EP0891471A1 - Verfahren und vorrichtung zum schubausgleich bei einer turbomaschine - Google Patents
Verfahren und vorrichtung zum schubausgleich bei einer turbomaschineInfo
- Publication number
- EP0891471A1 EP0891471A1 EP97918065A EP97918065A EP0891471A1 EP 0891471 A1 EP0891471 A1 EP 0891471A1 EP 97918065 A EP97918065 A EP 97918065A EP 97918065 A EP97918065 A EP 97918065A EP 0891471 A1 EP0891471 A1 EP 0891471A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pressure
- inner housing
- thrust compensation
- axial
- turbo machine
- 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.)
- Granted
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
- F01D25/24—Casings; Casing parts, e.g. diaphragms, casing fastenings
- F01D25/26—Double casings; Measures against temperature strain in casings
-
- 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
- F01D25/24—Casings; Casing parts, e.g. diaphragms, casing fastenings
- F01D25/26—Double casings; Measures against temperature strain in casings
- F01D25/265—Vertically split casings; Clamping arrangements 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
- F01D3/00—Machines or engines with axial-thrust balancing effected by working-fluid
- F01D3/04—Machines or engines with axial-thrust balancing effected by working-fluid axial thrust being compensated by thrust-balancing dummy piston or the like
Definitions
- the present invention relates to a method and a device in a turbomachine with an outer and an inner housing or guide vane carrier for thrust compensation.
- the field of application of the invention is in pot-type turbo-engines, the pressure of a fluid flowing through the turbo-machine causing an axial force in the longitudinal direction of the shaft at least on the inner housing.
- DE 22 18 500 describes a multi-shell casing of a steam turbine for high steam pressures and steam temperatures.
- the live steam enters the inner housing at high pressure. After an expansion of approximately 20% of the total gradient of the partial turbine, the steam is led through bores into the outer casing and thus compresses the inner casing in the area of the parting joints in the area of the further expansion course.
- the design with a guide vane carrier is selected. The full live steam pressure is present in the space between the inner and outer housing and thus presses the two carrier halves together.
- the term “inner housing” always also includes the constructive solution with guide vane carrier.
- the pressures acting on various surfaces continue to provide a resulting thrust on the components in their superposition, which must be absorbed by corresponding devices on the inner housing and / or outer housing and / or on the shaft.
- the space between the inner and outer housing against the exit side of the through Fluid flowing through the turbomachine is sealed, so that the differential pressure between the inlet and outlet has to be taken up by the inner housing, while the outer housing has to withstand the outlet pressure on the downstream side and the pressure between the outer and inner housing against the atmospheric pressure.
- the pressures prevailing in the various rooms of a turbo machine ensure high axial forces, which are transmitted through appropriate devices, such as. B. bayonet rings, threaded rings, Uhde board cutter closures or screw connections must be transferred to the outer housing or other suitable devices. In addition to possible large deformations, these forces also cause high surface pressures on corresponding supports.
- the object of the present invention is therefore to create a method for thrust compensation in a turbomachine and a corresponding embodiment of the same.
- the invention is intended to compensate for axial forces occurring in the longitudinal direction of the shaft.
- the invention provides that at least a first surface of the exterior of a part of the inner housing for axial thrust compensation is subdivided into two partial surfaces for axial thrust compensation, which are each subjected to different pressures, with a delimitation between the two pressures by at least one Means, in particular a seal, is caused.
- the outside of a part of the inner housing is preferably subjected to a pressure for axial thrust compensation, which is at least as large as the outlet pressure of the fluid, and preferably approximately as large as the inlet pressure.
- the pressure for axial thrust compensation counteracts the axial force of the outlet pressure on the inner housing.
- the result of the overlapping of both pressures is a reduced resulting pressure, which therefore also causes less thrust.
- This axial thrust compensation can be carried out in particular on the inner housing of the turbomachine. It is thereby achieved that the previous high construction costs for fixing the inner housing can be reduced. The surface pressures occurring on the fixing elements are therefore lower and therefore lead also to smaller deformations.
- the pressure on the outer part of the inner housing is set according to the operating conditions, such as full or partial load. The axial thrust occurring on the inner housing can then be adjusted by suitable control of the pressure.
- the dimensions of this outer part are further limited by the suitable means, preferably a seal.
- the axial thrust compensation of the inner housing can thus be influenced not only by the pressure, but also by the effective surface available for the pressure to form an axial force.
- This acting surface as the first surface is now divided into the two partial surfaces by the mean.
- the active surface preferably comprises at least part of the outer end face of the inner housing.
- the axial thrust can also be adjusted by varying the areas, determined by means of the diameter of one or two I-ring seals.
- the seal itself is thus pressurized and in particular loaded. Because of the seal, the pressure acting on both partial surfaces can also be applied between the inner and outer housing.
- FIG. 1 shows a stationary high-pressure turbine according to the invention in pot design and Figure 2 shows a schematic arrangement of a turbine train.
- FIG. 1 shows, as an exemplary embodiment of a turbomachine 1 according to the invention, a high-pressure turbine 1 in pot design, which has an inner housing 2 and an outer housing 3.
- the fluid 4 flowing through the turbomachine 1 enters with the inlet pressure P1 and leaves the high-pressure turbine 1 again with the outlet pressure P2.
- the pressure difference between the inlet and the outlet pressure leads to an axial thrust not only on the inner housing 2 but also on the shaft 5.
- the inner housing 2 has on its outside a surface AI which is subjected to the inlet pressure Pl.
- a pressure on the surface AI is preferably at least as large as the outlet pressure P2 of the fluid 4 from the turbomachine 1.
- the pressure on the surface AI can also be as large as the inlet pressure of the fluid and / or a pressure in the interior of the inner housing Be 2.
- the surface AI preferably comprises a part of the end face of the inner housing 2.
- the axial thrust which arises on this surface AI superimposes the axial force on the inner housing 2 which arises on the surface A2 ', as a result of which axial thrust compensation takes place on the latter.
- the fixation 6 of the inner housing 2 relative to the outer housing 3 is subject to lower surface pressures due to this axial thrust compensation. This allows a variety of construction options for introducing an axial thrust force into the outer housing 3, e.g. B. can in the previous state of
- the axial pressure-transmitting surface AI of the outer part of the inner housing 2 limited by a arranged around the shaft 5 means 7.
- This means 7 advantageously a seal, limits the pressure P1 to the axial pressure-transmitting surface AI so that a precisely defined axial thrust compensation can take place by using the means 7.
- the use of such a means 7 offers the possibility of applying a further pressure P3 to a further surface A3 on the outer part of the inner housing 2.
- the pressure P3 in connection with the surface A3 then also makes a contribution to the axial thrust compensation.
- the surfaces AI and A3 together therefore form a first surface of the outer part of the inner housing 2 in the sense of the invention.
- the areas AI and A3 individually are the partial areas.
- the pressure P3 which is advantageously lower than the pressure Pl, serves as a barrier pressure. Pressure and flow losses over the seal or seals as means 7 can be reduced by means of this advantageous pressure step. As a result, the seal, in particular an I-ring seal, can not only be pressurized, but also with the
- seal 7 is advantageously attached between the inner part of the outer housing 3 and the outer part of the inner housing 2, in particular in such a way that it has direct contact with the inner housing 2 and the outer housing 3.
- a seal 7 is an I-ring seal, whose
- Diameter D depends on the area A1 or A3 which transmits the desired axial force.
- An advantageous embodiment of the invention provides that axial thrust compensation takes place not only on the inner housing 2 but also on the shaft 5.
- the turbomachine is designed in such a way that the outlet pressure P2 is applied to an area A2 ′′ transmitting axial pressure. So, because of the Pressure difference between the inlet pressure Pl and the outlet pressure P2 above the blades, axial thrust occurring on the shaft 5 can be at least partially compensated for.
- FIG. 2 shows a schematic illustration of the arrangement of a high-pressure part HD, a medium-pressure part MD and a low-pressure part ND of a turbine on a shaft.
- This illustration shows that the forces from the pressure Pl on the surface AI and from the pressure P3 on the surface A3 act in the negative X direction.
- the force from the pressure P2 on the surface A2 ′′ counteracts these forces in the positive X direction.
- the invention can thus be used not only on a partial turbine, but rather also on a line of turbomachines connected in series for axial thrust compensation.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Turbine Rotor Nozzle Sealing (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Basic Packing Technique (AREA)
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19614335 | 1996-04-11 | ||
DE19614335 | 1996-04-11 | ||
PCT/DE1997/000674 WO1997038209A1 (de) | 1996-04-11 | 1997-04-02 | Verfahren und vorrichtung zum schubausgleich bei einer turbomaschine |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0891471A1 true EP0891471A1 (de) | 1999-01-20 |
EP0891471B1 EP0891471B1 (de) | 2002-06-26 |
Family
ID=7791006
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP97918065A Expired - Lifetime EP0891471B1 (de) | 1996-04-11 | 1997-04-02 | Verfahren und vorrichtung zum schubausgleich bei einer turbomaschine |
Country Status (11)
Country | Link |
---|---|
US (1) | US6213710B1 (de) |
EP (1) | EP0891471B1 (de) |
JP (1) | JP2000508040A (de) |
KR (1) | KR20000005303A (de) |
CN (1) | CN1081724C (de) |
AT (1) | ATE219816T1 (de) |
CZ (1) | CZ326498A3 (de) |
DE (1) | DE59707599D1 (de) |
PL (1) | PL183594B1 (de) |
RU (1) | RU2175721C2 (de) |
WO (1) | WO1997038209A1 (de) |
Families Citing this family (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO1999023359A1 (de) * | 1997-11-03 | 1999-05-14 | Siemens Aktiengesellschaft | Turbinengehäuse sowie verfahren zu dessen herstellung |
JP3986873B2 (ja) * | 2001-05-08 | 2007-10-03 | 花王株式会社 | 液体洗浄剤組成物 |
ES2267655T3 (es) * | 2001-11-22 | 2007-03-16 | Siemens Aktiengesellschaft | Metodo de fabricacion de turbinas de vapor. |
JP2006016976A (ja) * | 2004-06-30 | 2006-01-19 | Toshiba Corp | タービンノズル支持装置および蒸気タービン |
US8256575B2 (en) * | 2007-08-22 | 2012-09-04 | General Electric Company | Methods and systems for sealing rotating machines |
WO2009123301A2 (en) * | 2008-03-31 | 2009-10-08 | Mitsubishi Heavy Industries, Ltd. | Rotary machine |
DE102008022966B4 (de) * | 2008-05-09 | 2014-12-24 | Siemens Aktiengesellschaft | Rotationsmaschine |
EP2192266A1 (de) * | 2008-11-26 | 2010-06-02 | Siemens Aktiengesellschaft | Rotorvorrichtung für eine Dampfturbine und Dampfturbine |
JP2010174795A (ja) * | 2009-01-30 | 2010-08-12 | Mitsubishi Heavy Ind Ltd | タービン |
CH701914A1 (de) * | 2009-09-30 | 2011-03-31 | Alstom Technology Ltd | Dampfturbine mit Entlastungsnut am Rotor im Bereich des Schubausgleichskolbens. |
EP2333253A1 (de) * | 2009-12-08 | 2011-06-15 | Siemens Aktiengesellschaft | Innengehäuse für eine Strömungsmaschine |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE281253C (de) * | ||||
FR1094273A (fr) * | 1953-08-31 | 1955-05-16 | Siemens Ag | Turbine à double enveloppe fonctionnant à forte pression d'échappement |
DE1152703B (de) * | 1959-12-14 | 1963-08-14 | Licentia Gmbh | Vielstufige Gleichdruckturbine |
JPS5227282B2 (de) | 1970-11-05 | 1977-07-19 | ||
DE2218500B2 (de) * | 1972-04-17 | 1974-01-31 | Kraftwerk Union AG, 4330 Mülheim | Mehrschaliges gehaeuse einer dampfturbine fuer hohe dampfdruecke und dampftemperaturen |
JPS59213907A (ja) * | 1983-05-19 | 1984-12-03 | Fuji Electric Co Ltd | つぼ型タ−ビン |
-
1997
- 1997-04-02 KR KR1019980708015A patent/KR20000005303A/ko active IP Right Grant
- 1997-04-02 DE DE59707599T patent/DE59707599D1/de not_active Expired - Lifetime
- 1997-04-02 WO PCT/DE1997/000674 patent/WO1997038209A1/de active IP Right Grant
- 1997-04-02 EP EP97918065A patent/EP0891471B1/de not_active Expired - Lifetime
- 1997-04-02 CN CN97193662A patent/CN1081724C/zh not_active Expired - Lifetime
- 1997-04-02 JP JP9535741A patent/JP2000508040A/ja active Pending
- 1997-04-02 CZ CZ983264A patent/CZ326498A3/cs unknown
- 1997-04-02 AT AT97918065T patent/ATE219816T1/de not_active IP Right Cessation
- 1997-04-02 RU RU98120399/06A patent/RU2175721C2/ru not_active IP Right Cessation
- 1997-04-02 PL PL97329236A patent/PL183594B1/pl not_active IP Right Cessation
-
1998
- 1998-10-13 US US09/170,183 patent/US6213710B1/en not_active Expired - Lifetime
Non-Patent Citations (1)
Title |
---|
See references of WO9738209A1 * |
Also Published As
Publication number | Publication date |
---|---|
JP2000508040A (ja) | 2000-06-27 |
RU2175721C2 (ru) | 2001-11-10 |
ATE219816T1 (de) | 2002-07-15 |
EP0891471B1 (de) | 2002-06-26 |
KR20000005303A (ko) | 2000-01-25 |
US6213710B1 (en) | 2001-04-10 |
PL329236A1 (en) | 1999-03-15 |
CN1081724C (zh) | 2002-03-27 |
CN1215449A (zh) | 1999-04-28 |
PL183594B1 (pl) | 2002-06-28 |
WO1997038209A1 (de) | 1997-10-16 |
DE59707599D1 (de) | 2002-08-01 |
CZ326498A3 (cs) | 1999-02-17 |
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