CN101749059B - Vibration damping in an exhaust-gas turbocharger - Google Patents
Vibration damping in an exhaust-gas turbocharger Download PDFInfo
- Publication number
- CN101749059B CN101749059B CN200910258098.XA CN200910258098A CN101749059B CN 101749059 B CN101749059 B CN 101749059B CN 200910258098 A CN200910258098 A CN 200910258098A CN 101749059 B CN101749059 B CN 101749059B
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- China
- Prior art keywords
- disturbance
- fluid
- fluid machinery
- guide vane
- vibration
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
- 238000013016 damping Methods 0.000 title abstract description 6
- 239000012530 fluid Substances 0.000 claims abstract description 67
- 238000002485 combustion reaction Methods 0.000 claims description 11
- 238000000034 method Methods 0.000 claims description 4
- 238000011144 upstream manufacturing Methods 0.000 claims description 4
- 230000001939 inductive effect Effects 0.000 abstract 1
- 239000007789 gas Substances 0.000 description 15
- 239000002912 waste gas Substances 0.000 description 9
- 230000005284 excitation Effects 0.000 description 3
- 239000000463 material Substances 0.000 description 3
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 230000001419 dependent effect Effects 0.000 description 2
- 230000001133 acceleration Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000000763 evoking effect Effects 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 230000002452 interceptive effect Effects 0.000 description 1
- 238000000465 moulding Methods 0.000 description 1
- 230000010355 oscillation Effects 0.000 description 1
- 230000003071 parasitic effect Effects 0.000 description 1
- 230000000737 periodic effect Effects 0.000 description 1
- 230000010363 phase shift Effects 0.000 description 1
- 238000004088 simulation Methods 0.000 description 1
Images
Classifications
-
- 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
- F01D17/00—Regulating or controlling by varying flow
- F01D17/10—Final actuators
- F01D17/12—Final actuators arranged in stator parts
- F01D17/14—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits
- F01D17/16—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of nozzle vanes
-
- 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
-
- 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
- F01D25/04—Antivibration arrangements
- F01D25/06—Antivibration arrangements for preventing blade vibration
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/12—Control of the pumps
- F02B37/22—Control of the pumps by varying cross-section of exhaust passages or air passages, e.g. by throttling turbine inlets or outlets or by varying effective number of guide conduits
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/12—Control of the pumps
- F02B37/24—Control of the pumps by using pumps or turbines with adjustable guide vanes
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
- F02B39/16—Other safety measures for, or other control of, pumps
-
- 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
-
- 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
- F05D2260/96—Preventing, counteracting or reducing vibration or noise
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Chemical Kinetics & Catalysis (AREA)
- General Chemical & Material Sciences (AREA)
- Supercharger (AREA)
- Turbine Rotor Nozzle Sealing (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The invention relates to vibration damping in an exhaust gas turbocharger, in particular to a fluid machine for an exhaust gas turbocharger, comprising a housing (1) which defines a flow path for a fluid flowing through the fluid machine; a rotor hub (2) rotatably accommodated in the housing; a plurality of rotor blades (3) arranged on the hub for deflection of the fluid flow; and a guide device with guide vanes (4) for deflection of the fluid flow; and a disturbance generator (5) for inducing a disturbance in the fluid flow, which disturbance reduces, by superposition, the vibrations of the rotor blades (3) induced by the guide blades (4).
Description
Technical field
The present invention relates to a kind of according to the fluid machinery for exhaust-gas turbocharger (Abgasturbolader) of the preamble of claim 1 (Stroemungsmaschine), be particularly useful for self-igniting internal combustion engine, with the exhaust-gas turbocharger of this fluid machinery, and the method for a kind of vibration damping for this exhaust-gas turbocharger (Schwingungsreduzierung).
Background technique
For the exhaust-gas turbocharger of internal-combustion engine, always comprise two fluid machineries: for the compressor (Verdichter) of the compression of internal-combustion engine combustion air used (Verbrennungsluft), and for the turbo machine (Turbine) of drive compression machine.Especially at for example, exhaust-gas turbocharger for high power self-igniting internal combustion engine (marine diesel engine), compressor and turbo machine bear high mechanical load and thermomechanics load by flowing through their fluid (that is, combustion air or waste gas).On the other hand, make every effort to now the working blade of fluid machinery (Laufschaufel) implement to obtain elongated as far as possible (schlank).
Yet this type of blade (Schaufeln) is because it is compared with little moment of inertia and rigidity and the impact of easy especially vibrated excitation (Schwingungsanregungen).This vibration is brought out (induzieren) by the guide wheel impeller (Leitradschaufel) of front guide device working blade upstream or downstream or rear guide device especially in the following way, that is, it causes that in fluid stream (Fluidstroemung) normal is periodic disturbance (Stoerung).Working blade vibrates so by the fluid of disturbance, then in one side, to be excited---being nowadays configured to more and more thinner---.This vibrational excitation meeting affects spendable speed range, lowers efficiency, and increase noise generates and can be until cause the material load of structural collapse under resonance.
Summary of the invention
Therefore, the object of the invention is to, reduce or avoid one or more in above-mentioned impact.
In order to realize this object, the feature according to the fluid machinery of the preamble of claim 1 by its characteristic is modified.The claimed exhaust-gas turbocharger with this fluid machinery of claim 11, the method for the claimed vibration damping for this exhaust-gas turbocharger of claim 12.Favourable form of implementation of the present invention and improvement project provide in the dependent claims.
Exhaust-gas turbocharger according to fluid machinery of the present invention, there is in known manner the guiding device (Leiteinrichtung) of guide vane (Leitschaufeln) that the housing of the runner (Stroemungskanal) having defined for flowing through the fluid of this fluid machinery, the active wheel wheel hub (Laufradnabe) that is contained in rotationally this housing, a plurality of working blades that are arranged in the deflection (Umlenken) for fluid stream on wheel hub and band are useful on the deflection of this fluid stream.
Fluid stream can be for example the combustion air for internal-combustion engine, and it is compressed by the compressor that is especially configured to radial flow compressor or diagonal flow type compressor (Diagonalverdichter) of exhaust-gas turbocharger; Or, be the waste gas of internal-combustion engine, it drives the turbo machine that is especially configured to axial flow turbine of exhaust-gas turbocharger.
Guiding device can be especially at the upper rear guiding device that (stromabwaerts) arranges after working blade downstream of flow direction (Stroemungsrichtung), but also can on flow direction in upstream (stromaufwaerts) front guiding device of arranging before working blade.Guide vane can be fixed or adjustable with respect to guiding device.
By this guiding device, will bring out flow disturbance (Stroemungsstoerungen), especially pressure surge or speed fluctuation, parasitic (parasitaere) or the stream of convection current in fluid for example, it can evoke in one side the vibration of runner vane (Laufradschaufeln).
Therefore, according to the present invention, advise, by disturbance generator (Stoerungsgenerator), in fluid stream, bring out such disturbance, the vibration of the working blade that this disturbance reduces to be brought out by guide vane by stack (Ueberlagerung).
As everyone knows, the vibration that Oscillation Amplitude (Schwingungsamplituden) can be applied by haply anti-phase (gegenphasig) is reduced or cancellation.This as interfering, initiatively de-noising (Gegenschall) or noise reduction (Antischall) and known principle can advantageously be used with two kinds of forms in the present invention: on the one hand, disturbance generator can bring out such flow disturbance, especially pressure or speed fluctuation in fluid---and it evokes the vibration of runner vane in one side, then this vibration reduces such vibration by superposeing, that is, this vibration is brought out by guide vane.Therefore, working blade is loaded by two such flow disturbances, that is, these two flow disturbances have caused the vibration of cutting down each other of working blade.Extraly or alternatively, disturbance generator also can bring out such flow disturbance, especially pressure or speed fluctuation in fluid---and it reduces such flow disturbance by superposeing, that is, this flow disturbance is produced and is evoked the non-desired vibration of runner vane by guide vane.Therefore the flow disturbance, working blade being loaded be just reduced and thus the vibrational excitation of working blade be reduced.
So can reduce in particular or avoid the resonance of working blade.With which, preferably can use in other cases due to speed range that resonance is difficult to arrive, raise the efficiency, improve thermodynamic parameter (Kennwerte) and/or mechanical parameter and/or reduce significantly noise and generate or material load.
Disturbance generator can be configured to active member, and the diaphragm or the fellow that be for example configured to piezoelectric transducer, can electromagnetic mode handle, to bring out suitable flow disturbance in fluid.Extraly or alternatively, disturbance generator can comprise (geometrischen) disturbance position (Stoerstelle) of one or more geometry.When fluid flows along this disturbance position, this flows by disturbance.
How much disturbance portion bit position and/or shape are preferably so selected, that is, the resonance amplitude (Resonanzamplitude) of the vibration of the working blade that brought out by guide vane is reduced by superposeing.Those skilled in the art can be for example determine the optimum disturbance position of corresponding fluid machinery by experimental test and/or analog computation, especially FEM vibration and/or flow field simulation.
In particular, one or more disturbances position can construct (blinde) perforation or obstructed in wall-forming portion,, the recess (Aussparung) of blind-hole type, fluid is in these recess by-pass flows.This recess can be suitable form manufacturedly simply go out.Extraly or alternatively, disturbance position also can be configured to the projection (Erhebungen) in wall portion, fluid is in this projection by-pass flow.This recess and/or projection can be together with wall portion by moulding (urgeformt) or afterwards for example in the mode of cutting or be constructed by the additional of additional materials.
That this recess and/or projection can for example have is circular, oval-shaped, water-drop-shaped or rectangle, by the cross section of fluid institute circulation (umstroemen).For example, recess can hole, especially slot-type be holed (Langlochbohrung), or the formal construction of seam forms.Can being extended in axial and/or circumferential direction by the main axis in the cross section of fluid institute circulation of recess and/or projection.
Disturbance generator, especially above-mentioned disturbance position, can preferably be arranged in as fluid definition in the housing and/or guiding device of runner.
Preferably, how much the number at disturbance position conforms to (entsprechen) with the number of the guide vane of guiding device or the integral multiple of this number, because can bring out thus the disturbance that is particularly suitable for the vibration that reduces to be brought out by guide vane in fluid flows.
For effective especially vibration damping, the vibration that the phase place of the disturbance during the phase place of the vibration in the working blade being brought out by disturbance generator (Phase) or the fluid being brought out by disturbance generator flow can be brought out by guide vane in contrast to (entgegengerichtet) haply or the phase place of disturbance.Yet, with other phase shift and/or vibration and/or the disturbance of other frequency, be suitable for equally the vibration that reduces to be brought out by guide vane.
Accompanying drawing explanation
Other advantage and feature draw in dependent claims and embodiment.Wherein, partly schematically:
Fig. 1 has shown a part for the compressor of exhaust-gas turbocharger according to an embodiment of the present in the partial cross section of perspective; And
Fig. 2 has shown a part for the turbo machine of exhaust-gas turbocharger according to an embodiment of the present in the partial cross section of perspective.
List of reference characters
1 housing
2 active wheel wheel hubs
3 working blades
4 guide vanes
5 holes
N rotating speed
Embodiment
In Fig. 1 in perspective view with profile type shown marine diesel engine exhaust-gas turbocharger according to radial flow compressor of the present invention.
Active wheel wheel hub or rotor hub 2 are so contained in housing 1, that is, make, and have defined the runner for this marine diesel engine combustion air used between them.In this runner, be furnished with acceleration (Beschleunigung) for air and the working blade 3 of deflection, it rotates and air is flowed to the guide vane 4 of the rear guiding device that is arranged in downstream together with active wheel wheel hub 2 around the longitudinal axis of compressor with rotation speed n, in rear guiding device, the kinetic energy of air is partly converted into pressure energy.
By guide vane 4, in air stream, brought out the disturbance that is pressure and speed fluctuation form, it loads working blade 3.Therefore because that working blade is configured to thin wall-type and there is little flexural rigidity, so, thereby being excited, the disturbance of working blade by the air stream that brought out by guide vane 4 do non-desired vibration.
In housing 1, in upstream, before each guide vane 4, be configured with haply in upwardly extending slot-type boring 5 of week.Similarly in air stream, brought out thus the disturbance that is pressure and speed fluctuation form, it excites working blade 3 to vibrate equally.Position, shape, size and the degree of depth of slot-type boring 5 are so selected, and, make the vibration being induced the therefrom anti-phase vibration of being brought out by guide vane 4 in (gegenphasig zu) haply in working blade that is.Therefore, these the two kinds of vibrations in working blade 3 are reciprocally offset haply by stack, thereby, reduced significantly the global vibration amplitude of working blade 3.
In Fig. 2 in perspective view with profile type shown marine diesel engine exhaust-gas turbocharger according to axial flow turbine of the present invention.The element corresponding to each other is to mark as the identical reference number in Fig. 1.
Correspondingly, active wheel wheel hub 2 is so contained in housing 1,, makes to have defined the runner for the waste gas of marine diesel engine between them that is.In this runner, be furnished with the working blade 3 for the deflection of waste gas, it is the longitudinal axis rotation around turbo machine with rotation speed n together with active wheel wheel hub 2.
The guide vane 4 that makes the guiding device of waste gas deflection by the mode with suitable has brought out the disturbance of the form that is pressure and speed fluctuation in air stream, and it loads working blade 3.Therefore because that working blade is configured to thin wall-type and there is little flexural rigidity, so the disturbance meeting by the waste gas streams that brought out by guide vane 4 evokes the non-desired vibration of working blade.
For each guide vane 4 is assigned the slot-type extending in the circumferential direction haply boring 5 being configured in housing 1.Similarly in waste gas streams, brought out thus the disturbance that is pressure and speed fluctuation form.Position, shape, size and the degree of depth of slot-type boring 5 are so selected, that is, make, and the disturbance being induced therefrom in waste gas streams is anti-phase in the disturbance of being brought out by guide vane 4 haply.Therefore, two kinds of disturbances of this in waste gas streams are reciprocally offset haply by stack, thereby working blade 3 is loaded and is excited in slighter mode and vibrates, thereby, at this, reduced equally significantly the global vibration amplitude of working blade 3.
Claims (17)
1. for the fluid machinery of exhaust-gas turbocharger, with
Defined for flowing through the housing (1) of runner of the fluid of described fluid machinery;
Be contained in rotationally the active wheel wheel hub (2) in described housing;
Be arranged in a plurality of working blades (3) of the deflection for fluid stream on described wheel hub; With
Be with the guiding device of the guide vane (4) of the deflection that is useful on described fluid stream;
It is characterized in that,
Described fluid machinery has for bring out the disturbance generator of disturbance at described fluid stream, and this disturbance reduces the vibration of the described working blade (3) that brought out by described guide vane (4) by superposeing.
2. fluid machinery according to claim 1, is characterized in that, described fluid machinery is compressor or the turbo machine of exhaust-gas turbocharger.
3. fluid machinery according to claim 2, is characterized in that, described compressor is radial flow compressor or diagonal flow type compressor.
4. fluid machinery according to claim 2, is characterized in that, described turbo machine is axial flow turbine.
5. according to the fluid machinery described in any one in aforementioned claim 1 to 4, it is characterized in that, described guiding device is be downstream arranged in rear guiding device afterwards of described working blade (3) or on flow direction, in upstream, be arranged in described working blade (3) front guiding device before on flow direction.
6. according to the fluid machinery described in any one in aforementioned claim 1 to 4, it is characterized in that, described disturbance generator is configured for bringing out the disturbance of the fluid stream that flows through described fluid machinery, for passing through this fluid induced vibration in described working blade (3), it reduces the vibration of the described working blade (3) that brought out by described guide vane (4) by superposeing, and/or, the disturbance of flowing for the fluid that flows through described fluid machinery that reduces by superposeing to be brought out by described guide vane (4).
7. according to the fluid machinery described in any one in aforementioned claim 1 to 4, it is characterized in that, described disturbance generator comprises at least one disturbance position of how much.
8. fluid machinery according to claim 7, is characterized in that, at least one disturbance position is configured to recess that connect or obstructed or is configured to projection.
9. fluid machinery according to claim 8, is characterized in that, at least one disturbance position has by the cross section of fluid circulation, wherein, on the axial direction of the main axis in this cross section for the longitudinal axis with respect to fluid machinery, extends.
10. fluid machinery according to claim 8, is characterized in that, at least one disturbance position has by the cross section of fluid circulation, wherein, in the circumferential direction of the main axis in this cross section for the longitudinal axis with respect to fluid machinery, extends.
11. according to the fluid machinery described in any one in aforementioned claim 1 to 4, it is characterized in that, described disturbance generator is arranged in described guiding device and/or described housing (1).
12. according to aforementioned fluid machinery claimed in claim 7, it is characterized in that, the number at disturbance position of described geometry and the number of the guide vane of described guiding device (4) or the integral multiple of this number conforms to.
13. according to aforementioned fluid machinery claimed in claim 7, it is characterized in that, disturbance portion bit position and/or the shape of described geometry are so selected, that is, the resonance amplitude of the vibration of the described working blade (3) that brought out by described guide vane (4) is reduced by superposeing.
14. according to the fluid machinery described in any one in aforementioned claim 1 to 4, it is characterized in that, the phase place of the vibration of being brought out by described disturbance generator in described working blade (3) is haply in contrast to the phase place of the vibration of being brought out by described guide vane (4), and/or the phase place of the disturbance of being brought out by described disturbance generator in fluid stream is haply in contrast to the phase place of the disturbance of being brought out by described guide vane (4).
15. 1 kinds of exhaust-gas turbochargers, are with good grounds fluid machinery in any one of the preceding claims wherein.
16. exhaust-gas turbochargers according to claim 15, is characterized in that, described exhaust-gas turbocharger is the exhaust-gas turbocharger for self-igniting internal combustion engine.
17. 1 kinds for reducing according to the method for the vibration of being brought out by guide vane (4) of the working blade of the fluid machinery of the exhaust-gas turbocharger described in claim 15 or 16 (3), it is characterized in that, disturbance generator brings out disturbance in fluid stream, and this disturbance reduces the vibration of the described working blade (3) that brought out by described guide vane (4) by superposeing.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102008061235.9 | 2008-12-09 | ||
| DE102008061235.9A DE102008061235B4 (en) | 2008-12-09 | 2008-12-09 | Vibration reduction in an exhaust gas turbocharger |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101749059A CN101749059A (en) | 2010-06-23 |
| CN101749059B true CN101749059B (en) | 2014-05-07 |
Family
ID=42145718
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200910258098.XA Expired - Fee Related CN101749059B (en) | 2008-12-09 | 2009-12-09 | Vibration damping in an exhaust-gas turbocharger |
Country Status (5)
| Country | Link |
|---|---|
| JP (1) | JP4995881B2 (en) |
| KR (2) | KR20100066341A (en) |
| CN (1) | CN101749059B (en) |
| CH (1) | CH700069B1 (en) |
| DE (1) | DE102008061235B4 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104246168A (en) * | 2012-05-03 | 2014-12-24 | 博格华纳公司 | Exhaust-gas turbocharger |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2001027103A (en) * | 1999-07-14 | 2001-01-30 | Ishikawajima Harima Heavy Ind Co Ltd | Stationary blade structure for axial turbo-machine |
| JP2004257311A (en) * | 2003-02-26 | 2004-09-16 | Ishikawajima Harima Heavy Ind Co Ltd | Fan for aircraft engine, aircraft engine, and fan stationary blade |
| CN1902379A (en) * | 2003-11-19 | 2007-01-24 | 霍尼韦尔国际公司 | Profiled blades for turbocharger turbines, compressors, and the like |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5275902U (en) * | 1975-12-05 | 1977-06-07 | ||
| EP0229519B2 (en) * | 1985-12-24 | 1996-11-13 | Holset Engineering Company Limited | Improvements in and relating to compressors |
| JPH10110611A (en) * | 1996-10-03 | 1998-04-28 | Ippei Torigoe | Silencer |
| JPH10131891A (en) * | 1996-10-29 | 1998-05-19 | Daikin Ind Ltd | Propeller fan |
| JP3801367B2 (en) * | 1998-10-08 | 2006-07-26 | 三菱重工業株式会社 | Exhaust gas turbocharger |
| US6669436B2 (en) * | 2002-02-28 | 2003-12-30 | Dresser-Rand Company | Gas compression apparatus and method with noise attenuation |
-
2008
- 2008-12-09 DE DE102008061235.9A patent/DE102008061235B4/en not_active Expired - Fee Related
-
2009
- 2009-08-18 CH CH01280/09A patent/CH700069B1/en unknown
- 2009-09-29 KR KR1020090092442A patent/KR20100066341A/en active Application Filing
- 2009-10-07 JP JP2009233561A patent/JP4995881B2/en not_active Expired - Fee Related
- 2009-12-09 CN CN200910258098.XA patent/CN101749059B/en not_active Expired - Fee Related
-
2015
- 2015-09-15 KR KR1020150130473A patent/KR101821457B1/en active IP Right Grant
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2001027103A (en) * | 1999-07-14 | 2001-01-30 | Ishikawajima Harima Heavy Ind Co Ltd | Stationary blade structure for axial turbo-machine |
| JP2004257311A (en) * | 2003-02-26 | 2004-09-16 | Ishikawajima Harima Heavy Ind Co Ltd | Fan for aircraft engine, aircraft engine, and fan stationary blade |
| CN1902379A (en) * | 2003-11-19 | 2007-01-24 | 霍尼韦尔国际公司 | Profiled blades for turbocharger turbines, compressors, and the like |
Also Published As
| Publication number | Publication date |
|---|---|
| KR101821457B1 (en) | 2018-01-23 |
| DE102008061235A1 (en) | 2010-06-10 |
| DE102008061235B4 (en) | 2017-08-10 |
| JP2010138896A (en) | 2010-06-24 |
| CH700069B1 (en) | 2014-02-28 |
| CN101749059A (en) | 2010-06-23 |
| KR20150109319A (en) | 2015-10-01 |
| CH700069A2 (en) | 2010-06-15 |
| JP4995881B2 (en) | 2012-08-08 |
| KR20100066341A (en) | 2010-06-17 |
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