EP0202531B1 - Blade-to-blade connection for the rotor of a turbo machine - Google Patents

Blade-to-blade connection for the rotor of a turbo machine Download PDF

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Publication number
EP0202531B1
EP0202531B1 EP86106150A EP86106150A EP0202531B1 EP 0202531 B1 EP0202531 B1 EP 0202531B1 EP 86106150 A EP86106150 A EP 86106150A EP 86106150 A EP86106150 A EP 86106150A EP 0202531 B1 EP0202531 B1 EP 0202531B1
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EP
European Patent Office
Prior art keywords
blades
button
tying
conical
blade
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Expired
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EP86106150A
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German (de)
French (fr)
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EP0202531A1 (en
Inventor
Hans-Joachim Herrmann
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MAN Gutehoffnungshutte GmbH
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MAN Gutehoffnungshutte GmbH
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    • 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
    • F01D5/12—Blades
    • F01D5/22—Blade-to-blade connections, e.g. for damping vibrations

Definitions

  • the invention relates to a binding of rotor blades of a thermal turbomachine by means of extensions which extend in the circumferential direction and are rigidly connected in pairs to the associated rotor blade and which are supported at least during operation of the turbine or the compressor via flat contact surfaces.
  • the natural frequency is increased by such a binding of the rotor blades on the circumference in the upper part of the blades; in addition, the excitability of a bound blade ring is significantly lower.
  • Known bindings of the rotor blades or rotor blade groups of steam turbines and compressors are cover plates which have a certain excess in the circumferential direction, as a result of which a tangential preload is created between the cover plates when the blades are installed, or arcuate elements, so-called arcades, in the form of pairs on the rotor blade attached steel arches, the V-shaped ends of two adjacent steel arches intermeshing and under pressure in the circumferential direction, or supporting wings, d. H. in the circumferential direction extending lugs on the blades with a streamlined profile. - Shifts between these circumferentially braced binding elements - z. B.
  • the invention has for its object to provide a binding of the type mentioned, which ensures for all operating areas of the machine and for a sufficient time a defined, independent of manufacture, material and operating behavior, flat contact between the binding elements.
  • the constancy of the frictional relationships between the binding elements should be ensured in order to protect individual tunnels from being overstressed as a result of instability and evasion processes and to minimize fretting wear.
  • one or both contact surfaces per adjacent pair of lugs are formed by the one or more flat end faces of one or two pressure bodies each having a conical seat, that each pressure body in a neck recess with a conical seat, the The inclination is steeper than the inclination of the pressure body seat, is mounted such that it can be tilted, and that each pressure body receives its final placement and bedding as a result of the moment F T contact m, as well as the F T hurling, and the bending moment F T.
  • e transmits self-locking, where F T is the circumferential force component and e is the eccentric position or m is the distance from the pressure body edge to the pressure body axis of symmetry.
  • the conical seat of the pressure body enables the rotary movement required for parallel adjustment to the support surface through the angle difference ⁇ , as well as the notch-free introduction of moments and pressures, also from the centrifugal force, which ensures the fatigue strength of the connection.
  • the pressure bodies receive their final placement and bedding with an approximately uniform surface pressure distribution over the contact surface by local flow of the pressure body seat up to the annular support in the seat of the projections; Since the conical section, which deviates from the ideal ring surface, becomes force-fit and form-fitting due to the unique plasticization and elastic bedding, self-locking bending moments from the coupling vibration can be transmitted to a large extent from the pressure bodies under pressure due to the ratio e / p. - Due to the loose attachment of the pressure body, their interchangeability is relatively easy and independent of location, so that there is also interchangeability in the power plant.
  • each pressure body is beveled conically at the front end.
  • each pressure element has a cylindrical section between its conical seat and its front part, and that pressure elements with different heights of the cylindrical section are used.
  • the pressure bodies In order to be able to fasten the pressure bodies in the binding elements by loose caulking, the pressure bodies each have a conical section between the cylindrical section and the conical front part in particular.
  • the pressure bodies consist of a material with little differences between static and sliding friction, little or no porosity, high pressure and bending strength, high corrosion resistance and - if necessary - high abrasion resistance.
  • the manufacture of the pressure hull with a relatively free choice of material, an optimal selection of sliding partners with the desired constant friction coefficient as possible, i. H. Sliding partner with slight differences between static and sliding friction, without seizing and taking corrosion protection into account, whereby the binding function, and thus the desired vibration behavior, is ensured.
  • defined contact relationships between the binding elements are ensured for the desired, relatively long time, so that the binding according to the invention can be used especially in steam turbines and compressors, that is to say machines with a long service life.
  • each front, cylindrical wall part in the associated attachment has a corresponding opening at the bottom and / or top.
  • each pressure body is cut off laterally symmetrically to its longitudinal median plane, such that the distance between the straight side surfaces is slightly less than the width of the opening or openings in the extension wall part.
  • the twisted, radially mountable rotor blades are numbered 1, to which two steel lugs 2, each pointing in the circumferential direction, are rigidly fastened - one lug each on different sides of the airfoils.
  • the lugs 2 are preferably an integral part of the associated moving blade.
  • the approaches 2 are shown in the example shown as a support wing with a streamlined profile 3; but they can also be cover plates or other binding elements.
  • the free ends of the lugs 2 have flat, sloping surfaces; the plane through this surface - seen in plan view - is rotated by such an angle with respect to the circumferential direction that the previously mentioned displacement movements between the later-mentioned contact surfaces 6e are possible, and the blades are not prevented from rotating by self-locking.
  • the lugs 2 have recesses on their flat end faces, each with a conical seat 4 and a concave wall part 5 adjoining the conical seat 4 for loosely receiving pressure bodies 6.
  • the pressure bodies 6 consist of a material which is as low as possible porosity, high pressure and bending strength, high corrosion resistance and high abrasion resistance, which is the case with certain sintered hard metals, certain hard metals produced in the so-called HIP process - compression under high pressure and high temperature or given certain ceramic plates with a high surface quality.
  • Each one-piece pressure body 6 has a plurality of sections, namely a frustoconical seat 6a, a cylindrical intermediate part 6b with a differently selectable height h, a frustoconical intermediate part 6c with a cone, which is used for mounting in the neck cavity by loose caulking, and a frustoconical front part 6d with a cone with a flat circular contact surface 6e, which are provided with the correspondingly high surface quality by appropriate processing methods such as grinding or the like.
  • the inclination of the conical seat 6a of the pressure body 6 is smaller by the angle ⁇ than the inclination of the conical seat 4 in the neck 2; in addition, the diameter of the wall part 5 of the neck 2 is larger than the largest diameter of the pressure body 6, so that the required tiltable mounting of the pressure body 6 is available for self-adjustment.
  • the largest diameter of the pressure body 6 and the corresponding diameter in the extension 2 is greater than the greatest height H of the extension profile, so that the wall part 5 has openings 7a, 7b at the top and bottom.
  • the largest diameter of the pressure body 6, however, is smaller than the maximum height H of the neck profile, a free milling is at least on the underside of the wall part 5 is advantageous for the simple replacement or removal of the pressure element 6, because then there is an engagement surface for a tool or the like.
  • the pressure bodies 6 protrude with their contact surfaces 6e from the end faces of the approaches 2 in the circumferential direction.
  • the pressure bodies 6 made of the corresponding hard metal are applied in pairs to two adjacent approaches 2. - In principle, however, it is also conceivable to use only one pressure element on one of the lugs 2 and its interaction with the flat end face of the adjacent lug on the next blade. For this purpose, however, it is necessary to choose a suitable material for the pressure body, which interacts with the steel attachment end face, without tending to eat or the like. A suitable material for the pressure body would be, for. B. certain bronzes.
  • corresponding pressure elements 6 with different height h are selected such that after the introduction of the pressure elements 6 into the openings 7 in the approaches 2 Gap widths are approximately the same over the circumference. - After the radial installation of the blades, there is no tangential preload in the preferred application example.
  • the pressure elements 6 can be prevented from falling out by two light mounting locks 8 which do not hinder the self-adjustment of the pressure elements if rotor blades have to be removed again after the initial installation.
  • the pressure elements 6 are self-adjusting because when the blade ring is rotated as a result of the moment F T - m - where F T is the circumferential force component and m is the distance between the pressure element edge and the pressure element symmetry axis 9 - the pressure element rotates up to the angular difference resulting from the different inclination of the seats ⁇ - which is in the order of 15 'to 30' (angular minutes) in the case of precise production - so that the deviations from the parallel position (eccentricity e) which are always present for production reasons are compensated for.
  • the contact surfaces are, as previously mentioned, so inclined to the circumferential direction that self-locking with displacements of two adjacent circular contact surfaces 6e are avoided with certainty.
  • the conical shape of the seat which deviates from the ideal ring surface, becomes non-positive and form-fitting due to the unique plasticization and elastic bedding.
  • the blades 1 can also be equipped with such pressure bodies by selecting appropriate heights h that the gap between the pressure bodies 6 is zero when installing, or that there is a tangential oversize, so that after the installation of the blades a desired tangential already with the turbine blade ring at rest Bias is present between the lugs 2 with the pressure bodies 6, the bias being increased in the operating state of the turbine.
  • the binding according to the invention can also be used with straight blades; only appropriate measures must be taken to ensure that the contact surfaces or the lugs with pressure bodies are supported against one another with appropriate circumferential force both at rest and in the course of the turbines or compressor blades.
  • the pressure hulls can be used without assembly-related restriction of the friction angle ⁇ , even after assembly of the blades in the wheel rim. If the gap between the lugs for the assembly is not large enough and the blades cannot be pressed apart far enough, the pressure bodies in the upper area must be cut off on opposite sides, such that the width of the pressure body between the cut, straight, parallel ones Areas is slightly less than the width of the opening in the neck 2. The cut pressure body is inserted radially, perpendicular to the turbine axis through the opening and then rotated by 90 °, so that the round sections are opposite the corresponding round sections of the wall part 5. Incidentally, as can be seen from FIG. 2, there also need not be two opposite openings 7, but an opening is also sufficient, which will preferably be provided at the base 2 in its outer area.
  • binding according to the invention are end blades in the low-pressure part of large steam turbines.
  • the binding according to the invention can also be used in the case of blade rings of other steam turbine stages, in the case of blade rings of compressors, gas turbines and the like.

Description

Die Erfindung bezieht sich auf eine Bindung von Laufschaufeln einer thermischen Turbomaschine durch in Umfangsrichtung sich erstreckende Ansätze, die paarweise mit der ihr zugehörigen Laufschaufel starr verbunden sind und sich zumindest im Betrieb der Turbine bzw. des Verdichters über ebene Berührungsflächen abstützen.The invention relates to a binding of rotor blades of a thermal turbomachine by means of extensions which extend in the circumferential direction and are rigidly connected in pairs to the associated rotor blade and which are supported at least during operation of the turbine or the compressor via flat contact surfaces.

Durch eine solche Bindung der Laufschaufeln am Umfang im oberen Teil der Schaufeln wird die Eigenfrequenz angehoben ; außerdem ist die Erregbarkeit eines gebundenen Schaufelkranzes wesentlich geringer.The natural frequency is increased by such a binding of the rotor blades on the circumference in the upper part of the blades; in addition, the excitability of a bound blade ring is significantly lower.

Bekannte Bindungen der Laufschaufein bzw. Laufschaufelgruppen von Dampfturbinen und Verdichtern sind Deckplatten, die in Umfangsrichtung ein gewisses Übermaß aufweisen, durch das beim Einbau der Schaufeln eine tangentiale Vorspannung zwischen den Deckplatten entsteht, oder bogenförmige Elemente, sogenannte Arkaden, in Form von paarweise an der Laufschaufel befestigten Stahlbögen, wobei die V-förmigen Enden zweier benachbarter Stahlbögen ineinander greifen und in Umfangsrichtung unter Druckvorspannung stehen, oder Stützflügel, d. h. in Umfangsrichtung sich erstreckende Ansätze an den Schaufeln mit strömungsgünstig ausgebildetem Profil. - Verschiebungen zwischen diesen umfangsverspannten Bindungselementen - z. B. durch radiale Dehnung oder Entwindung der Laufschaufeln unter Fliehkraft und daraus resultierender tangentialer Längenänderung des Radkranzes, durch Temperaturdifferenzen zwischen Schaufelbindung-Läufer und Schaufel, wie sie insbesondere bei Turbinen mit großen Schwankungen des Gegendrucks auftreten - führen jedoch zu erhöhtem Verschleiß und Änderung des Reibverhaltens zwischen den Kontaktflächen, was das Schwingungs- und Festigkeitsverhalten des Schaufelkranzes negativ beeinflußt. Als weiterer Nachteil wird auch die Möglichkeit punktförmigen Sitzes der Kontaktfläche, wie er aus Fliehkraftsverformung des Bindeelementes oder fertigungsbedingt entstehen kann, angesehen.Known bindings of the rotor blades or rotor blade groups of steam turbines and compressors are cover plates which have a certain excess in the circumferential direction, as a result of which a tangential preload is created between the cover plates when the blades are installed, or arcuate elements, so-called arcades, in the form of pairs on the rotor blade attached steel arches, the V-shaped ends of two adjacent steel arches intermeshing and under pressure in the circumferential direction, or supporting wings, d. H. in the circumferential direction extending lugs on the blades with a streamlined profile. - Shifts between these circumferentially braced binding elements - z. B. by radial expansion or unwinding of the blades under centrifugal force and the resulting tangential change in length of the wheel rim, by temperature differences between the blade binding rotor and blade, as they occur in particular in turbines with large fluctuations in the back pressure - lead to increased wear and change in the friction behavior between the contact surfaces, which negatively influences the vibration and strength behavior of the blade ring. Another disadvantage is the possibility of punctiform seating of the contact surface, as can arise from the centrifugal force deformation of the binding element or from production-related reasons.

Im Flugtriebwerksbau ist es bekannt, an den Kontaktflächen der Schaufelbindungselemente besondere Spritzbeschichtungen und Auftragsschweißungen mit überwiegend harten Werkstoffen wie z. B. Wolfram-Karbid, Chromkarbid und dergleichen aufzubringen. Diese, für die relativ kurze Betriebszeit bei Flugtriebwerken durchaus ausreichenden Maßnahmen, sind jedoch für Dampfturbinen nicht wirtschaftlich anwendbar, weil dort über die gesamte Betriebszeit von 200 000 Stunden und mehreren 1 000 Starts eine langzeitige Konstanz der Bindungs- und Reibungsverhältnisse erforderlich ist.In aircraft engine construction, it is known to apply special spray coatings and build-up welds with predominantly hard materials, such as, for example, to the contact surfaces of the blade binding elements. B. tungsten carbide, chromium carbide and the like. These measures, which are quite sufficient for the relatively short operating time for aircraft engines, cannot be used economically for steam turbines, because long-term consistency of the bond and friction conditions is required over the entire operating time of 200,000 hours and several 1,000 starts.

Der Erfindung liegt die Aufgabe zugrunde, eine Bindung der eingangs genannten Art zu schaffen, die für alle Betriebsbereiche der Maschine und für eine ausreichende Zeit einen definierten, von Fertigung, Material und Betriebsverhalten unabhängigen, flächigen Kontakt zwischen den Bindungselementen gewährleistet. Außerdem soll die Konstanz der Reibungsverhältnisse zwischen den Bindungselementen zum Schutz vor Überbeanspruchung einzelner Laufschaufein infolge von Instabilitäts- und Ausweichvorgängen und zur Minimierung des Reibverschleißes gesichert sein.The invention has for its object to provide a binding of the type mentioned, which ensures for all operating areas of the machine and for a sufficient time a defined, independent of manufacture, material and operating behavior, flat contact between the binding elements. In addition, the constancy of the frictional relationships between the binding elements should be ensured in order to protect individual tunnels from being overstressed as a result of instability and evasion processes and to minimize fretting wear.

Diese Aufgabe wird erfindungsgemäß dadurch gelöst, daß eine oder beide Berührungsflächen pro benachbartem Ansatzpaar von der bzw. den ebenen Stirnflächen eines bzw. zweier, je einen konischen Sitz aufweisender Druckkörper gebildet sind, daß jeder Druckkörper in einer Ansatz-Ausnehmung mit einem konischen Sitz, dessen Neigung steiler als die Neigung des Druckkörpers-Sitzes ist, kippbeweglich gelagert ist, und daß jeder Druckkörper durch das Moment FT Kontakt m selbsteinstellend, sowie beim F T schleudern seine endgültige Plazierung und Bettung erhält, sowie das Biegemoment FT . e selbsthemmend überträgt, wobei FT die Umfangskraftkomponente und e die exzentrische Lage bzw. m der Abstand der Druckkörperkante zur Druckkörper-Symmetrieachse bedeuten.This object is achieved in that one or both contact surfaces per adjacent pair of lugs are formed by the one or more flat end faces of one or two pressure bodies each having a conical seat, that each pressure body in a neck recess with a conical seat, the The inclination is steeper than the inclination of the pressure body seat, is mounted such that it can be tilted, and that each pressure body receives its final placement and bedding as a result of the moment F T contact m, as well as the F T hurling, and the bending moment F T. e transmits self-locking, where F T is the circumferential force component and e is the eccentric position or m is the distance from the pressure body edge to the pressure body axis of symmetry.

Der konische Sitz der Druckkörper ermöglicht einerseits die zur parallelen Anpassung an die Stützfläche erforderliche Drehbewegung durch die Winkeldifferenz Δϕ, sowie andererseits das kerbfreie Einleiten von Momenten und Drücken, auch aus der Fliehkraft, was die Dauerfestigkeit der Verbindung sichert. Die Druckkörper erhalten beim Schleudern, durch örtliches Fließen des Druckkörper-Sitzes bis zur ringförmigen Auflage im Sitz der Ansätze, ihre endgültige Plazierung und Bettung mit über der Kontaktfläche annähernd gleichförmiger Flächenpressungsverteilung ; da der von der idealen Ringfläche abweichende, kegelschnittförmige Sitz durch einmalige Plastifizierung und elastische Bettung kraft- und formschlüssig wird, können in hohem Maße von dem unter Druck stehenden Druckkörpern durch das Verhältnis e/p selbsthemmende Biegemomente aus der Koppelschwingung übertragen werden. - Durch die lockere Befestigung der Druckkörper ist auch deren Auswechselbarkeit relativ problemlos und ortsunabhängig, so daß auch Auswechselbarkeit im Kraftwerk gegeben ist.The conical seat of the pressure body enables the rotary movement required for parallel adjustment to the support surface through the angle difference Δϕ, as well as the notch-free introduction of moments and pressures, also from the centrifugal force, which ensures the fatigue strength of the connection. When spinning, the pressure bodies receive their final placement and bedding with an approximately uniform surface pressure distribution over the contact surface by local flow of the pressure body seat up to the annular support in the seat of the projections; Since the conical section, which deviates from the ideal ring surface, becomes force-fit and form-fitting due to the unique plasticization and elastic bedding, self-locking bending moments from the coupling vibration can be transmitted to a large extent from the pressure bodies under pressure due to the ratio e / p. - Due to the loose attachment of the pressure body, their interchangeability is relatively easy and independent of location, so that there is also interchangeability in the power plant.

Aus Gründen des Kanten- und Verschleißschutzes, sowie um singuläre Druckspannungen am Gleitflächenrand abzubauen, ist, in weiterer Ausgestaltung der Erfindung, jeder Druckkörper am vorderen Ende konisch abgeschrägt.For reasons of edge and wear protection, as well as to reduce singular compressive stresses on the edge of the sliding surface, in a further embodiment of the invention, each pressure body is beveled conically at the front end.

Eine vorteilhafte Weiterbildung der erfindungsgemäßen Bindung besteht darin, daß jeder Druckkörper einen zylindrischen Abschnitt zwischen seinem konischen Sitz und seinem Vorderteil aufweist, und daß Druckkörper mit verschiedenen Höhen des zylindrischen Abschnitts eingesetzt sind. - Durch diese Maßnahmen ist bei der Montage durch entsprechende Auswahl der Druckkörperhöhen ein eng toleriertes Spiel zwischen allen Kontaktfiächen, oder eine gewünschte tangentiale Vorspannung in der Bindung, einstellbar, wodurch über den Umfang unterschiedliche Spaltdifferenzen, wie sie sich aus Fertigung und Montage ergeben, und daraus resultierende Spannungserhöhungen in den Schaufeiblättern, vermieden sind ; außerdem ist ein nachträgliches Abstimmen der Resonanzfrequenzen möglich.An advantageous development of the binding according to the invention is that each pressure element has a cylindrical section between its conical seat and its front part, and that pressure elements with different heights of the cylindrical section are used. - By means of these measures, a tightly tolerated play between all contact surfaces, or a desired one, is achieved during the installation by appropriately selecting the pressure body heights no tangential preload in the binding, adjustable, which avoids different gap differences over the circumference, such as those resulting from manufacture and assembly, and the resulting increase in tension in the shovel blades; a subsequent adjustment of the resonance frequencies is also possible.

Um die Druckkörper in den Bindungselementen durch loses Verstemmen befestigen zu können, weisen die Druckkörper zwischen dem zylindrischen Abschnitt und dem insbesondere konischen Vorderteil je einen konischen Abschnitt auf.In order to be able to fasten the pressure bodies in the binding elements by loose caulking, the pressure bodies each have a conical section between the cylindrical section and the conical front part in particular.

In weiterer vorteilhafter Ausgestaltung der Erfindung bestehen die Druckkörper aus einem Werkstoff mit geringen Unterschieden zwischen Haft- und Gleitreibung, geringer oder keiner Porosität, hoher Druck- und Biegefestigkeit, hoher Korrosionsbeständigkeit und - erforderlichenfalls - hoher Abriebfestigkeit. - Dadurch gestattet, unabhängig von Schaufel-Fertigungsverfahren, Schaufel-Fertigungsablauf und Schaufel-Werkstoff, die Herstellung der Druckkörper bei relativ freier Wahl des Werkstoffs eine optimale Auswahl der Gleitpartner mit gewünschtem möglichst konstantem Reibungskoeffizienten, d. h. Gleitpartner mit geringen Unterschieden zwischen Haft- und Gleitreibung, ohne Fressen und unter Beachtung des Korrosionsschutzes, wobei die Bindungsfunktion, und damit das gewünschte Schwingungsverhalten, sichergestellt ist. - Bei entsprechender Werkstoffauswahl sind für die gewünschte, relativ lange Zeit definierte Kontaktverhältnisse zwischen den Bindungselementen sichergestellt, so daß die erfindungsgemäße Bindung speziell bei Dampfturbinen und Verdichtern, also Maschinen mit langer Lebensdauer, einsetzbar ist.In a further advantageous embodiment of the invention, the pressure bodies consist of a material with little differences between static and sliding friction, little or no porosity, high pressure and bending strength, high corrosion resistance and - if necessary - high abrasion resistance. - This allows, regardless of blade manufacturing process, blade manufacturing process and blade material, the manufacture of the pressure hull with a relatively free choice of material, an optimal selection of sliding partners with the desired constant friction coefficient as possible, i. H. Sliding partner with slight differences between static and sliding friction, without seizing and taking corrosion protection into account, whereby the binding function, and thus the desired vibration behavior, is ensured. - With the appropriate choice of material, defined contact relationships between the binding elements are ensured for the desired, relatively long time, so that the binding according to the invention can be used especially in steam turbines and compressors, that is to say machines with a long service life.

Die Auswahl der Druckkörper und ein möglicher Austausch sind erleichtert, wenn - in weiterer Ausgestaltung der Erfindung - jeder vordere, zylindrische Wandungsteil im zugehörigen Ansatz unten und/oder oben eine entsprechende Öffnung aufweist.The selection of the pressure body and a possible exchange are facilitated if - in a further embodiment of the invention - each front, cylindrical wall part in the associated attachment has a corresponding opening at the bottom and / or top.

Um die erfindungsgemäße Bindung auch bei axial montierten Laufschaufeln - z. B. geraden oder gebogenen Tannenbaumfußverbindungen - anwenden zu können, ist jeder Druckkörper symmetrisch zu seiner Längsmittelebene seitlich abgeschnitten, derart, daß der Abstand zwischen den geraden Seitenflächen etwas geringer ist als die Breite der Öffnung bzw. Öffnungen im Ansatz-Wandungsteil.To the binding according to the invention even with axially mounted blades - z. B. straight or curved fir tree foot connections - to use, each pressure body is cut off laterally symmetrically to its longitudinal median plane, such that the distance between the straight side surfaces is slightly less than the width of the opening or openings in the extension wall part.

In der Zeichnung sind Ausführungsbeispiele der Erfindung schematisch dargestellt. Es zeigt :

  • Figur 1a, 1b eine Draufsicht auf einen Schaufelkranzausschnitt im Außerbetriebszustand (1a) und im Betriebszustand (1 b),
  • Figur 2 eine Seitenansicht auf einen Schaufelansatz,
  • Figur 3 einen Schnitt gemäß der Linie 11-11 nach Figur 2, und
  • Figur 4a, 4b einen modifizierten Druckkörper in einer Seitenansicht und in einer Draufsicht.
Exemplary embodiments of the invention are shown schematically in the drawing. It shows :
  • 1a, 1b a top view of a blade ring section in the non-operating state (1a) and in the operating state (1b),
  • FIG. 2 shows a side view of a blade attachment,
  • 3 shows a section along the line 11-11 of Figure 2, and
  • Figure 4a, 4b a modified pressure body in a side view and in a plan view.

Mit 1 sind die verwundenen, radial montierbaren Laufschaufeln beziffert, an denen je zwei, in Umfangsrichtung weisende stählere Ansätze 2 - je ein Ansatz auf verschiedenen Seiten der Schaufelblätter - starr befestigt sind. Vorzugsweise sind die Ansätze 2 integraler Bestandteil der zugehörigen Laufschaufel. - Die Ansätze 2 sind in dem dargestellten Beispiel zwar als Stützflügel mit einem strömungsgünstigen Profil 3 dargestellt ; sie können aber auch Deckplatten oder andere Bindungselemente sein. - Die freien Enden der Ansätze 2 weisen ebene, schräge Flächen auf ; wobei die Ebene durch diese Fläche - in der Draufsicht gesehen - um einen solchen Winkel gegenüber der Umfangsrichtung verdreht ist, daß die vorher erwähnten Verschiebebewegungen zwischen den später erwähnten Kontaktflächen 6e möglich sind, und nicht etwa die Laufschaufeln durch Selbsthemmung an der Verdrehung gehindert sind.The twisted, radially mountable rotor blades are numbered 1, to which two steel lugs 2, each pointing in the circumferential direction, are rigidly fastened - one lug each on different sides of the airfoils. The lugs 2 are preferably an integral part of the associated moving blade. - The approaches 2 are shown in the example shown as a support wing with a streamlined profile 3; but they can also be cover plates or other binding elements. - The free ends of the lugs 2 have flat, sloping surfaces; the plane through this surface - seen in plan view - is rotated by such an angle with respect to the circumferential direction that the previously mentioned displacement movements between the later-mentioned contact surfaces 6e are possible, and the blades are not prevented from rotating by self-locking.

Die Ansätze 2 weisen an ihren ebenen Stirnflächen Ausnehmungen mit je einem konischen Sitz 4 und je einem konkaven, an den konischen Sitz 4 anschließenden Wandungsteil 5 zur lockeren Aufnahme von Druckkörpern 6 auf.The lugs 2 have recesses on their flat end faces, each with a conical seat 4 and a concave wall part 5 adjoining the conical seat 4 for loosely receiving pressure bodies 6.

Die Druckkörper 6 bestehen für den bevorzugten Anwendungsbereich aus einem Werkstoff möglichst geringer Porosität, hoher Druck- und Biegefestigkeit, hoher Korrosionsbeständigkeit und hoher Abriebfestigkeit, was bei bestimmten gesinterten Hartmetallen, bestimmten im sogenannten HIP-Verfahren - Verdichtung unter hohem Druck und hoher Temperatur - hergestellten Hartmetallen oder bei bestimmten Keramikplatten mit hoher Oberflächengüte gegeben ist.For the preferred area of application, the pressure bodies 6 consist of a material which is as low as possible porosity, high pressure and bending strength, high corrosion resistance and high abrasion resistance, which is the case with certain sintered hard metals, certain hard metals produced in the so-called HIP process - compression under high pressure and high temperature or given certain ceramic plates with a high surface quality.

Jeder einstückige Druckkörper 6 weist mehrere Abschnitte auf, nämlich einen kegelstumpfförmigen Sitz 6a, einen zylindrischen Zwischenteil 6b mit unterschiedlich wählbarer Höhe h, einen kegelstumpfförmigen Zwischenteil 6c mit einem Konus, der einer Montage-Befestigung im Ansatzhohlraum durch loses Verstemmen dient, und einem kegelstumpfförmigen Vorderteil 6d mit einem Konus mit ebener kreisförmiger Kontaktfläche 6e, die durch entsprechende Bearbeitungsverfahren wie Schleifen oder dergleichen mit der entsprechend hohen Oberflächengüte versehen sind.Each one-piece pressure body 6 has a plurality of sections, namely a frustoconical seat 6a, a cylindrical intermediate part 6b with a differently selectable height h, a frustoconical intermediate part 6c with a cone, which is used for mounting in the neck cavity by loose caulking, and a frustoconical front part 6d with a cone with a flat circular contact surface 6e, which are provided with the correspondingly high surface quality by appropriate processing methods such as grinding or the like.

Die Neigung des konusförmigen Sitzes 6a des Druckkörpers 6 ist um den Winkel Δϕ geringer als die Neigung des konusförmigen Sitzes 4 im Ansatz 2 ; außerdem ist der Durchmesser des Wandungsteils 5 des Ansatzes 2 größer als der größte Durchmesser des Druckkörpers 6, so daß die erforderliche kippbewegliche Lagerung des Druckkörpers 6 zur Selbsteinstellung vorliegt.The inclination of the conical seat 6a of the pressure body 6 is smaller by the angle Δϕ than the inclination of the conical seat 4 in the neck 2; in addition, the diameter of the wall part 5 of the neck 2 is larger than the largest diameter of the pressure body 6, so that the required tiltable mounting of the pressure body 6 is available for self-adjustment.

Sind entsprechend große Kontaktflächen 6e nötig, dann ist der größte Durchmesser des Druckkörpers 6 und der entsprechende Durchmesser im Ansatz 2 größer als die größte Höhe H des Ansatz-Profils, so daß der Wandungsteil 5 oben und unten Öffnungen 7a, 7b aufweist. - Ist der größte Durchmesser des Druckkörpers 6 hingegen kleiner als die maximale Höhe H des Ansatz-Profils, ist eine Freifräsung zumindest an der Unterseite des Wandungsteils 5 für den einfachen Austausch bzw. das Entfernen des Druckkörpers 6 vorteilhaft, weil dann eine Angriffsfläche für ein Werkzeug oder dergleichen vorhanden ist. - Die Druckkörper 6 ragen mit ihren Kontaktflächen 6e aus den Stirnflächen der Ansätze 2 in Umfangsrichtung hervor.If correspondingly large contact surfaces 6e are necessary, then the largest diameter of the pressure body 6 and the corresponding diameter in the extension 2 is greater than the greatest height H of the extension profile, so that the wall part 5 has openings 7a, 7b at the top and bottom. - If the largest diameter of the pressure body 6, however, is smaller than the maximum height H of the neck profile, a free milling is at least on the underside of the wall part 5 is advantageous for the simple replacement or removal of the pressure element 6, because then there is an engagement surface for a tool or the like. - The pressure bodies 6 protrude with their contact surfaces 6e from the end faces of the approaches 2 in the circumferential direction.

Zwischen dem konusförmigen Sitz 4 im Ansatz 2 und dem konusförmigen Sitz 6e am Druckkörper 6 kann noch eine dünne Schicht aus Kunststoff, eine galvanisch auf den Druckkörper aufgebrachte Zwischenschicht oder ähnliches vorgesehen sein.Between the conical seat 4 in the neck 2 and the conical seat 6e on the pressure body 6, a thin layer of plastic, an intermediate layer applied galvanically to the pressure body or the like can also be provided.

Die Druckkörper 6 aus entsprechendem Hartmetall sind paarweise an zwei benachbarten Ansätzen 2 angewendet. - Prinzipiell ist aber auch der Einsatz nur jeweils eines Druckkörpers an einem der Ansätze 2 und sein Zusammenwirken mit der ebenen Stirnfläche des benachbarten Ansatzes an der nächsten Schaufel denkbar. Dazu ist es aber erforderlich, einen geeigneten Werkstoff für den Druckkörper zu wählen, der mit der stählernen Ansatz-Stirnfläche, ohne zu Fressen oder dergleichen zu neigen, zusammenwirkt. Ein geeigneter Werkstoff für die Druckkörper wären z. B. bestimmte Bronzen.The pressure bodies 6 made of the corresponding hard metal are applied in pairs to two adjacent approaches 2. - In principle, however, it is also conceivable to use only one pressure element on one of the lugs 2 and its interaction with the flat end face of the adjacent lug on the next blade. For this purpose, however, it is necessary to choose a suitable material for the pressure body, which interacts with the steel attachment end face, without tending to eat or the like. A suitable material for the pressure body would be, for. B. certain bronzes.

Da die Spaltbreite As zwischen jeweils zwei benachbarten Ansätzen 2 aus Fertigungsgründen über den Umfang streut, werden entsprechende Druckkörper 6 mit unterschiedlicher, der jeweiligen Spaltbreite angepaßter Höhe h ausgewählt, derart, daß nach dem Einbringen der Druckkörper 6 in die Öffnungen 7 in den Ansätzen 2 die Spaltbreiten über den Umfang annähernd gleich sind. - Nach dem radialen Einbau der Laufschaufeln ist in dem bevorzugten Anwendungsbeispiel keine tangentiale Vorspannung vorhanden.Since the gap width As between two adjacent approaches 2 scatters the circumference for manufacturing reasons, corresponding pressure elements 6 with different height h, adapted to the respective gap width, are selected such that after the introduction of the pressure elements 6 into the openings 7 in the approaches 2 Gap widths are approximately the same over the circumference. - After the radial installation of the blades, there is no tangential preload in the preferred application example.

Die Druckkörper 6 können durch zwei leichte, die Selbsteinstellung der Druckkörper nicht behindernde Montagesicherungen 8 am Herausfallen gehindert werden, falls Laufschaufeln nach der Erstmontage nochmals ausgebaut werden müssen.The pressure elements 6 can be prevented from falling out by two light mounting locks 8 which do not hinder the self-adjustment of the pressure elements if rotor blades have to be removed again after the initial installation.

Die Druckkörper 6 sind selbsteinstellend, weil beim Drehen des Schaufelkranzes infolge des Momentes FT - m - wobei FT die Umfangskraftkomponente und m der Abstand der Druckkörperkante zur Druckkörpersymmetrieachse 9 bedeuten - eine Drehung des Druckkörpers bis zu der aus der unterschiedlichen Neigung der Sitze resultierende Winkeldifferenz Δϕ - die bei genauer Fertigung in der Größenordnung von 15' bis 30' (Winkelminuten) liegt - erfolgt, so daß die aus Fertigungsgründen immer vorhandenen Abweichungen aus der parallelen Lage (Exzentrizität e) ausgeglichen werden. - Nach erfolgter Selbsteinstellung liegen die Kontaktflächen, wie vorher bereits erwähnt, so schräg zur Umfangsrichtung, daß Selbsthemmung bei Verschiebungen jeweils zweier benachbarter kreisförmiger Kontaktflächen 6e mit Sicherheit vermieden sind.The pressure elements 6 are self-adjusting because when the blade ring is rotated as a result of the moment F T - m - where F T is the circumferential force component and m is the distance between the pressure element edge and the pressure element symmetry axis 9 - the pressure element rotates up to the angular difference resulting from the different inclination of the seats Δϕ - which is in the order of 15 'to 30' (angular minutes) in the case of precise production - so that the deviations from the parallel position (eccentricity e) which are always present for production reasons are compensated for. - After self-adjustment, the contact surfaces are, as previously mentioned, so inclined to the circumferential direction that self-locking with displacements of two adjacent circular contact surfaces 6e are avoided with certainty.

Die Druckkörper 6 erhalten durch Höchstlast, z. B. beim bei Überdrehzahl (= über der Nenndrehzahl der Turbine liegende Drehzahl) stattfindenden Schleudern, durch einmaliges örtliches Fließen des Druckkörper-Sitzes 6a bis zur ringförmigen Auflage im Bindungselement (Ansatz 2) ihre endgültige Plazierung und Bettung, wobei über der Kontaktfläche 6e annähernd gleichförmige Flächenpressungsverteilung anfällt. Dabei wird der von der idealen Ringfläche abweichende, Kegelschnittform aufweisende Sitz durch einmalige Plastifizierung und elastische Bettung kraft-und formschlüssig.The pressure body 6 obtained by maximum load, for. B. at overspeed (= above the nominal speed of the turbine speed) spinning, by one-time local flow of the pressure body seat 6a to the annular support in the binding element (approach 2) their final placement and bedding, with approximately uniform contact surface 6e Surface pressure distribution arises. The conical shape of the seat, which deviates from the ideal ring surface, becomes non-positive and form-fitting due to the unique plasticization and elastic bedding.

Zur Vermeidung von Punktberührung muß ferner über alle in der Kontaktfläche liegende Achsen die Bedingung FT . e/ρ . µ. < M erfüllt sein, wobei bedeuten :

  • FT Umfangskraftkomponente mit um den Abstand e versetzter Wirkungslinie gegenüber der Druckkörpersymmetrieachse 9
  • e Exzentrizität
  • p senkrechte Entfernung der Druckkörperauflage von der Druckkörper-Längsmittelebene
  • µ Reibungskoeffizient
  • M Biegemoment
In order to avoid point contact, the condition F T must also apply to all axes lying in the contact area. e / ρ. µ. <M must be fulfilled, where:
  • F T circumferential force component with an action line offset by the distance e with respect to the pressure body axis of symmetry 9
  • e eccentricity
  • p Vertical distance of the pressure hull support from the longitudinal plane of the pressure hull
  • µ coefficient of friction
  • M bending moment

Die Laufschaufeln 1 können auch durch Wahl entsprechender Höhen h mit solchen Druckkörpern ausgerüstet werden, daß beim Einbau der Spalt zwischen den Druckkörpern 6 Null ist, oder daß ein tangentiales Übermaß gegeben ist, so daß nach dem Einbau der Schaufeln bereits bei ruhendem Turbinenschaufelkranz eine gewünschte tangentiale Vorspannung zwischen den Ansätzen 2 mit den Druckkörpern 6 vorhanden ist, wobei die Vorspannung im Betriebszustand der Turbine noch verstärkt wird.The blades 1 can also be equipped with such pressure bodies by selecting appropriate heights h that the gap between the pressure bodies 6 is zero when installing, or that there is a tangential oversize, so that after the installation of the blades a desired tangential already with the turbine blade ring at rest Bias is present between the lugs 2 with the pressure bodies 6, the bias being increased in the operating state of the turbine.

Die erfindungsgemäße Bindung ist prinzipiell auch bei geraden Schaufeln anwendbar ; nur muß hier durch geeignete Maßnahmen dafür gesorgt werden, daß sich die Kontaktflächen bzw. die Ansätze mit Druckkörpern sowohl in Ruhe, als auch im Lauf der Turbinen bzw. Verdichterschaufein mit entsprechender Umfangskraft gegeneinander abstützen.In principle, the binding according to the invention can also be used with straight blades; only appropriate measures must be taken to ensure that the contact surfaces or the lugs with pressure bodies are supported against one another with appropriate circumferential force both at rest and in the course of the turbines or compressor blades.

Auch bei axial montierbaren Laufschaufeln, z. B. Schaufeln mit Tannenbaumfuß, sind die Druckkörper, auch nach Montage der Schaufeln im Radkranz, ohne montagebedingte Einschränkung des Reibwinkels ϕµ einsetzbar. Wenn der Spalt zwischen den Ansätzen für die Montage nicht groß genug ist und die Laufschaufeln nicht entsprechend weit auseinander gedrückt werden können, müssen die Druckkörper im oberen Bereich auf gegenüberliegenden Seiten abgeschnitten werden, derart, daß die Breite des Druckkörpers zwischen den abgeschnittenen, geraden, parallelen Flächen etwas geringer ist als die Breite der Öffnung im Ansatz 2. Der abgeschnittene Druckkörper wird radial, senkrecht zur Turbinenachse durch die Öffnung eingeschoben und dann um 90° gedreht, so daß die runden Abschnitte den entsprechenden runden Abschnitten des Wandungsteils 5 gegenüberliegen. Es müssen übrigens auch nicht, wie aus Figur 2 ersichtlich, zwei gegenüberliegende Öffnungen 7 vorhanden sein, sondern es genügt auch eine Öffnung, die man vorzugsweise unten am Ansatz 2 in dessem äußeren Bereich vorsehen wird.Even with axially mountable blades, e.g. B. shovels with a fir tree base, the pressure hulls can be used without assembly-related restriction of the friction angle ϕµ, even after assembly of the blades in the wheel rim. If the gap between the lugs for the assembly is not large enough and the blades cannot be pressed apart far enough, the pressure bodies in the upper area must be cut off on opposite sides, such that the width of the pressure body between the cut, straight, parallel ones Areas is slightly less than the width of the opening in the neck 2. The cut pressure body is inserted radially, perpendicular to the turbine axis through the opening and then rotated by 90 °, so that the round sections are opposite the corresponding round sections of the wall part 5. Incidentally, as can be seen from FIG. 2, there also need not be two opposite openings 7, but an opening is also sufficient, which will preferably be provided at the base 2 in its outer area.

Ist - wie im gezeichneten Ausführungsbeispiel dargestellt - bei den Laufschaufeln in Ruhe jeweils ein geringer, konstanter Spalt zwischen den gegenüberliegenden Druckkörpern 6 vorhanden, dann wird im Lauf - da sich die Ansätze 2 durch Drehung der Schaufeln nähern oder aufbiegen - der Spalt zunächst Null und später entsteht ein gewisses tangentiales Übermaß mit daraus resultierender tangentialer Spannung, so daß die Druckkörper 6 unter entsprechend hohem Druck stehen, was eine vor allem in Umfangsrichtung sehr wirksamen Abstützung ergibt.Is - as in the illustrated embodiment shown - each with a small, constant gap between the opposing pressure elements 6 at rest in the rotor blades, then in the barrel - since the lugs 2 approach or bend due to rotation of the blades - the gap initially becomes zero and later a certain tangential excess occurs resulting tangential tension, so that the pressure bodies 6 are under a correspondingly high pressure, which results in a support which is very effective, particularly in the circumferential direction.

Dehnen sich die Ansätze 2 - z. B. durch Erwärmung - in Umfangsrichtung, dann gestatten die Schaufeln durch eigenes Verdrehen den Ansätzen 2 die der Dehnung entsprechende Lage einzunehmen, wobei die Kontaktflächen sich gegeneinander verschieben und die Kontaktflächen durch die Selbsteinstellung der Druckkörper parallel bleiben.Do approaches 2 - z. B. by heating - in the circumferential direction, then allow the blades by their own twisting the approaches 2 to take the position corresponding to the expansion, the contact surfaces shifting against each other and the contact surfaces remain parallel by the self-adjustment of the pressure body.

Bevorzugtes Anwendungsgebiet der erfindungsgemäßen Bindung sind Endschaufeln im Niederdruckteil großer Dampfturbinen. Die erfindungsgemäße Bindung ist grundsätzlich jedoch auch bei Schaufelkränzen anderer Dampfturbinenstufen, bei Schaufelkränzen von Verdichtern, Gasturbinen und dergleichen anwendbar.The preferred application of the binding according to the invention are end blades in the low-pressure part of large steam turbines. In principle, however, the binding according to the invention can also be used in the case of blade rings of other steam turbine stages, in the case of blade rings of compressors, gas turbines and the like.

Claims (10)

1. Method of tying the moving blades of a thermal turbo-machine by projections extending in the circumferential direction which are rigidly connected in pairs to their allied moving blade and, at least during operation of the turbine or compressor bear against each other via plane contact faces, characterized in that one or both contact faces per adjacent pair of projections (2) are formed by the plane end face or faces of one or two button elements (6) each formed with a conical bearing surface (6a), in that each button (6) is tiltably supported in a cavity in the projection having a conical seat (4) whose angle is steeper than the angle of the button bearing surface (6a), and in that each button (6) is self-aligning due to the moment FT contact m, is imparted its final position and bedding under the overspeed test force (FT overspeed) and transmits the bending moment FT - e in a self-locking manner where FT is the circumferential force component and e the eccentric position or, respectively m the distance of the edge of the button from the symmetry axis (9) of the button.
2. Method of tying blades as in Claim 1, characterized in that each button (6) is conically chamfered at its front end (front part 6a).
3. Method of tying blades as in Claims 1 and 2, characterized in each button (6) is formed with a cylindrical section (6b) between its conical bearing surface (6a) and its front part (6d) which typically is conical.
4. Method of tying blades as in Claim 3, characterized in that buttons (6) with different heights of the cylindrical section (6b) are used over the blade row.
5. Method of tying blades as in Claim 3, characterized in that each button (6) is formed with a conical section (6c) between the cylindrical section (6b) and the front part (6d) which typically is conical.
6. Method of tying blades as in Claims 1 to 5, characterized in that the buttons (6) consist of a material with minimum differences between the static friction and sliding friction, minimum or no porosity, high compression and bending strength and high corrosion resistance.
7. Method of tying blades as in Claims 1 to 5, characterized in that the buttons (6) consist of a material with minimum differences between the static friction and sliding friction, minimum or no porosity, high compression and bending strength, high corrosion resistance and high wearing resistance.
8. Method of tying blades as in Claim 1, where a front cylindrical section of the cavity wall adjoins the conical seat in the blade projection, characterized in that the cavity wall (5) is formed at the bottom and/or top with a corresponding opening (7).
9. Method of tying blades as in Claim 8, characterized in that each button (6) is cut off at the side symmetrically to its longitudinal centre plane in a manner that the distance between its straight sides is slightly smaller than the width of the opening or openings (7) in the cavity wall (5) of the projection.
EP86106150A 1985-05-14 1986-05-06 Blade-to-blade connection for the rotor of a turbo machine Expired EP0202531B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19853517283 DE3517283A1 (en) 1985-05-14 1985-05-14 BINDING BLADES OF A THERMAL TURBO MACHINE
DE3517283 1985-05-14

Publications (2)

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EP0202531A1 EP0202531A1 (en) 1986-11-26
EP0202531B1 true EP0202531B1 (en) 1988-08-17

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EP86106150A Expired EP0202531B1 (en) 1985-05-14 1986-05-06 Blade-to-blade connection for the rotor of a turbo machine

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EP (1) EP0202531B1 (en)
CS (1) CS271330B2 (en)
DE (1) DE3517283A1 (en)
IN (1) IN167677B (en)
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ZA (1) ZA863523B (en)

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US4798519A (en) * 1987-08-24 1989-01-17 United Technologies Corporation Compressor part span shroud
US5695323A (en) * 1996-04-19 1997-12-09 Westinghouse Electric Corporation Aerodynamically optimized mid-span snubber for combustion turbine blade
DE10328310A1 (en) 2003-06-23 2005-01-13 Alstom Technology Ltd Method of modifying the coupling geometry of shroud segments of turbine blades
DE10342207A1 (en) 2003-09-12 2005-04-07 Alstom Technology Ltd Blade binding of a turbomachine
EP1944466A1 (en) * 2007-01-10 2008-07-16 Siemens Aktiengesellschaft Coupling of two rotor blades
EP2116693A1 (en) * 2008-05-07 2009-11-11 Siemens Aktiengesellschaft Rotor for a turbomachine
EP2669477B1 (en) * 2012-05-31 2017-04-05 General Electric Technology GmbH Shroud for airfoils

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DE818806C (en) * 1949-02-17 1951-10-29 Escher Wyss Ag Blading on rotors of axially flowed through, strongly twisted blades having centrifugal machines, in particular steam, gas turbines and compressors
US2957675A (en) * 1956-05-07 1960-10-25 Gen Electric Damping means
US2942843A (en) * 1956-06-15 1960-06-28 Westinghouse Electric Corp Blade vibration damping structure
CH418360A (en) * 1962-11-21 1966-08-15 Ass Elect Ind Turbo engine
AT252962B (en) * 1964-09-25 1967-03-10 Elin Union Ag Support of turbine blades
GB1121194A (en) * 1967-05-01 1968-07-24 Rolls Royce Bladed rotor for a fluid flow machine
US3719432A (en) * 1971-04-23 1973-03-06 Gen Electric Articulated sleeve for turbine bucket lashing
JPS5632441B2 (en) * 1973-11-30 1981-07-28
FR2329845A1 (en) * 1975-10-28 1977-05-27 Europ Turb Vapeur PROVISION FOR CONTINUOUS LINKAGE OF MOBILE BLADES OF A TURBO-MACHINE
FR2337251A1 (en) * 1975-12-29 1977-07-29 Europ Turb Vapeur TURBOMACHINE MOBILE STAGE
JPS54125307A (en) * 1978-03-24 1979-09-28 Toshiba Corp Connecting device for turbine movable blades
GB2033492A (en) * 1978-11-08 1980-05-21 Northern Eng Ind Interconnecting turbine blades
JPS572405A (en) * 1980-06-05 1982-01-07 Hitachi Ltd Rotary blade connector of axial-flow rotary machine
GB2105414B (en) * 1981-09-08 1985-02-13 Northern Eng Ind Axial-flow steam turbine wheel

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DE3517283C2 (en) 1988-05-19
ZA863523B (en) 1987-01-28
YU44289B (en) 1990-04-30
EP0202531A1 (en) 1986-11-26
CS271330B2 (en) 1990-09-12
DE3517283A1 (en) 1986-11-20
CS348486A2 (en) 1990-02-12
IN167677B (en) 1990-12-08

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