WO2008125677A1 - Gleichdruckturbine - Google Patents
Gleichdruckturbine Download PDFInfo
- Publication number
- WO2008125677A1 WO2008125677A1 PCT/EP2008/054561 EP2008054561W WO2008125677A1 WO 2008125677 A1 WO2008125677 A1 WO 2008125677A1 EP 2008054561 W EP2008054561 W EP 2008054561W WO 2008125677 A1 WO2008125677 A1 WO 2008125677A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- rotor
- pressure turbine
- guide
- guide vanes
- brush seals
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/16—Sealings between relatively-moving surfaces
- F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
- F16J15/3284—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings characterised by their structure; Selection of materials
- F16J15/3288—Filamentary structures, e.g. brush seals
-
- 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
- F01D1/00—Non-positive-displacement machines or engines, e.g. steam turbines
- F01D1/02—Non-positive-displacement machines or engines, e.g. steam turbines with stationary working-fluid guiding means and bladed or like rotor, e.g. multi-bladed impulse steam turbines
- F01D1/10—Non-positive-displacement machines or engines, e.g. steam turbines with stationary working-fluid guiding means and bladed or like rotor, e.g. multi-bladed impulse steam turbines having two or more stages subjected to working-fluid flow without essential intermediate pressure change, i.e. with velocity stages
-
- 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
- F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
- F01D11/001—Preventing or minimising internal leakage of working-fluid, e.g. between stages for sealing space between stator blade and rotor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/002—Sealings comprising at least two sealings in succession
- F16J15/006—Sealings comprising at least two sealings in succession with division of the pressure
-
- 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
- F05D2240/00—Components
- F05D2240/55—Seals
- F05D2240/56—Brush seals
Definitions
- the present invention relates to a constant pressure turbine.
- the principle of the constant pressure turbines has over the reaction principle of the overpressure turbines an efficiency advantage.
- the thermodynamics and flow technology of the constant pressure turbines require a larger shaft diameter than overpressure turbines.
- labyrinth seals are installed over the vanes and blades to seal the steam channel.
- the radial clearance of the seals is approximately the same for constant-pressure and high-pressure turbines.
- the minimum radial clearance of the seals is determined by the movement of the rotor in the bearings and the shaft vibrations. The game must be greater than the maximum rotor movement to avoid contact and thus damage.
- the diameter of the rotor is reduced in the region of the guide vanes, and a guide bottom is in each case mounted over the stationary guide vanes, the outer surface of which faces the rotor at a specific distance in accordance with the required radial play. In this way, the circumference of the gap and thus the gap surface is significantly reduced.
- the resulting disk-shaped carriers of the blades on the shaft are referred to as "wheel disks.”
- the resulting wheel friction losses between the guide plate and the wheel discs have a disadvantage and vanes completely lifted.
- this design brings considerable problems regarding the strength in the guide floor and a considerable cost overhead by the construction costs with it.
- the object of the present invention is to provide a constant-pressure turbine in which the leakage losses are minimized and at the same time the wheel friction between the guide plate and the guide blade is considerably reduced.
- this object is achieved by providing burst seals at the free ends of the guide vanes in the instantaneous pressure turbine according to the invention, which form an acute angle with the radial line with respect to the radial line in the direction of rotation of the rotor shaft.
- the brushes In contrast to the labyrinth seals made of rigid sheet metal, the brushes consist of a multitude of fine wires. Under a pressure differential, the wires lay tightly together forming a dense vapor impermeable bandage.
- baffle plate is arranged between the brush seals. With the help of the baffle plate a further reduction of the leakage current is possible.
- Figure 1 is a partial section through a conventional
- Figure 2 is a partial section through a constant pressure turbine according to the present invention.
- FIG. 1 shows parts of the housing 1 with the guide vanes 3 fastened thereto.
- the rotor blades 4 are fastened on the rotor shaft 2 and sealed relative to the housing 1.
- each vane 3 At the free end of each vane 3, a so-called guide bottom 5 is provided, which engages in a recess in the rotor shaft 2 Tor. Between the free end of the guide plate 5 and the rotor shaft 2 labyrinth seals 6 are provided.
- FIG. 2 shows a partial section through a constant pressure turbine according to the present invention.
- the vanes 9 are attached.
- the blades 10 are fixedly connected to the rotor shaft 8.
- the thickness of the shaft is not reduced in the region of the guide vanes.
- two brush seals 11 are provided.
- the brushes are made of a variety of fine wires.
- the wires attach tightly together forming a dense vapor impermeable dressing.
- the seal is touch tolerant. Due to the small radial gap of the brush seals, which is usually 5 to 7/100, in contrast to a radial gap in the labyrinth seal of a 3/10, the large leakage losses can be significantly reduced.
- a further reduction of the leakage results from the installation of a baffle plate 12 between the two brush seals.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Turbine Rotor Nozzle Sealing (AREA)
- Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
- Sealing Devices (AREA)
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
BRPI0810372-0A2A BRPI0810372A2 (pt) | 2007-04-17 | 2008-04-15 | Turbina de impulso |
US12/596,017 US20100129206A1 (en) | 2007-04-17 | 2008-04-15 | Impulse turbine |
JP2010503483A JP2010523902A (ja) | 2007-04-17 | 2008-04-15 | 衝動タービン |
EP08736247A EP2134926A1 (de) | 2007-04-17 | 2008-04-15 | Gleichdruckturbine |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102007018063.4 | 2007-04-17 | ||
DE102007018063A DE102007018063B4 (de) | 2007-04-17 | 2007-04-17 | Gleichdruckturbine |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2008125677A1 true WO2008125677A1 (de) | 2008-10-23 |
Family
ID=39588044
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2008/054561 WO2008125677A1 (de) | 2007-04-17 | 2008-04-15 | Gleichdruckturbine |
Country Status (7)
Country | Link |
---|---|
US (1) | US20100129206A1 (de) |
EP (1) | EP2134926A1 (de) |
JP (1) | JP2010523902A (de) |
CN (1) | CN101657608A (de) |
BR (1) | BRPI0810372A2 (de) |
DE (1) | DE102007018063B4 (de) |
WO (1) | WO2008125677A1 (de) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102008060706A1 (de) * | 2008-12-05 | 2010-06-10 | Man Turbo Ag | Düsensegment für eine Dampfturbine |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20130236302A1 (en) * | 2012-03-12 | 2013-09-12 | Charles Alexander Smith | In-situ gas turbine rotor blade and casing clearance control |
WO2016124262A1 (de) * | 2015-02-04 | 2016-08-11 | Siemens Aktiengesellschaft | Bürstendichtungsanordnung |
CN109441568B (zh) * | 2018-11-16 | 2024-04-19 | 华电电力科学研究院有限公司 | 一种高效率的低压隔板套装置及其装配方法 |
Citations (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE4446361A1 (de) * | 1994-12-23 | 1996-06-27 | Mtu Muenchen Gmbh | Bürstendichtung für Turbomaschine |
US6131910A (en) | 1992-11-19 | 2000-10-17 | General Electric Co. | Brush seals and combined labyrinth and brush seals for rotary machines |
US6318728B1 (en) | 1997-07-11 | 2001-11-20 | Demag Delaval Turbomachinery Corporation | Brush-seal designs for elastic fluid turbines |
US6669443B2 (en) | 2001-11-16 | 2003-12-30 | General Electric Company | Rotor platform modification and methods using brush seals in diaphragm packing area of steam turbines to eliminate rotor bowing |
US20040036227A1 (en) | 2002-08-26 | 2004-02-26 | General Electric Company | In situ load sharing brush seals |
US20050104300A1 (en) | 2003-10-14 | 2005-05-19 | Simon Hogg | Sealing arrangement using flexible seals |
US20060006603A1 (en) | 1999-04-06 | 2006-01-12 | Dalton William S | Brush seal designs for turbines and similar rotary apparatus |
US20060024156A1 (en) | 2004-07-29 | 2006-02-02 | Alstom Technology Ltd | Axial flow steam turbine assembly |
US20060088409A1 (en) * | 2004-10-21 | 2006-04-27 | General Electric Company | Grouped reaction nozzle tip shrouds with integrated seals |
EP1734230A1 (de) | 2005-06-13 | 2006-12-20 | Siemens Aktiengesellschaft | Thermische Strömungsmaschine |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6435514B1 (en) * | 2000-12-15 | 2002-08-20 | General Electric Company | Brush seal with positive adjustable clearance control |
GB0319002D0 (en) * | 2003-05-13 | 2003-09-17 | Alstom Switzerland Ltd | Improvements in or relating to steam turbines |
GB0416932D0 (en) * | 2004-07-29 | 2004-09-01 | Alstom Technology Ltd | Axial flow steam turbine assembly |
US7549835B2 (en) * | 2006-07-07 | 2009-06-23 | Siemens Energy, Inc. | Leakage flow control and seal wear minimization system for a turbine engine |
-
2007
- 2007-04-17 DE DE102007018063A patent/DE102007018063B4/de not_active Expired - Fee Related
-
2008
- 2008-04-15 JP JP2010503483A patent/JP2010523902A/ja active Pending
- 2008-04-15 US US12/596,017 patent/US20100129206A1/en not_active Abandoned
- 2008-04-15 EP EP08736247A patent/EP2134926A1/de not_active Withdrawn
- 2008-04-15 BR BRPI0810372-0A2A patent/BRPI0810372A2/pt not_active IP Right Cessation
- 2008-04-15 WO PCT/EP2008/054561 patent/WO2008125677A1/de active Application Filing
- 2008-04-15 CN CN200880012399A patent/CN101657608A/zh active Pending
Patent Citations (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6131910A (en) | 1992-11-19 | 2000-10-17 | General Electric Co. | Brush seals and combined labyrinth and brush seals for rotary machines |
DE4446361A1 (de) * | 1994-12-23 | 1996-06-27 | Mtu Muenchen Gmbh | Bürstendichtung für Turbomaschine |
US6318728B1 (en) | 1997-07-11 | 2001-11-20 | Demag Delaval Turbomachinery Corporation | Brush-seal designs for elastic fluid turbines |
US20060006603A1 (en) | 1999-04-06 | 2006-01-12 | Dalton William S | Brush seal designs for turbines and similar rotary apparatus |
US6669443B2 (en) | 2001-11-16 | 2003-12-30 | General Electric Company | Rotor platform modification and methods using brush seals in diaphragm packing area of steam turbines to eliminate rotor bowing |
US20040036227A1 (en) | 2002-08-26 | 2004-02-26 | General Electric Company | In situ load sharing brush seals |
US20050104300A1 (en) | 2003-10-14 | 2005-05-19 | Simon Hogg | Sealing arrangement using flexible seals |
US20060024156A1 (en) | 2004-07-29 | 2006-02-02 | Alstom Technology Ltd | Axial flow steam turbine assembly |
US20060088409A1 (en) * | 2004-10-21 | 2006-04-27 | General Electric Company | Grouped reaction nozzle tip shrouds with integrated seals |
EP1734230A1 (de) | 2005-06-13 | 2006-12-20 | Siemens Aktiengesellschaft | Thermische Strömungsmaschine |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102008060706A1 (de) * | 2008-12-05 | 2010-06-10 | Man Turbo Ag | Düsensegment für eine Dampfturbine |
Also Published As
Publication number | Publication date |
---|---|
BRPI0810372A2 (pt) | 2014-10-29 |
CN101657608A (zh) | 2010-02-24 |
DE102007018063B4 (de) | 2012-02-09 |
EP2134926A1 (de) | 2009-12-23 |
JP2010523902A (ja) | 2010-07-15 |
US20100129206A1 (en) | 2010-05-27 |
DE102007018063A1 (de) | 2008-10-23 |
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