EP0906494A1 - Turbine shaft and process for cooling it - Google Patents

Turbine shaft and process for cooling it

Info

Publication number
EP0906494A1
EP0906494A1 EP97923804A EP97923804A EP0906494A1 EP 0906494 A1 EP0906494 A1 EP 0906494A1 EP 97923804 A EP97923804 A EP 97923804A EP 97923804 A EP97923804 A EP 97923804A EP 0906494 A1 EP0906494 A1 EP 0906494A1
Authority
EP
European Patent Office
Prior art keywords
shaft
turbine shaft
turbine
flow
steam
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
Application number
EP97923804A
Other languages
German (de)
French (fr)
Other versions
EP0906494B1 (en
Inventor
Andreas FELDMÜLLER
Helmut Pollak
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Siemens AG
Siemens Corp
Original Assignee
Siemens AG
Siemens Corp
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Siemens AG, Siemens Corp filed Critical Siemens AG
Publication of EP0906494A1 publication Critical patent/EP0906494A1/en
Application granted granted Critical
Publication of EP0906494B1 publication Critical patent/EP0906494B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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
    • F01D9/00—Stators
    • F01D9/06—Fluid supply conduits to nozzles or the like
    • F01D9/065—Fluid supply or removal conduits traversing the working fluid flow, e.g. for lubrication-, cooling-, or sealing fluids
    • 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
    • F01D3/02—Machines or engines with axial-thrust balancing effected by working-fluid characterised by having one fluid flow in one axial direction and another fluid flow in the opposite direction
    • 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
    • F01D5/08—Heating, heat-insulating or cooling means

Definitions

  • the invention relates to a turbine shaft, which extends along a main axis and has an outer surface, and to a method for cooling a turbine shaft.
  • EP 0 088 944 B1 describes a shaft shield with swirl cooling for a region of a turbine shaft to which the live steam is exposed immediately after flowing into the turbine.
  • swirl cooling steam flows through four tangential bores in the shaft shield in the direction of rotation of the turbine shaft into the area between the shaft shield and the turbine shaft. The steam expands, the temperature drops, which cools the turbine shaft.
  • the shaft shield is connected to a row of guide vanes in a vapor-tight manner. Due to the swirl cooling, the temperature of the turbine shaft in the vicinity of the rotor shield can be reduced by approximately 15 K.
  • nozzles are introduced for the swirl cooling, which, seen in the direction of rotation of the turbine shaft, open tangentially into the ring channel formed between the turbine shaft and the shaft shield.
  • the object of the invention is to provide a turbine shaft which can be cooled in a region which can withstand high thermal loads. Another object of the invention is to provide a drive to cool a turbine shaft arranged in a turbine.
  • the object directed to a turbine shaft, which extends along a main axis and has an outer surface, is achieved in that the turbine shaft has a plurality of cylindrical shaft segments arranged axially one behind the other along the main axis, each of which has a connecting axis along a common connecting axis. Have opening through which a bracing element is guided. An axial gap is formed between the tensioning element and at least one shaft segment, which is fluidically connected to two axially spaced radial channels, in particular gaps, which each open on the outer surface.
  • cooling fluid can be introduced into the interior of the turbine shaft and can be passed through the axial gap through the turbine shaft in the axial direction, so that cooling of the turbine shaft in the region of the axial gap is ensured.
  • the cooling fluid is preferably an action fluid (process steam), which sets the turbine shaft into rotation by an inflow of rotor blades connected to the turbine shaft.
  • the radial channels preferably open at different pressure levels on the outer surface of the turbine shaft, so that a flow through the turbine shaft is automatically formed even by the pressure gradient.
  • the volume flow of the cooling fluid which is branched off from the action fluid can be adapted to the required cooling capacity.
  • the action fluid (process steam) withdrawn for cooling only does so via the fluid present between the radial channels Differential pressure level no mechanical work to drive the turbine shaft. After flowing out through the radial channel at a lower pressure level back into the flow of the action fluid, the action fluid used as the cooling fluid again does mechanical work and thus contributes to the efficiency of the steam turbine.
  • the cylindrical shaft segments also referred to below as rotor disks, preferably each have a central connection opening through which a single connection element, a tie rod, is guided.
  • the connection opening has a larger cross section than the tie rod, so that preferably an annular axial gap is formed between the shaft segment and the tie rod for the flow of cooling fluid.
  • connection elements rods
  • the respective connection axis of the connection elements is parallel to the main axis of the turbine shaft.
  • the respective connecting axes are preferably arranged on a circle, the center of which coincides with the main axis.
  • At least one radial channel is preferably formed between two directly adjacent shaft segments. This is achieved, for example, in that corresponding recesses or recesses, grooves, are provided in the mutually adjacent shaft segments.
  • a radial channel can, however, also be realized through an essentially radial bore through the shaft segment from the outer surface to the connection opening.
  • radial preferably means perpendicular to the main axis, but also includes any connection between the outer surface and the connection opening which is at least partially directed in the direction of the main axis.
  • the turbine shaft is preferably provided for a double-flow turbine and accordingly has an axial central region, to which the action fluid reaches the turbine immediately after it has flowed in and is divided there into two essentially equal partial flows.
  • the axial central region is preferably arranged axially between the radial channels.
  • the central region, which is exposed to the action fluid at a highest temperature, preferably has a cavity through which cooling fluid can flow.
  • the cavity is preferably rotationally symmetrical to the
  • Main axis trained It is closed off by a shielding element which has a rotationally symmetrical elevation for current division.
  • the cavity can be connected to the axial gap in terms of flow technology. It is also possible to supply cooling fluid via the housing of a turbine and a holder which fixes the shielding element to the housing.
  • the turbine shaft is preferably arranged in a steam turbine, in particular a double-flow medium-pressure partial turbine. Cooling of the central region of the turbine shaft is ensured by the flow path formed over the central region, comprising the two axially spaced radial ducts and the axial duct connected therewith in terms of flow technology. In particular arrives as
  • Action fluid acting as cooling fluid from the partial flow of one flood at a lower pressure level into the partial stream of the second flood.
  • the action fluid used as the cooling fluid is fed back into the entire steam process and thus contributes to the efficiency of the overall process.
  • the object directed to a method for cooling a turbine shaft is achieved in that in the case of a turbine shaft with a plurality of cylindrical shaft segments arranged axially one behind the other along a main axis and braced with one another by a bracing element, cooling fluid through a first radial channel into an axial gap between the bracing element and the shaft segment and is led out of the turbine shaft through a second radial channel.
  • this allows a turbine shaft to be cooled from the inside in a region which is thermally highly stressed during operation of the turbine shaft.
  • Such a turbine shaft is therefore also suitable in a steam turbine plant with steam inlet temperatures above 600 ° C.
  • a volume flow of cooling fluid is fed to the axial gap, which is between 1% to 4%, in particular between 1.5% and 3%, of the total live steam volume flow.
  • the single figure shows a longitudinal section of a section of a turbine with a turbine shaft.
  • a turbine shaft 1 is arranged in a housing 18.
  • the turbine shaft 1 extends along a main axis 2 and has a plurality of shaft segments 4a, 4b, 4c, 4d, 4e arranged axially one behind the other.
  • Each shaft segment 4a, 4b has a respective connection opening 6 around the main axis 2.
  • the connection openings 6 each have the same cross section and are arranged centrally to one another and to the main axis 2.
  • a bracing element 7, a tie rod is guided through the connecting openings 6 along a connecting axis 5.
  • the connection axis 5 coincides with the main axis 2.
  • the tie rod 7 attacks the outermost, not shown, shaft segments so that the shaft elements 4a, 4b, 4c, 4d are braced axially to one another.
  • the tie rod 7 preferably has a thread, not shown, in which a clamping nut, also not shown, engages.
  • a spur tooth coupling in particular a serration toothing (serration toothing).
  • connection openings 6 each have a cross section which is larger than the cross section of the tie rod 7, so that an axial gap 8, in particular an annular gap, remains between a respective shaft segment 4a and the tie rod 7.
  • An outer surface 3 of the turbine shaft 1 is formed by the shaft segments 4a, 4b, etc. In the vicinity of the outer surface 3, adjacent shaft segments 4a, 4d; 4a, 4b connected to one another by a respective sealing weld 16 impervious to a fluid.
  • two pairs of adjacent shaft segments 4d, 4e; 4b, 4c are arranged so that a respective radial channel 9a, 9b remains between them.
  • the housing 18 surrounding the turbine shaft 1 has an inflow region 19 for live steam 12.
  • the turbine shaft 1 Associated with the inflow region 19, the turbine shaft 1 has a central region 11 in which a cavity 13 is formed.
  • This cavity 13 and the central region 11 of the turbine shaft 1 are shielded against a hot action fluid 12 (live steam) flowing through the inflow region 19 by a shielding element 17 from direct contact with the action fluid 12.
  • the shielding element 17 is rotationally symmetrical to the main axis 2 and has an elevation directed away from the main axis 2.
  • the shielding element 17 serves to divide the action fluid 12, the live steam, into two approximately equal partial flows.
  • the shielding element 17 is connected to the housing 18 via the first row of guide vanes 14 of each partial flow.
  • cooling fluid feeds By not provided cooling fluid feeds, cooling fluid passes through the housing 18, the first row of guide vanes 14 and the shielding element 17 into the cavity 13 and there causes cooling of the turbine shaft 1 in the central region 11.
  • the cooling fluid can flow into the cavity 13 due to the heat exchange are heated with the action fluid 12 and are fed back to the steam process via fluid discharge lines, not shown.
  • rotor blade rows 15 and guide vane rows 14 connected to the turbine shaft 1 are arranged alternately axially one behind the other. Cooling of the turbine shaft 1 also from the inside, in particular in the central region 11, is achieved in that the first radial channel 9a already releases somewhat relaxed actuation fluid 12 into the axial gap 8 between the tie rod 7 and shaft segments 4d, 4a, 4b flows in.
  • This partial flow of the action fluid 12 acts as a cooling fluid 12b, which is first conducted against the direction of flow of the partial flow flowing on the left in the illustration.
  • Cooling fluid 12b is discharged through the first radial channel 9a at a pressure of approximately 11 bar and a temperature of approximately 400 ° C. from the partial flow directed to the left and fed back to the partial flow directed to the right at a pressure level less than 11 bar. It is also possible to connect the axial gap 8 to the cavity 13 in terms of flow technology for the purpose of cooling. A volume fraction of 1% to 4%, in particular 1.5% to 3%, of the total live steam volume flow which drives the turbine shaft is preferably fed to the axial gap 8.
  • the invention is characterized by a turbine shaft, which has a plurality of shaft segments arranged axially one behind the other and braced with one another, in the interior of which an axially directed gap is provided.
  • This gap is fluidically connected to the flow of the action fluid driving the turbine shaft via two radial channels at two different pressure levels.
  • the radial channels are preferably located where two shaft segments adjoin each other.
  • a pressure-difference-operated cooling fluid flow is branched off from the action fluid (live steam).
  • a cooling steam flow branched off from the live steam flow arrives via the first radial channel into the axially directed gap and from there via the second radial channel back into the live steam flow.
  • the region of the turbine shaft adjacent to the axial gap is cooled from the inside and the cooling fluid used for the cooling is fed back to the entire steam process.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
  • Motor Or Generator Cooling System (AREA)
  • Heat Treatment Of Articles (AREA)

Abstract

A turbine shaft extends along a principal axis and has an outer surface. The turbine shaft is formed by a plurality of cylindrical shaft segments which are disposed axially one behind the other and are braced together by a bracing element. An axial gap which is formed between the bracing element and at least one shaft segment is connected in terms of flow to two axially spaced radial passages. The radial passages each open at the outer surface of the turbine shaft. A method for cooling a turbine shaft is also provided.

Description

Beschreibungdescription

Turbinenwelle sowie Verfahren zur Kühlung einer TurbinenwelleTurbine shaft and method for cooling a turbine shaft

Die Erfindung betrifft eine Turbinenwelle, welche sich ent¬ lang einer Hauptachse erstreckt und eine Außenoberfläche auf¬ weist, sowie ein Verfahren zur Kühlung einer Turbinenwelle.The invention relates to a turbine shaft, which extends along a main axis and has an outer surface, and to a method for cooling a turbine shaft.

Zur Steigerung des Wirkungsgrades einer Dampfturbine trägt die Verwendung von Dampf mit höheren Drücken und Temperaturen bei, insbesondere sogenannte überkritische Dampfzustände, mit einer Temperatur von beispielsweise über 550 °C. Die Verwen¬ dung von Dampf mit einem solchen Dampfzustand stellt erhöhte Anforderungen an eine entsprechend beaufschlagte Turbinen- welle einer Dampfturbine.The use of steam at higher pressures and temperatures, in particular so-called supercritical steam conditions with a temperature of, for example, above 550 ° C., contributes to increasing the efficiency of a steam turbine. The use of steam with such a steam state places increased demands on a turbine shaft of a steam turbine which is acted upon accordingly.

In der DE 32 09 506 AI, hierzu korrespondiert dieIn DE 32 09 506 AI, this corresponds to

EP 0 088 944 Bl, ist eine Wellenabschirmung mit Drallkühlung für einen Bereich einer Turbinenwelle beschrieben, der der Frischdampf unmittelbar nach Einströmen in die Turbine ausge¬ setzt ist. Bei der Drallkühlung strömt Dampf durch vier tan- gentiale Bohrungen der Wellenabschirmung in Drehrichtung der Turbinenwelle in den Bereich zwischen der Wellenabschirmung und der Turbinenwelle ein. Dabei expandiert der Dampf, die Temperatur sinkt, wodurch die Turbinenwelle gekühlt wird. Die Wellenabschirmung ist dampfdicht mit einer Leitschaufelreihe verbunden. Durch die Drallkühlung läßt sich eine Temperatur- absenkung der Turbinenwelle in der Umgebung der Läuferab¬ schirmung von etwa 15 K erreichen. In der Wellenabschirmung sind für die Drallkühlung Düsen eingebracht, welche in Dreh¬ richtung der Turbinenwelle gesehen tangential in den zwischen der Turbinenwelle und der Wellenabschirmung gebildeten Ring¬ kanal einmünden.EP 0 088 944 B1 describes a shaft shield with swirl cooling for a region of a turbine shaft to which the live steam is exposed immediately after flowing into the turbine. During swirl cooling, steam flows through four tangential bores in the shaft shield in the direction of rotation of the turbine shaft into the area between the shaft shield and the turbine shaft. The steam expands, the temperature drops, which cools the turbine shaft. The shaft shield is connected to a row of guide vanes in a vapor-tight manner. Due to the swirl cooling, the temperature of the turbine shaft in the vicinity of the rotor shield can be reduced by approximately 15 K. In the shaft shield, nozzles are introduced for the swirl cooling, which, seen in the direction of rotation of the turbine shaft, open tangentially into the ring channel formed between the turbine shaft and the shaft shield.

Aufgabe der Erfindung ist es, eine Turbinenwelle anzugeben, welche in einem thermisch hoch belastbaren Bereich kühlbar ist. Eine weitere Aufgabe der Erfindung liegt darin, ein Ver- fahren zur Kühlung einer in einer Turbine angeordneten Turbi¬ nenwelle anzugeben.The object of the invention is to provide a turbine shaft which can be cooled in a region which can withstand high thermal loads. Another object of the invention is to provide a drive to cool a turbine shaft arranged in a turbine.

Die auf eine Turbinenwelle, welche sich entlang einer Hauptachse erstreckt und eine Außenoberfläche aufweist, ge¬ richtete Aufgabe wird dadurch gelöst, daß die Turbinenwelle eine Mehrzahl entlang der Hauptachse axial hintereinander an¬ geordneter zylindrischer Wellensegmente aufweist, die entlang einer gemeinsamen Verbindungsachse jeweils eine Verbindungs- Öffnung aufweisen, durch welche ein Verspannungselement ge¬ führt ist. Zwischen dem Verspannungselement und zumindest ei¬ nem Wellensegment ist ein axialer Spalt gebildet, der mit zwei axial voneinander beabstandeten radialen Kanälen, insbe¬ sondere Spalten, strömungstechnisch verbunden ist, die je- weils an der Außenoberfläche münden.The object directed to a turbine shaft, which extends along a main axis and has an outer surface, is achieved in that the turbine shaft has a plurality of cylindrical shaft segments arranged axially one behind the other along the main axis, each of which has a connecting axis along a common connecting axis. Have opening through which a bracing element is guided. An axial gap is formed between the tensioning element and at least one shaft segment, which is fluidically connected to two axially spaced radial channels, in particular gaps, which each open on the outer surface.

Bei einer solchen Turbinenwelle ist mithin eine strömungs- technische Verbindung zwischen der Außenoberfläche der Turbi¬ nenwelle und einem in ihrem Inneren liegenden axialen Spalt gebildet. Dadurch kann Kühlfluid in das Innere der Turbinen¬ welle eingeführt und durch den axialen Spalt in axialer Rich¬ tung durch die Turbinenwelle hindurchgeführt werden, so daß eine Kühlung der Turbinenwelle im Bereich des axialen Spaltes gewährleistet ist. Bei einer Dampfturbine ist hierbei das Kühlfluid vorzugsweise ein Aktionsfluid (Prozeßdampf) , wel¬ ches durch eine Anströmung von mit der Turbinenwelle verbun¬ denen Laufschaufeln die Turbinenwelle in eine Rotation ver¬ setzt. Die radialen Kanäle münden vorzugsweise an unter¬ schiedlichen Druckniveaus an der Außenoberfläche der Turbi- nenwelle, so daß sich bereits durch das Druckgefälle automa¬ tisch eine Strömung durch die Turbinenwelle hindurch ausbil¬ det. Durch die geometrische Anordnung der Mündung der radia¬ len Kanäle an die Außenoberfläche kann der Volumenstrom des Kühlfluides, welches aus dem Aktionsfluid abgezweigt wird, an die geforderte Kühlleistung angepaßt werden. Das zur Kühlung entzogene Aktionsfluid (Prozeßdampf) verrichtet hierbei le¬ diglich über das zwischen den radialen Kanälen vorhandene Differenzdruckniveau keine mechanische Arbeit zum Antrieb der Turbinenwelle. Nach Ausströmen durch den radialen Kanal mit niedrigerem Druckniveau zurück in den Strom des Aktionsflui- des verrichtet auch das als Kühlfluid verwendete Aktionsfluid erneut mechanische Arbeit und trägt somit zu dem Wirkungsgrad der Dampfturbine bei.In the case of such a turbine shaft, a fluidic connection is therefore formed between the outer surface of the turbine shaft and an axial gap located in its interior. As a result, cooling fluid can be introduced into the interior of the turbine shaft and can be passed through the axial gap through the turbine shaft in the axial direction, so that cooling of the turbine shaft in the region of the axial gap is ensured. In the case of a steam turbine, the cooling fluid is preferably an action fluid (process steam), which sets the turbine shaft into rotation by an inflow of rotor blades connected to the turbine shaft. The radial channels preferably open at different pressure levels on the outer surface of the turbine shaft, so that a flow through the turbine shaft is automatically formed even by the pressure gradient. Due to the geometrical arrangement of the opening of the radial channels on the outer surface, the volume flow of the cooling fluid which is branched off from the action fluid can be adapted to the required cooling capacity. The action fluid (process steam) withdrawn for cooling only does so via the fluid present between the radial channels Differential pressure level no mechanical work to drive the turbine shaft. After flowing out through the radial channel at a lower pressure level back into the flow of the action fluid, the action fluid used as the cooling fluid again does mechanical work and thus contributes to the efficiency of the steam turbine.

Die zylindrischen Wellensegmente, im folgenden auch als Läu¬ ferscheiben bezeichnet, weisen vorzugsweise jeweils eine zen- trale Verbindungsöffnung auf, durch die ein einziges Verbin¬ dungselement, ein Zuganker, geführt ist. Die Verbindungsöff¬ nung hat hierbei einen größeren Querschnitt als der Zuganker, so daß vorzugsweise ein ringförmiger axialer Spalt zwischen Wellensegment und Zuganker zur Durchströmung mit Kühlfluid gebildet ist.The cylindrical shaft segments, also referred to below as rotor disks, preferably each have a central connection opening through which a single connection element, a tie rod, is guided. The connection opening has a larger cross section than the tie rod, so that preferably an annular axial gap is formed between the shaft segment and the tie rod for the flow of cooling fluid.

Es ist ebenfalls prinzipiell möglich, mehrere, insbesondere drei oder mehr Verbindungselemente (Zuganker) vorzusehen. Die jeweilige Verbindungsach.se der Verbindungselemente liegt par- allel zur Hauptachse der Turbinenwelle. Vorzugsweise sind die jeweiligen Verbindungsachsen auf einem Kreis angeordnet, des¬ sen Mittelpunkt mit der Hauptachse zusammenfällt.In principle, it is also possible to provide several, in particular three or more connecting elements (tie rods). The respective connection axis of the connection elements is parallel to the main axis of the turbine shaft. The respective connecting axes are preferably arranged on a circle, the center of which coincides with the main axis.

Vorzugsweise wird zumindest ein radialer Kanal, insbesondere werden beide radiale Kanäle, zwischen zwei unmittelbar anein¬ ander grenzenden Wellensegmenten gebildet. Dies ist bei¬ spielsweise dadurch realisiert, daß in den aneinander angren¬ zenden Wellensegmenten entsprechende Vertiefungen oder Aus¬ nehmungen, Nuten, vorgesehen sind. Ein radialer Kanal kann allerdings auch durch eine im wesentlichen radiale Bohrung durch das Wellensegment von der Außenoberfläche zur Verbin- dunngsöffnung hindurch realisiert sein. Radial bedeutet hierin vorzugsweise senkrecht zur Hauptachse, schließt aller¬ dings auch jedwede Verbindung zwischen der Außenoberfläche und der Verbindungsöffnung ein, die zumindest teilweise in Richtung der Hauptachse gerichtet ist. Die Turbinenwelle ist vorzugsweise für eine zweiflutige Tur¬ bine vorgesehen und weist dementsprechend einen axialen Mit¬ telbereich auf, an den das Aktionsfluid unmittelbar nach Ein¬ strömung in die Turbine gelangt und dort in zwei im wesentli- chen gleiche Teilströme aufgeteilt wird. Der axiale Mittelbe¬ reich ist vorzugsweise axial zwischen den radialen Kanälen angeordnet. Der Mittelbereich, welcher dem Aktionsfluid bei einer höchsten Temperatur ausgesetzt ist, weist vorzugsweise einen Hohlraum auf, welcher von Kühlfluid durchströmbar ist. Der Hohlraum ist vorzugsweise rotationssymmetrisch zurAt least one radial channel, in particular both radial channels, is preferably formed between two directly adjacent shaft segments. This is achieved, for example, in that corresponding recesses or recesses, grooves, are provided in the mutually adjacent shaft segments. A radial channel can, however, also be realized through an essentially radial bore through the shaft segment from the outer surface to the connection opening. In this context, radial preferably means perpendicular to the main axis, but also includes any connection between the outer surface and the connection opening which is at least partially directed in the direction of the main axis. The turbine shaft is preferably provided for a double-flow turbine and accordingly has an axial central region, to which the action fluid reaches the turbine immediately after it has flowed in and is divided there into two essentially equal partial flows. The axial central region is preferably arranged axially between the radial channels. The central region, which is exposed to the action fluid at a highest temperature, preferably has a cavity through which cooling fluid can flow. The cavity is preferably rotationally symmetrical to the

Hauptachse ausgebildet. Er ist durch ein Abschirmelement ab¬ geschlossen, welches zur Stromteilung eine rotationssymmetri¬ sche Erhebung aufweist. Der Hohlraum kann strömungstechnisch mit dem axialen Spalt verbunden sein. Es ist ebenfalls mög- lieh, Kühlfluid über das Gehäuse einer Turbine und einer das Abschirmelement an das Gehäuse befestigende Halterung zuzu¬ führen.Main axis trained. It is closed off by a shielding element which has a rotationally symmetrical elevation for current division. The cavity can be connected to the axial gap in terms of flow technology. It is also possible to supply cooling fluid via the housing of a turbine and a holder which fixes the shielding element to the housing.

Die Turbinenwelle ist vorzugsweise in einer Dampfturbine, insbesondere einer zweiflutigen Mitteldruck-Teilturbine, an¬ geordnet. Durch den über den Mittelbereich hinweg gebildeten Strömungsweg umfassend die beiden axial voneinander beabstan- deten radialen Kanäle und den damit strömungstechnisch ver¬ bundenen axialen Kanal ist eine Kühlung des Mittelbereichs der Turbinenwelle gewährleistet. Insbesondere gelangt alsThe turbine shaft is preferably arranged in a steam turbine, in particular a double-flow medium-pressure partial turbine. Cooling of the central region of the turbine shaft is ensured by the flow path formed over the central region, comprising the two axially spaced radial ducts and the axial duct connected therewith in terms of flow technology. In particular arrives as

Kühlfluid fungierendes Aktionsfluid aus dem Teilstrom der ei¬ nen Flut bei einem niedrigeren Druckniveau in den Teilstrom der zweiten Flut hinein. Hierdurch wird das als Kühlfluid verwendete Aktionsfluid wieder dem gesamten Dampfprozeß zuge- führt und trägt mithin zum Wirkungsgrad des Gesamtprozesses bei.Action fluid acting as cooling fluid from the partial flow of one flood at a lower pressure level into the partial stream of the second flood. As a result, the action fluid used as the cooling fluid is fed back into the entire steam process and thus contributes to the efficiency of the overall process.

Die auf ein Verfahren zur Kühlung einer Turbinenwelle gerich¬ tete Aufgabe wird dadurch gelöst, daß bei einer Turbinenwelle mit einer Mehrzahl entlang einer Hauptachse axial hinterein¬ ander angeordneter zylindrischer Wellensegmente, die mit ei¬ nem Verspannungselement miteinander verspannt sind, Kühlfluid durch einen ersten radialen Kanal in einen axialen Spalt zwi¬ schen dem Verspannungselement und dem Wellensegment einge¬ führt und durch einen zweiten radialen Kanal aus der Turbi¬ nenwelle herausgeführt wird. Hierdurch ist, wie bereits oben ausgeführt, eine Turbinenwelle in einem thermisch während des Betriebs der Turbinenwelle hoch belasteten Bereich von innen her kühlbar. Eine solche Turbinenwelle ist somit auch in ei¬ ner Dampfturbinenanlage mit Dampfeintrittstemperaturen ober¬ halb 600 °C geeignet. Zur Durchführung einer entsprechenden Kühlleistung wird dem axialen Spalt ein Volumenstrom an Kühl¬ fluid zugeführt, der zwischen 1% bis 4%, insbesondere zwi¬ schen 1,5% und 3%, des gesamten Frischdampfvolumenstroms liegt.The object directed to a method for cooling a turbine shaft is achieved in that in the case of a turbine shaft with a plurality of cylindrical shaft segments arranged axially one behind the other along a main axis and braced with one another by a bracing element, cooling fluid through a first radial channel into an axial gap between the bracing element and the shaft segment and is led out of the turbine shaft through a second radial channel. As already explained above, this allows a turbine shaft to be cooled from the inside in a region which is thermally highly stressed during operation of the turbine shaft. Such a turbine shaft is therefore also suitable in a steam turbine plant with steam inlet temperatures above 600 ° C. To carry out a corresponding cooling capacity, a volume flow of cooling fluid is fed to the axial gap, which is between 1% to 4%, in particular between 1.5% and 3%, of the total live steam volume flow.

Die Turbinenwelle sowie das Verfahren werden beispielhaft an¬ hand der in der Zeichnung dargestellten Figur erläutert.The turbine shaft and the method are explained by way of example with reference to the figure shown in the drawing.

Die einzige Figur zeigt in einem Längsschnitt einen Aus¬ schnitt einer Turbine mit einer Turbinenwelle.The single figure shows a longitudinal section of a section of a turbine with a turbine shaft.

In der einzigen Figur ist ein Ausschnitt eines Längsschnittes durch eine zweiflutige Mitteldruck-Teilturbine 10 einer Dampfturbinenanlage dargestellt. In einem Gehäuse 18 ist eine Turbinenwelle 1 angeordnet. Die Turbinenwelle 1 erstreckt sich entlang einer Hauptachse 2 und weist eine Mehrzahl axial hintereinander angeordneter Wellensegmente 4a, 4b, 4c, 4d, 4e auf. Jedes Wellensegment 4a, 4b weist um die Hauptachse 2 herum eine jeweilige Verbindungsöffnung 6 auf. Die Verbin¬ dungsöffnungen 6 haben jeweils denselben Querschnitt und sind zentrisch zueinander und zur Hauptachse 2 angeordnet. Durch die Verbindungsöffnungen 6 ist entlang einer Verbindungsachse 5 ein Verspannungselement 7, ein Zuganker, geführt. Die Ver¬ bindungsachse 5 fällt in dem dargestellten Ausführungsbei- spiel mit der Hauptachse 2 zusammen. Es ist prinzipiell mög- lieh, auch mehrere, insbesondere mehr als drei, Verspannungs- elemente 7 vorzusehen, die durch jeweils entsprechende Ver¬ bindungsöffnungen 6 geführt sind. Der Zuganker 7 greift an den äußersten, nicht dargestellten, Wellensegmenten so an, daß eine axiale Verspannung der Wellenelemente 4a, 4b, 4c, 4d aneinander erfolgt. Vorzugsweise weist der Zuganker 7 hierzu ein nicht dargestelltes Gewinde auf, in dem eine ebenfalls nicht dargestellte Spannmutter eingreift. Zur Vermeidung ei¬ ner Bewegung benachbarter Wellensegmente 4a, 4b in Umfangs- richtung gegeneinander können diese verdrehsicher über eine Stirnzahnkupplung, insbesondere eine Plankerbverzahnung (Hirthverzahnung) miteinander verbunden sein. Die Verbin- dungsöffnungen 6 haben jeweils einen Querschnitt, der größer als der Querschnitt des Zugankers 7 ist, so daß zwischen ei¬ nem jeweiligen Wellensegment 4a und dem Zuganker 7 ein axia¬ ler Spalt 8, insbesondere ein Ringspalt, verbleibt. Durch die Wellensegmente 4a, 4b, etc. ist eine Außenoberfläche 3 der Turbinenwelle 1 gebildet. In der Umgebung der Außenoberfläche 3 sind aneinandergrenzende Wellensegmente 4a, 4d; 4a, 4b durch eine jeweilige Dichtschweißung 16 für ein Fluid un¬ durchlässig miteinander verbunden. Vorzugsweise zwei Paare von aneinandergrenzenden Wellensegmenten 4d, 4e; 4b, 4c sind so aneinander angeordnet, daß zwischen ihnen ein jeweiliger radialer Kanal 9a, 9b verbleibt.In the single figure, a section of a longitudinal section through a double-flow medium-pressure partial turbine 10 of a steam turbine system is shown. A turbine shaft 1 is arranged in a housing 18. The turbine shaft 1 extends along a main axis 2 and has a plurality of shaft segments 4a, 4b, 4c, 4d, 4e arranged axially one behind the other. Each shaft segment 4a, 4b has a respective connection opening 6 around the main axis 2. The connection openings 6 each have the same cross section and are arranged centrally to one another and to the main axis 2. A bracing element 7, a tie rod, is guided through the connecting openings 6 along a connecting axis 5. In the exemplary embodiment shown, the connection axis 5 coincides with the main axis 2. In principle, it is possible to borrow several, in particular more than three, tensioning elements 7, which are led through corresponding connection openings 6. The tie rod 7 attacks the outermost, not shown, shaft segments so that the shaft elements 4a, 4b, 4c, 4d are braced axially to one another. For this purpose, the tie rod 7 preferably has a thread, not shown, in which a clamping nut, also not shown, engages. To prevent adjacent shaft segments 4a, 4b from moving in the circumferential direction against one another, they can be connected to one another in a rotationally secure manner via a spur tooth coupling, in particular a serration toothing (serration toothing). The connection openings 6 each have a cross section which is larger than the cross section of the tie rod 7, so that an axial gap 8, in particular an annular gap, remains between a respective shaft segment 4a and the tie rod 7. An outer surface 3 of the turbine shaft 1 is formed by the shaft segments 4a, 4b, etc. In the vicinity of the outer surface 3, adjacent shaft segments 4a, 4d; 4a, 4b connected to one another by a respective sealing weld 16 impervious to a fluid. Preferably two pairs of adjacent shaft segments 4d, 4e; 4b, 4c are arranged so that a respective radial channel 9a, 9b remains between them.

Das die Turbinenwelle 1 umgebende Gehäuse 18 weist einen Ein¬ strömbereich 19 für Frischdampf 12 auf. Dem Einströmbereich 19 zugeordnet weist die Turbinenwelle 1 einen Mittelbereich 11 auf, in dem ein Hohlraum 13 ausgebildet ist. Dieser Hohl¬ raum 13 sowie der Mittelbereich 11 der Turbinenwelle 1 sind gegenüber einem heißen, durch den Einströmbereich 19 durch¬ strömenden Aktionsfluid 12 (Frischdampf) durch ein Abschir- melement 17 vor einem unmittelbaren Kontakt mit dem Aktions¬ fluid 12 abgeschirmt. Das Abschirmelement 17 ist rotations- symmetrisch zur Hauptachse 2 ausgebildet und weist eine von der Hauptachse 2 weg gerichtete Erhebung auf. Das Abschirm¬ element 17 dient einer Aufteilung des Aktionsfluides 12, des Frischdampfes, in zwei annähernd gleiche Teilströme. Das Ab¬ schirmelement 17 ist über die erste Leitschaufelreihe 14 je¬ des Teilstroms mit dem Gehäuse 18 verbunden. Durch nicht dar- gestellte Kühlfluidzuführungen gelangt Kühlfluid durch das Gehäuse 18, die erste Leitschaufelreihe 14 und das Abschirm¬ element 17 hindurch in den Hohlraum 13 hinein und bewirkt dort eine Kühlung der Turbinenwelle 1 in dem Mittelbereich 11. Das Kühlfluid kann in dem Hohlraum 13 aufgrund des Wärme- austauschs mit dem Aktionsfluid 12 erhitzt werden und über nicht dargestellte Fluidableitungen dem Dampfprozeß wieder zugeführt werden.The housing 18 surrounding the turbine shaft 1 has an inflow region 19 for live steam 12. Associated with the inflow region 19, the turbine shaft 1 has a central region 11 in which a cavity 13 is formed. This cavity 13 and the central region 11 of the turbine shaft 1 are shielded against a hot action fluid 12 (live steam) flowing through the inflow region 19 by a shielding element 17 from direct contact with the action fluid 12. The shielding element 17 is rotationally symmetrical to the main axis 2 and has an elevation directed away from the main axis 2. The shielding element 17 serves to divide the action fluid 12, the live steam, into two approximately equal partial flows. The shielding element 17 is connected to the housing 18 via the first row of guide vanes 14 of each partial flow. By not provided cooling fluid feeds, cooling fluid passes through the housing 18, the first row of guide vanes 14 and the shielding element 17 into the cavity 13 and there causes cooling of the turbine shaft 1 in the central region 11. The cooling fluid can flow into the cavity 13 due to the heat exchange are heated with the action fluid 12 and are fed back to the steam process via fluid discharge lines, not shown.

In Strömungsrichtung des Aktionsfluides 12 sind, wie bei ei¬ ner Dampfturbine üblich, abwechselnd axial hintereinander mit der Turbinenwelle 1 verbundene Laufschaufelreihen 15 und mit dem Gehäuse 18 verbundene Leitschaufelreihen 14 angeordnet. Eine Kühlung der Turbinenwelle 1 auch von innen heraus, ins- besondere in dem Mittelbereich 11, wird erzielt, indem durch den ersten radialen Kanal 9a bereits etwas entspanntes Akti¬ onsfluid 12 in den axialen Spalt 8 zwischen Zuganker 7 und Wellensegmenten 4d, 4a, 4b einströmt. Dieser Teilstrom des Aktionsfluides 12 wirkt als Kühlfluid 12b, welches zuerst entgegen der Stömungsrichtung des in der Darstellung links strömenden Teilstroms geführt wird. Durch den zweiten radia¬ len Spalt 9b gelangt das Kühlfluid 12b an einer Stelle nied¬ rigeren Drucks in den nach rechts gerichteten Teilstrom hin¬ ein und leistet somit wieder Arbeit an den noch zu durchströ- menden Laufschaufein 15. Bei der dargestellten Turbine 10 kann das Kühlfluid 12b durch den ersten radialen Kanal 9a bei einem Druck von etwa 11 bar und einer Temperatur von etwa 400 °C aus dem nach links gerichteten Teilstrom abgeführt und bei einem Druckniveau kleiner 11 bar dem nach rechts gerich- teten Teilstrom wieder zugeführt werden. Es ist ebenfalls möglich, zum Zwecke der Kühlung den axialen Spalt 8 strö¬ mungstechnisch mit dem Hohlraum 13 zu verbinden. Dem axialen Spalt 8 wird vorzugsweise ein Volumenεtromanteil von 1% bis 4%, insbesondere 1,5% bis 3%, des gesamten Frischdampfvolu- menstromε, welcher die Turbinenwelle antreibt, zugeführt. Die Erfindung zeichnet sich durch eine Turbinenwelle aus, welche eine Mehrzahl axial hintereinander angeordneter und miteinander verspannter Wellensegmente aufweist, in deren In¬ nerem ein axial gerichteter Spalt vorgesehen ist. Dieser Spalt ist über zwei radiale Kanäle an zwei unterschiedlichen Druckniveaus mit dem Strom des die Turbinenwelle antreibenden Aktionsfluides strömungstechnisch verbunden. Die radialen Ka¬ näle liegen vorzugsweise dort, wo jeweils zwei Wellensegmente aneinandergrenzen. Bereits aufgrund der unterschiedlichen Druckniveaus, an denen die jeweiligen radialen Spalte an der Außenoberfläche der Turbinenwelle münden, wird eine druckdif- ferenz-betriebene Kühlfluidströmung von dem Aktionsfluid (Frischdampf) abgezweigt. Ein aus dem Frischdampfström abge¬ zweigter Kühldampfström gelangt über den ersten radialen Ka- nal in den axial gerichteten Spalt und von dort über den zweiten radialen Kanal wieder in den Frischdampfström zurück. Hierdurch wird der dem axialen Spalt benachbarte Bereich der Turbinenwelle von innen heraus gekühlt und das für die Küh¬ lung verwendete Kühlfluid wieder dem gesamten Dampfprozeß zu- geführt. In the flow direction of the action fluid 12, as is customary in the case of a steam turbine, rotor blade rows 15 and guide vane rows 14 connected to the turbine shaft 1 are arranged alternately axially one behind the other. Cooling of the turbine shaft 1 also from the inside, in particular in the central region 11, is achieved in that the first radial channel 9a already releases somewhat relaxed actuation fluid 12 into the axial gap 8 between the tie rod 7 and shaft segments 4d, 4a, 4b flows in. This partial flow of the action fluid 12 acts as a cooling fluid 12b, which is first conducted against the direction of flow of the partial flow flowing on the left in the illustration. Through the second radial gap 9b, the cooling fluid 12b enters the partial flow directed to the right at a point of lower pressure and thus again works on the rotor blades 15 to be flowed through. In the illustrated turbine 10, this can be done Cooling fluid 12b is discharged through the first radial channel 9a at a pressure of approximately 11 bar and a temperature of approximately 400 ° C. from the partial flow directed to the left and fed back to the partial flow directed to the right at a pressure level less than 11 bar. It is also possible to connect the axial gap 8 to the cavity 13 in terms of flow technology for the purpose of cooling. A volume fraction of 1% to 4%, in particular 1.5% to 3%, of the total live steam volume flow which drives the turbine shaft is preferably fed to the axial gap 8. The invention is characterized by a turbine shaft, which has a plurality of shaft segments arranged axially one behind the other and braced with one another, in the interior of which an axially directed gap is provided. This gap is fluidically connected to the flow of the action fluid driving the turbine shaft via two radial channels at two different pressure levels. The radial channels are preferably located where two shaft segments adjoin each other. Already on the basis of the different pressure levels at which the respective radial gaps open on the outer surface of the turbine shaft, a pressure-difference-operated cooling fluid flow is branched off from the action fluid (live steam). A cooling steam flow branched off from the live steam flow arrives via the first radial channel into the axially directed gap and from there via the second radial channel back into the live steam flow. As a result, the region of the turbine shaft adjacent to the axial gap is cooled from the inside and the cooling fluid used for the cooling is fed back to the entire steam process.

Claims

Patentansprüche Claims 1. Turbinenwelle (1) , die sich entlang einer Hauptachse (2) erstreckt und eine Außenoberfläche (3) aufweist, mit einer Mehrzahl entlang der Hauptachse (2) axial hintereinander an¬ geordneter zylindrischer Wellensegmente (4a, 4b, 4c, 4d,4e) , die entlang einer gemeinsamen Verbindungsachse (5) jeweils eine Verbindungsöffnung (6) aufweisen, durch welche ein Verspan¬ nungselement (7) geführt ist, wobei zwischen Verspannungsele- ment (6) und zumindest einem Wellensegment (4a,4b,4c) ein axialer Spalt (8) gebildet ist sowie zwei axial voneinander beabstandete radiale Kanäle (9a, 9b) vorgesehen sind, die mit dem axialen Spalt (8) stömungstechnisch verbunden sind und jeweils an der Außenoberfläche (3) münden.1. Turbine shaft (1) which extends along a main axis (2) and has an outer surface (3) with a plurality of cylindrical shaft segments (4a, 4b, 4c, 4d, 4e) arranged axially one behind the other along the main axis (2) ), each of which has a connection opening (6) along a common connection axis (5) through which a tensioning element (7) is guided, with a tensioning element (6) and at least one shaft segment (4a, 4b, 4c) between axial gap (8) is formed and two axially spaced radial channels (9a, 9b) are provided, which are fluidically connected to the axial gap (8) and each open on the outer surface (3). 2. Turbinenwelle (1) nach Anspruch 1, bei der das Verbin¬ dungselement (7) ein zentraler Zuganker ist, für den Hauptachse (2) und Verbindungsach.se (5) zusammenfallen.2. Turbine shaft (1) according to claim 1, wherein the connec tion element (7) is a central tie rod for the main axis (2) and Verbindungsach.se (5) coincide. 3. Turbinenwelle (1) nach Anspruch 1, bei der mindestens drei Verbindungselemente (7) vorgesehen sind, deren jeweilige Verbindungsasche (5) parallel zur Hauptachse (3) gerichtet ist.3. Turbine shaft (1) according to claim 1, in which at least three connecting elements (7) are provided, the respective connecting pocket (5) of which is directed parallel to the main axis (3). 4. Turbinenwelle (1) nach einem der vorhergehenden Ansprü¬ che, bei der zumindest ein radialer Kanal (9a, 9b) zwischen zwei aneinandergrenzenden Wellensegmenten (4b, 4c;4d, 4e) vor¬ gesehen ist .4. Turbine shaft (1) according to one of the preceding claims, in which at least one radial channel (9a, 9b) is provided between two adjacent shaft segments (4b, 4c; 4d, 4e). 5. Turbinenwelle (1) nach einem der vorhergehenden Ansprü¬ che, für eine zweiflutige Turbine (10) mit einem axialen Mit¬ telbereich (11) für die Einströmung und Stromteilung eines Aktionsfluides (12) , welcher axial zwischen den radialen Ka¬ nälen (9a, 9b) angeordnet ist.5. Turbine shaft (1) according to one of the preceding claims, for a double-flow turbine (10) with an axial central region (11) for the inflow and flow division of an action fluid (12) which is axially between the radial channels ( 9a, 9b) is arranged. 6. Turbinenwelle (1) nach Anspruch 5, bei dem in dem Mit¬ telbereich (11) ein Hohlraum (13) , welcher von Kühlfluid (12b) durchströmbar ist, vorgesehen ist.6. Turbine shaft (1) according to claim 5, in which in the central region (11) a cavity (13) containing cooling fluid (12b) can be flowed through, is provided. 7. Turbinenwelle (1) nach Anspruch 6, bei der der Hohlraum (7) mit dem axialen Spalt (8) strömungstechnisch verbunden ist.7. turbine shaft (1) according to claim 6, wherein the cavity (7) with the axial gap (8) is connected in terms of flow. 8. Turbinenwelle (1) nach einem der vorhergehenden Ansprü¬ che, in einer Dampfturbine (15) , insbesondere einer zweiflu- tigen Mitteldruck-Teilturbine.8. Turbine shaft (1) according to one of the preceding claims, in a steam turbine (15), in particular a double-flow medium-pressure turbine part. 9. Verfahren zur Kühlung einer Turbinenwelle (1) mit einer Mehrzahl entlang einer Hauptachse (2) axial hintereinander angeordneter zylindrischer Wellensegmente (4a,4b,4c,4d,4e) , die mit einem Verspannungselement (7) miteinander verspannt sind, wobei Kühlfluid (12a) durch einen ersten radialen Kanal (9a) in einen axialen Spalt (8) zwischen Verspannungselement (7) und Wellensegment (4a) eingeführt und durch einen zweiten radialen Kanal (9b) aus der Turbinenwelle (1) herausgeführt wird.9. Method for cooling a turbine shaft (1) with a plurality of cylindrical shaft segments (4a, 4b, 4c, 4d, 4e) arranged axially one behind the other along a main axis (2), which are braced together with a bracing element (7), cooling fluid ( 12a) through a first radial channel (9a) into an axial gap (8) between the bracing element (7) and shaft segment (4a) and is led out of the turbine shaft (1) through a second radial channel (9b). 10. Verfahren nach Anspruch 9, bei dem in einer Dampfturbine (10) dem axialen Spalt (8) als Kühlfluid (12b) ein Volumen¬ strom an Dampf von 1,0 % bis 4,0 %, insbesondere 1,5% bis 3%, des gesamten Frischdampfvolumenstroms zugeführt wird. 10. The method according to claim 9, in which in a steam turbine (10) the axial gap (8) as cooling fluid (12b) a volume flow of steam of 1.0% to 4.0%, in particular 1.5% to 3 % of the total live steam volume flow is supplied.
EP97923804A 1996-06-21 1997-05-12 Turbine shaft and process for cooling it Expired - Lifetime EP0906494B1 (en)

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PCT/DE1997/000953 WO1997049901A1 (en) 1996-06-21 1997-05-12 Turbine shaft and process for cooling it

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JP2000512706A (en) 2000-09-26
RU2182975C2 (en) 2002-05-27
US6048169A (en) 2000-04-11
ATE247766T1 (en) 2003-09-15
CN1228134A (en) 1999-09-08
EP0906493B1 (en) 2003-08-20
ATE230065T1 (en) 2003-01-15
CZ422798A3 (en) 1999-04-14
PL330425A1 (en) 1999-05-10
KR20000022066A (en) 2000-04-25
DE59710625D1 (en) 2003-09-25
JP3939762B2 (en) 2007-07-04
CZ423498A3 (en) 1999-04-14
EP0906494B1 (en) 2002-12-18
CN1106496C (en) 2003-04-23
ES2206724T3 (en) 2004-05-16
DE59709016D1 (en) 2003-01-30
JP2000512708A (en) 2000-09-26
RU2182976C2 (en) 2002-05-27
KR20000022065A (en) 2000-04-25
PL330755A1 (en) 1999-05-24
WO1997049900A1 (en) 1997-12-31
CN1100193C (en) 2003-01-29
JP3943136B2 (en) 2007-07-11
WO1997049901A1 (en) 1997-12-31
EP0906493A1 (en) 1999-04-07
CN1227619A (en) 1999-09-01
US6102654A (en) 2000-08-15

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