CN103375183B - Turbine vibration reduction system - Google Patents
Turbine vibration reduction system Download PDFInfo
- Publication number
- CN103375183B CN103375183B CN201310135027.7A CN201310135027A CN103375183B CN 103375183 B CN103375183 B CN 103375183B CN 201310135027 A CN201310135027 A CN 201310135027A CN 103375183 B CN103375183 B CN 103375183B
- Authority
- CN
- China
- Prior art keywords
- reduction system
- vibration reduction
- opening
- turbine vibration
- wheel blade
- 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
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
- F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
- F01D25/04—Antivibration arrangements
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Turbine Rotor Nozzle Sealing (AREA)
- Vibration Prevention Devices (AREA)
Abstract
Turbine vibration reduction system includes the operable wheel blade connected of nozzle and nozzle and has the structure of at least one opening, and this opening is configured to spray a fluid in the stream moving through nozzle and wheel blade to destroy the formation of eddy current.
Description
Technical field
Subject matter disclosed herein relates generally to turbine, and more particularly relates to the system of its vibration damping.
Summary of the invention
According to an aspect of the present invention, a kind of turbine vibration reduction system includes the operable wheel blade (bucket) connected of nozzle and nozzle and the structure with at least one opening, and this opening is configured to spray a fluid in the stream moving through nozzle and wheel blade to destroy the formation of eddy current (vortex).
According to a further aspect in the invention, a kind of turbine vibration reduction system includes the operable afterbody wheel blade connected of nozzle and nozzle and the shell surrounding this afterbody wheel blade, this shell is provided with the opening being positioned at afterbody wheel blade downstream, this opening is configured to spray a fluid in the stream of afterbody wheel blade, to destroy the formation of the eddy current in fluid during the turbine operation state that beneficially eddy current is formed.These and other advantage and feature will become more fully apparent from following description with reference to the accompanying drawings.
According to an aspect of the present invention, described fluid is steam.
According to an aspect of the present invention, described structure is hub.
According to an aspect of the present invention, at least one opening described is slit.
According to an aspect of the present invention, at least one opening described is around multiple openings that described hub is circumferentially distributed.
According to an aspect of the present invention, at least one opening described is at an angle of, and becomes about 25-45 degree angle to spray steam with the axis relative to described hub.
According to an aspect of the present invention, at least one opening described is configured to spray about 3.0 pounds of steam per second under about 1.0 pound per square inches.
According to an aspect of the present invention, described structure is shell.
According to an aspect of the present invention, at least one opening described is positioned at described shell in the part in described wheel blade downstream.
According to an aspect of the present invention, at least one opening described is the multiple holes being circumferentially distributed around described shell.
According to an aspect of the present invention, a kind of turbine vibration reduction system, including: nozzle；The afterbody wheel blade that connect operable with described nozzle；And surround the shell of described afterbody wheel blade, described shell has the opening being positioned at described afterbody wheel blade downstream, described opening is configured to spray a fluid in the stream of described afterbody wheel blade, to destroy the formation of the eddy current in described fluid during the turbine operation state that beneficially eddy current is formed.
Accompanying drawing explanation
It is considered as in subject of the present invention claims at the summary of description specifically noting and being distinctly claimed right.From following detailed description of the accompanying drawings, the aforementioned and further feature of the present invention and advantage are it is clear that in the accompanying drawings:
Fig. 1 shows a part for the side view of the embodiment of turbine vibration reduction system disclosed herein；
Fig. 2 shows the view of the wheel blade from computational fluid dynamics model, it is shown that eddy current；
Fig. 3 shows a part for nozzle and the wheel blade with line, it is shown that the position that eddy current is formed；
Fig. 4 shows a part for the side view of the alternate embodiment of turbine vibration reduction system disclosed herein；And
Fig. 5 shows a part for the side view of another alternate embodiment of turbine vibration reduction system disclosed herein.
Describe in detail and describe embodiments of the invention and advantage and feature the most by way of example.
List of parts
10 turbine vibration reduction system
14 nozzles
16 structures
18 wheel blades
22 openings
30 eddy current
34 hubs (hub)
38 lines
46 shells
110 turbine vibration reduction system
114 nozzles
122 openings
134 hubs
210 turbine vibration reduction system
222 openings
224 shells.
Detailed description of the invention
With reference to Fig. 1, illustrate turbine vibration reduction system with 10.System 10 includes nozzle 14 wheel blade 18 that connect operable with nozzle 14 and the structure 16 with at least one opening 22, and this opening 22 is configured to spray a fluid in the fluid stream moving through nozzle 14 and wheel blade 18.This embodiment uses steam as fluid.
With reference to Fig. 2 and Fig. 3, in presently disclosed embodiment, the injection of steam destroys the flow separation near wheel blade 18.This flow separation has utilized computational fluid dynamics modeling and has been shown as eddy current 30 at this, and this eddy current 30 produces near hub 34 and radially outward grows along the line 38 shown in Fig. 3.This flow separation often operates at full speed no load, and formation during being particularly combined with high condenser pressure.Flow separation is in the upper air force distributing instability of wheel blade (usually L-0 (or afterbody) wheel blade) or random vibration (asynchronous vibration).Presently disclosed embodiment discloses to spray the system of steam, and injection steam destroys the formation (and flow separation) of eddy current 30 thus vibration damping.The embodiment of system disclosed herein is also configured to specifically spray during the turbine operation state that beneficially eddy current is formed steam.
Referring again to Fig. 1, at least one opening 22 through its injection steam is formed in the multiple openings 22 in multiple nozzle 14 in this embodiment.Nozzle 14 limiting structure 16 in this embodiment.Opening 22 can be located on the trailing edge of nozzle 14 and is oriented and become by the steam discharged from it adjustment (align) and flow through fluid therein in line.Opening 22 can be the hole with the diameter in the range of 0.1 to 0.2 inch.Preferably opening 22 is positioned at the comparing for shell 46 closer in half portion of hub 34 of the most each nozzle 14 towards the inner radial portion of nozzle 14, and makes opening 22 be equally spaced.Have been found that the about 10.0 pounds of mass velocities per second under the pressure of about 1.5 pound per square inches from the opening 22 in nozzle 14 be enough to destroy flow separation.
With reference to Fig. 4, with 110 alternate embodiments illustrating turbine vibration reduction system disclosed herein.The difference of system 110 and system 10 is the position of at least one opening 122 through its injection steam.In this embodiment, hub 134 limiting structure 16 and at least one opening 122 are positioned in hub 134 between nozzle 114 and wheel blade 18.(multiple) opening 122 can have various configuration, such as, the axial symmetry slit (as shown in FIG.) being formed in hub 134 or multiple hole.200-240 hole of the slit having been found that about 0.15 inch or the diameter with about 0.15 inch is all especially suitable for.(multiple) opening 122 is oriented and becomes 25-45 degree angle preferentially to adjust sprayed steam to destroy the formation of eddy current 30 relative to the axis of hub 134.The about 3.0 pounds of mass velocities per second under the pressure of about 1.0 pound per square inches carrying out (multiple) opening 122 in loose boss 134 be enough to destroy flow separation.
With reference to Fig. 5, with 210 another alternate embodiments illustrating turbine vibration reduction system disclosed herein.The difference of system 210 and system 10 and 110 is can be through the position of at least one opening 222 of its injection steam.In this embodiment, during shell 224 limiting structure 16 and at least one opening 222 are positioned at the shell 224 of wheel blade 18 downstream (as by the current limit by turbine vibration reduction system 210).In this embodiment, (multiple) opening 222 is positioned at about 2.0 inches of wheel blade 18 downstream.(multiple) opening 222 can be the axial symmetry slit of the width with about 0.5 inch being formed circumferentially in shell 224 or have about 0.5 inch diameter around the multiple single hole (about 200-240) that shell 224 is circumferentially distributed.(multiple) opening 222 is oriented and becomes 45 degree of angles preferentially to adjust sprayed steam to destroy the formation of eddy current 30 towards wheel blade 18 relative to the axis of hub 134.About 10.0 pounds of mass velocities per second under the pressure of about 1.5 pound per square inches from (multiple) opening 222 in shell 224 be enough to destroy flow separation.
Should be noted that, although the embodiment illustrated the most in the accompanying drawings the most only has one of them of single opening 22,122 and 222, but it is envisioned that alternate embodiment, it has the combination of wherein one or more of single opening 22,122 and 222 in single turbine vibration reduction system.
Although the embodiment having combined only limited quantity describe in detail the present invention, it should be readily understood that, the invention is not limited in these disclosed embodiments.On the contrary, can modify the present invention to merge not heretofore described but match with the spirit and scope of the present invention any amount of modification, retrofit, replace or equivalent arrangements.Additionally, although it have been described that various embodiments of the present invention, it is to be understood that, various aspects of the invention can only include a part of described embodiment.Therefore, the present invention is not construed as being limited by description above, and is only limited by scope of the following claims.
Claims (18)
1. a turbine vibration reduction system, including:
Nozzle；
The wheel blade that connect operable with described nozzle；And
Structure near described wheel blade, described structure has at least one opening, and at least one opening described is configured to spray steam
To destroy the formation of eddy current in the stream move through described nozzle and described wheel blade, at least one opening described is relative to described knot
The axis of structure is to become 25-45 degree angle injection steam.
Turbine vibration reduction system the most according to claim 1, it is characterised in that at least one opening described is positioned at described structure and exists
In part between described nozzle and described wheel blade.
Turbine vibration reduction system the most according to claim 1, it is characterised in that described wheel blade is afterbody wheel blade.
Turbine vibration reduction system the most according to claim 1, it is characterised in that described structure is described nozzle.
Turbine vibration reduction system the most according to claim 4, it is characterised in that at least one opening described is positioned at described nozzle
At trailing edge.
Turbine vibration reduction system the most according to claim 4, it is characterised in that at least one opening described is positioned at described nozzle
In interior radial direction half portion.
Turbine vibration reduction system the most according to claim 4, it is characterised in that at least one opening described is to have 0.15 inch
The hole of diameter.
Turbine vibration reduction system the most according to claim 4, it is characterised in that at least one opening described is on described nozzle
The multiple openings being equally spaced.
Turbine vibration reduction system the most according to claim 8, it is characterised in that the plurality of opening is oriented and becomes one with described stream
Straight line injection steam.
Turbine vibration reduction system the most according to claim 4, it is characterised in that at least one opening described is configured at 1.5 pounds
With 10 pounds of flow per second injection steam under pressure per square inch.
11. turbine vibration reduction system according to claim 1, it is characterised in that described structure is hub.
12. turbine vibration reduction system according to claim 11, it is characterised in that at least one opening described is slit.
13. turbine vibration reduction system according to claim 11, it is characterised in that at least one opening described is around described hub
The multiple openings being circumferentially distributed.
14. turbine vibration reduction system according to claim 12, it is characterised in that at least one opening described is configured at 1.0 pounds
With 3.0 pounds of flow per second injection steam under pressure per square inch.
15. turbine vibration reduction system according to claim 1, it is characterised in that described structure is shell.
16. turbine vibration reduction system according to claim 15, it is characterised in that at least one opening described is positioned at described shell
In the part in described wheel blade downstream.
17. turbine vibration reduction system according to claim 16, it is characterised in that at least one opening described is around described shell
The multiple holes being circumferentially distributed.
18. 1 kinds of turbine vibration reduction system, including:
Nozzle；
The afterbody wheel blade that connect operable with described nozzle；And
Surround the shell of described afterbody wheel blade, described shell has the opening being positioned at described afterbody wheel blade downstream, described
Opening is configured to become 25-45 degree angle to spray steam into through described afterbody wheel blade with the axis relative to described shell
In stream, to destroy the formation of the eddy current in described stream during the turbine operation state that beneficially eddy current is formed.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US13/450,170 US20130280050A1 (en) | 2012-04-18 | 2012-04-18 | Turbine vibration reduction system |
| US13/450170 | 2012-04-18 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103375183A CN103375183A (en) | 2013-10-30 |
| CN103375183B true CN103375183B (en) | 2016-08-17 |
Family
ID=48139760
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201310135027.7A Expired - Fee Related CN103375183B (en) | 2012-04-18 | 2013-04-18 | Turbine vibration reduction system |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20130280050A1 (en) |
| EP (1) | EP2653667A3 (en) |
| JP (1) | JP2013221522A (en) |
| CN (1) | CN103375183B (en) |
| RU (1) | RU2013117262A (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP2816199B1 (en) * | 2013-06-17 | 2021-09-01 | General Electric Technology GmbH | Control of low volumetric flow instabilities in steam turbines |
| EP2924245B1 (en) | 2014-03-24 | 2017-03-01 | General Electric Technology GmbH | Steam turbine with resonance chamber |
| US10371170B2 (en) | 2015-04-21 | 2019-08-06 | Pratt & Whitney Canada Corp. | Noise reduction using IGV flow ejections |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4255083A (en) * | 1976-11-05 | 1981-03-10 | Societe Nationale D'etude Et De Construction De Moteurs D'aviation | Method and device for reducing the noise of turbo-machines |
| US4967550A (en) * | 1987-04-28 | 1990-11-06 | Rolls-Royce Plc | Active control of unsteady motion phenomena in turbomachinery |
| EP2204537A2 (en) * | 2008-12-31 | 2010-07-07 | Rolls-Royce North American Technologies, Inc. | Turbine vane for gas turbine engine |
Family Cites Families (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3756740A (en) * | 1971-08-11 | 1973-09-04 | M Deich | Turbine stage |
| JPH04127804U (en) * | 1991-05-10 | 1992-11-20 | 三菱重工業株式会社 | Vibration damping device for rotor blades |
| JP2000213303A (en) * | 1999-01-26 | 2000-08-02 | Ishikawajima Harima Heavy Ind Co Ltd | Blade damping method and blade damping structure |
| US6527509B2 (en) * | 1999-04-26 | 2003-03-04 | Hitachi, Ltd. | Turbo machines |
| JP2002221005A (en) * | 2001-01-26 | 2002-08-09 | Ishikawajima Harima Heavy Ind Co Ltd | Cooling turbine blade |
| JP4342840B2 (en) * | 2003-05-30 | 2009-10-14 | 株式会社東芝 | Steam turbine |
| US7018172B2 (en) * | 2003-12-22 | 2006-03-28 | United Technologies Corporation | Airfoil surface impedance modification for noise reduction in turbofan engines |
| US20090148273A1 (en) * | 2004-12-01 | 2009-06-11 | Suciu Gabriel L | Compressor inlet guide vane for tip turbine engine and corresponding control method |
| US20130064638A1 (en) * | 2011-09-08 | 2013-03-14 | Moorthi Subramaniyan | Boundary Layer Blowing Using Steam Seal Leakage Flow |
-
2012
- 2012-04-18 US US13/450,170 patent/US20130280050A1/en not_active Abandoned
-
2013
- 2013-04-16 EP EP13163840.5A patent/EP2653667A3/en not_active Withdrawn
- 2013-04-16 RU RU2013117262/06A patent/RU2013117262A/en not_active Application Discontinuation
- 2013-04-17 JP JP2013086179A patent/JP2013221522A/en active Pending
- 2013-04-18 CN CN201310135027.7A patent/CN103375183B/en not_active Expired - Fee Related
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4255083A (en) * | 1976-11-05 | 1981-03-10 | Societe Nationale D'etude Et De Construction De Moteurs D'aviation | Method and device for reducing the noise of turbo-machines |
| US4967550A (en) * | 1987-04-28 | 1990-11-06 | Rolls-Royce Plc | Active control of unsteady motion phenomena in turbomachinery |
| EP2204537A2 (en) * | 2008-12-31 | 2010-07-07 | Rolls-Royce North American Technologies, Inc. | Turbine vane for gas turbine engine |
Also Published As
| Publication number | Publication date |
|---|---|
| EP2653667A2 (en) | 2013-10-23 |
| US20130280050A1 (en) | 2013-10-24 |
| EP2653667A3 (en) | 2014-01-01 |
| RU2013117262A (en) | 2014-10-27 |
| CN103375183A (en) | 2013-10-30 |
| JP2013221522A (en) | 2013-10-28 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20160817 Termination date: 20170418 |