictional heat or only produce low frictional heat, extra thus contribution is, the temperature of compressor impeller is remained in the critical range.In addition on the one hand, labyrinth type seal is also arranged and is acted on as radiating fin, has therefore improved medium from radial clearance to the parts of compressor housing and the heat conduction that enters cooling fluid.Therefore labyrinth type seal can preferably be arranged in the zone of parts of the compressor housing that cooling fluid flows through.
[description of drawings]
Further purpose of the present invention, advantage and technical characteristics can the accessory rights claims and are known from following embodiment of the present invention, wherein illustrate here:
Fig. 1 is according to the diagrammatic side view of the parts of the compressor of the first embodiment of the present invention;
Fig. 2 is the parts of the compressor of the second embodiment of the present invention of corresponding description in Fig. 1;
Fig. 3 is the parts of the compressor of the third embodiment of the present invention of corresponding description in Fig. 1,2;
Fig. 4 is the parts of the compressor of the fourth embodiment of the present invention of corresponding description in Fig. 1-3.
[embodiment]
Fig. 1 has schematically illustrated the side view according to the parts of the compressor of the first embodiment of the present invention.Compressor comprises compressor impeller 1, and it is rotatably settled in compressor housing 11 and separates by radial clearance 14 and compressor housing.Compressor blade 12 crooked on a plurality of circumferential direction is distributed on the circumference of hub of compressor impeller, only shows one in Fig. 1.
Compressor blade 12 is to have by aluminium oxide AI
2O
3The coating 2 of the minimizing heat input of making, this coating extends to impeller outlet and coated by thermal spraying from the air inlet edge 13 of partial blade group in an embodiment.Though can not be in Fig. 1 by cognition, the surface area of compressor wheel hub also is provided with coating in this zone.
Air radially with on the circumferential direction is being quickened by compressor blade 12, and slowing down in diffuser (not being illustrated) subsequently also is compressed thus.Wherein at first in the heating of partial blade group zone, the energy of air is imported into by acceleration air in the partial blade group.Its heat partly is dissipated into compressor impeller, and wherein importing proportional temperature difference with heat is the highest in the zone of partial blade group.The thermal transmission coefficient of the coating 2 by reducing heat input is less than the thermal transmission coefficient of not coated compressor impeller.Thus, less with the proportional heat input of thermal transmission coefficient, thus pressurized air total amount of heat still less passes to compressor impeller.
In order to discharge the part heat of compressor impeller, in first embodiment shown in the accompanying drawing 1, be provided with indirect cooling.For this reason, compressor housing 11 preferably is made of two parts, wherein respectively has groove (Aussparung) towards the parts 6 of radial clearance 14 and the another one parts of compressor housing 11, and these grooves define the chamber 4 under common coupled condition.Wherein be threaded on another parts of compressor housing 11 (not being illustrated) towards the parts 6 of radial clearance 14, chamber 4 resists radial clearances 14 by seal ring 5 and sealed.
, from the motor cool cycles flows into chamber, flow through chamber and from compressor housing, discharge once more by intake line 3 cold water by output pipe (not being illustrated).Here, water obtains heat from the air by compression heating, and it is from as the leakage flow of 11 of compressor impeller 1 and compressor housings, flow into radial clearance 14 along the main flow of blade 12.In order to improve transmission of heat, parts 6 have row's radiating fin and arrange 7 in chamber 4 zones, and radiating fin has enlarged heat conducting area, can improve the eddy current of leakage flow and the transmission of heat by convection current thereof in addition.Following heated water is cooled in the heat exchanger that is located at the compressor outside (not being illustrated) once more.
Be compressed on the one hand thus and, and therefore avoided towards the heating of the rear side of the compressor impeller 1 of radial clearance 14 because the air of the heated leakage flow of compression is cooled.The leakage flow that so is cooled in addition absorbs heat and heat is conducted the water that flows through in chamber 4 from compressor impeller.Compressor impeller 1 is indirectly by the air in radial clearance 14 thus, and radiating fin layout 7 is cooled with the water that flows through chamber 4.
Because the coating 2 of minimizing heat input has reduced the heat from pressurized air importing compressor impeller 1, the amount of the less circulating water that flows through chamber 4 just enough derives these heats from compressor impeller, make compressor impeller can not surpass for example 200 ℃ of critical temperatures that allow.Chamber 4, input pipeline 3, output pipeline and radiating fin arrange that 7 can design lessly thus.The power of necessary water cycle and the specification of the heat in the water being distributed the heat exchanger in the environment have been reduced like this.
Fig. 2 illustrates the parts according to the compressor of second embodiment of the invention of in Fig. 1 corresponding description.Only will the difference with first embodiment be elaborated below, all the other, especially identical feature is with reference to above stated specification.
Form labyrinth type seal 8 towards the parts 6 of radial clearance 14 with the rear side of compressor impeller 1 in a second embodiment.Wherein parts 6 define chamber 4 with another parts of compressor housing 11 under common coupled condition.The leakage flow of this hot compressed air that has reduced to come from main flow on the one hand in the radial clearance 14, so that the rear side of compressor impeller 1 no longer or is seldom impacted by high temperature air, advantageously reduced the heat input of compressor impeller and be used for the necessary cool stream scale of construction of cooling indirectly.In addition, labyrinth arranges 8, and it is built in chamber 4 zones of being flow through by water, works as the cold sink of describing among first embodiment arranges 7.
Fig. 3 illustrates the compressor part according to the third embodiment of the present invention.Only the difference with previous embodiment is elaborated once more below, remaining feature is with reference to above stated specification.
In the 3rd embodiment, be provided with the direct cooling of compressor impeller 1.For this reason, the parts 6 of compressor housing 11 have the axial bore 10 of a plurality of distributions on circumferential direction, and it communicates with chamber 4, and different with the one the second embodiments is that it does not have output pipe.Be extracted in the charger-air cooler that cool air never is illustrated, under superpressure, import chambers 4, flow through axial bore 10 and impact at rear side towards the compressor impeller 1 of radial clearance 14 from chamber by intake line 3.Also then flowing out radial clearance at that cool air from compressor impeller absorption heat enters the main flow of working medium.Thus advantageously not only the compressor impeller rear side be cooled, and reduced leakage flow simultaneously to impact from the hot compressed gas of main flow.
Because efficient directly combines with absorption from the cool air of charger-air cooler, the heat by reducing the derivation of passing through coating 2 of the present invention and reduce the necessary cool air amount that is attached thereto has improved the efficient of compressor.Fig. 4 illustrates the parts according to the compressor of the fourth embodiment of the present invention.Only the difference with previous embodiment is elaborated once more below, remaining feature is with reference to above stated specification.
Be different from the 3rd embodiment, have labyrinth type seal according to the 4th embodiment's compressor in chamber 4 zones, labyrinth type seal has reduced enter (the joining second embodiment) of leakage flow in the radial clearance 14.In this labyrinth type seal, be configured with the groove 9 that extends on a plurality of circumferential direction in circle distribution ground, groove communicates with chamber 4.As the 3rd embodiment, cool air flows through this groove, follows the rear side of impact compress machine impeller 1, and the rear side of compressor impeller 1 is cooled and then is directed in the main flow of working medium.By the labyrinth type seal of structure at compressor impeller 1 and on and the rotation of compressor impeller 1 near the parts 6 of the compressor housing 11 of compressor impeller, on cool air, stir by the stream that groove 9 leaves in this zone, this has improved the heat transmission between cool air and compressor impeller and has advantageously strengthened cooling thus greatly, makes maximum temperature that temperature at the compressor impeller that the present invention under the situation of less cool air amount applies is maintained at permission for example under 200 ℃.The minimizing of cool air amount has improved the efficient of compressor once more.
Claims (12)
1. compressor, especially centrifugal compressor, be used to the to have compressor impeller turbocharger of (1), it is received in compressor housing (11) revolvably, wherein pass through near the parts (6) of the compressor housing of the compressor impeller fluid that is cooled, it is characterized in that compressor impeller has the coating (2) that reduces the heat input at least in part.
2. compressor according to claim 1, it is characterized in that, compressor impeller comprises compressor wheel hub and at least one compressor blade (12), and wherein compressor wheel hub and/or at least one compressor blade have the coating that reduces the heat input at least in part.
3. compressor according to claim 2 is characterized in that, the coating that reduces the heat input only is configured on the surface in the face of the compressor of the main flow of the working fluid that is compressed by compressor.
4. compressor according to claim 3 is characterized in that, the coating of minimizing heat input extends to impeller outlet from the inlet edge (13) of partial blade group.
5. according to the described compressor of aforementioned arbitrary claim, it is characterized in that the coating that reduces the heat input comprises ceramic coating.
6. compressor according to claim 5 is characterized in that ceramic coating passes through thermal spray coating.
7. according to the arbitrary described compressor of claim 5-6, it is characterized in that ceramic coating comprises aluminium oxide and/or zirconium oxide, especially the solid zirconium oxide of yttrium.
8. according to the described compressor of aforementioned arbitrary claim, it is characterized in that the chamber (4) in the chilled fluid flow overcompression engine housing.
9. according to the described compressor of aforementioned arbitrary claim, it is characterized in that cooling fluid imports in the radial clearance, this radial clearance is built between compressor impeller and the compressor housing.
10. according to the described compressor of aforementioned arbitrary claim, it is characterized in that the parts (6) of the compressor housing of close compressor impeller have heat conducting radiating fin layout (7) in cooling fluid.
11., it is characterized in that the parts (6) of the compressor housing of close compressor impeller have the labyrinth type seal (8) of seal leakage stream according to the described compressor of aforementioned arbitrary claim.
12. the cooling means according to the described compressor of aforementioned arbitrary claim is characterized in that, flows through near the parts of the compressor housing of the compressor impeller fluid that is cooled.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102006048784.2 | 2006-10-12 | ||
| DE102006048784A DE102006048784A1 (en) | 2006-10-12 | 2006-10-12 | Compressor for a turbocharger and method for its cooling |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101631940A true CN101631940A (en) | 2010-01-20 |
Family
ID=38826577
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200780045671A Pending CN101631940A (en) | 2006-10-12 | 2007-10-10 | Compressor for turbocharger and cooling method thereof |
Country Status (6)
| Country | Link |
|---|---|
| JP (1) | JP2010506091A (en) |
| KR (1) | KR20090082890A (en) |
| CN (1) | CN101631940A (en) |
| CH (1) | CH698234B1 (en) |
| DE (1) | DE102006048784A1 (en) |
| WO (1) | WO2008043539A1 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107448417A (en) * | 2017-09-01 | 2017-12-08 | 西北工业大学 | Centrifugal compressor and impeller cooling device |
| CN107642382A (en) * | 2016-07-20 | 2018-01-30 | 曼柴油机和涡轮机欧洲股份公司 | Radial turbine rotor and the method for producing it |
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| DE102009024679B4 (en) | 2009-06-12 | 2016-04-07 | Man Diesel & Turbo Se | Compressor impeller and thus equipped centrifugal compressor |
| DE102009034962B3 (en) * | 2009-07-28 | 2011-01-13 | Man Diesel & Turbo Se | Radial compressor for consolidating and compressing e.g. natural gas in supercharger of internal-combustion engine, has rib provided in cooling fluid passage, and impeller-side wall section connected with interior-side wall section over rib |
| GB2531980B (en) * | 2009-11-21 | 2016-08-10 | Cummins Turbo Tech Ltd | Compressor wheel |
| GB2475533B (en) * | 2009-11-21 | 2016-04-13 | Cummins Turbo Tech Ltd | Compressor wheel |
| FR2960923B1 (en) * | 2010-06-08 | 2013-12-20 | Snecma | AXIAL PUSH CONTROL BY GUIDING AIR FROM A 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 |
| DE102010042104A1 (en) | 2010-10-07 | 2012-04-26 | Bayerische Motoren Werke Aktiengesellschaft | Supercharger for combustion engine, has compressor housing comprising coolant channel that is integrated into coolant circuit and extended tangentially and radially around compressor screw arranged radially around compressor wheel |
| KR20130063223A (en) | 2011-12-06 | 2013-06-14 | 현대자동차주식회사 | Compressor housing and two stage turbocharger thereof |
| GB2499627A (en) * | 2012-02-23 | 2013-08-28 | Napier Turbochargers Ltd | Turbocharger casing |
| JP2014111905A (en) * | 2012-12-05 | 2014-06-19 | Mitsubishi Heavy Ind Ltd | Centrifugal compressor and supercharger with the same, and operation method for centrifugal compressor |
| DE102012024314A1 (en) | 2012-12-13 | 2014-06-18 | Daimler Ag | Turbocharger for energy converter, has shaft mounted at housing by air suspension which is supplied with air for bearing shaft due to pressure difference between compressor room and turbine room and due to pressure drop over labyrinth seal |
| DE102013203455A1 (en) * | 2013-02-28 | 2014-08-28 | Abb Turbo Systems Ag | Partition wall for sealing the rear space of a centrifugal compressor |
| DE102013013235A1 (en) * | 2013-08-08 | 2015-02-12 | Man Diesel & Turbo Se | End cover for a compressor impeller of an exhaust gas turbocharger and turbocharger |
| JP6382120B2 (en) * | 2015-01-26 | 2018-08-29 | 三菱重工業株式会社 | Exhaust turbine turbocharger |
| JP6899232B2 (en) * | 2017-03-07 | 2021-07-07 | 三菱重工業株式会社 | Electric supercharger |
| US11300140B2 (en) | 2017-12-25 | 2022-04-12 | Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. | Compressor wheel and supercharger |
| KR102075550B1 (en) * | 2018-09-19 | 2020-02-11 | 한국과학기술원 | Oxy-fuel combustion power generation system |
| WO2022098437A2 (en) * | 2020-09-17 | 2022-05-12 | Applied Materials, Inc. | Aluminum oxide protective coatings on turbocharger components and other rotary equipment components |
| DE102021127333A1 (en) * | 2021-10-21 | 2023-04-27 | Ihi Charging Systems International Gmbh | Fuel cell charging system |
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| JPS60164602U (en) * | 1984-04-10 | 1985-11-01 | 三菱レイヨン株式会社 | Rotor for turbo gear |
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| JP3294491B2 (en) * | 1995-12-20 | 2002-06-24 | 株式会社日立製作所 | Turbocharger for internal combustion engine |
| DE19652754A1 (en) * | 1996-12-18 | 1998-06-25 | Asea Brown Boveri | Exhaust gas supercharger |
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| US6375425B1 (en) * | 2000-11-06 | 2002-04-23 | General Electric Company | Transpiration cooling in thermal barrier coating |
| EP1317995A1 (en) * | 2001-12-05 | 2003-06-11 | Siemens Aktiengesellschaft | Method and apparatus for smoothing the surface of a gas turbine airfoil |
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-
2006
- 2006-10-12 DE DE102006048784A patent/DE102006048784A1/en not_active Ceased
-
2007
- 2007-10-10 WO PCT/EP2007/008804 patent/WO2008043539A1/en active Application Filing
- 2007-10-10 KR KR1020097009541A patent/KR20090082890A/en not_active Application Discontinuation
- 2007-10-10 CH CH00609/09A patent/CH698234B1/en not_active IP Right Cessation
- 2007-10-10 JP JP2009531768A patent/JP2010506091A/en active Pending
- 2007-10-10 CN CN200780045671A patent/CN101631940A/en active Pending
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107642382A (en) * | 2016-07-20 | 2018-01-30 | 曼柴油机和涡轮机欧洲股份公司 | Radial turbine rotor and the method for producing it |
| CN107448417A (en) * | 2017-09-01 | 2017-12-08 | 西北工业大学 | Centrifugal compressor and impeller cooling device |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2008043539A1 (en) | 2008-04-17 |
| KR20090082890A (en) | 2009-07-31 |
| DE102006048784A1 (en) | 2008-04-17 |
| CH698234B1 (en) | 2010-10-15 |
| JP2010506091A (en) | 2010-02-25 |
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