EP0727564B1 - Vibration damping for turbine blades - Google Patents

Vibration damping for turbine blades Download PDF

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Publication number
EP0727564B1
EP0727564B1 EP96810059A EP96810059A EP0727564B1 EP 0727564 B1 EP0727564 B1 EP 0727564B1 EP 96810059 A EP96810059 A EP 96810059A EP 96810059 A EP96810059 A EP 96810059A EP 0727564 B1 EP0727564 B1 EP 0727564B1
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EP
European Patent Office
Prior art keywords
blades
blade
ring
cover plates
damping
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP96810059A
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German (de)
French (fr)
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EP0727564A1 (en
Inventor
Peter Dr. Ernst
Jakob Dr. Rhyner
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ABB Research Ltd Switzerland
ABB Research Ltd Sweden
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ABB Research Ltd Switzerland
ABB Research Ltd Sweden
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Publication of EP0727564A1 publication Critical patent/EP0727564A1/en
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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
    • F01D5/14—Form or construction
    • F01D5/16—Form or construction for counteracting blade vibration
    • 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
    • F01D5/26—Antivibration means not restricted to blade form or construction or to blade-to-blade connections or to the use of particular materials

Definitions

  • the invention relates to a device for damping Blade vibrations of an axially flowed turbomachine, where the ends of the rotating blades against the sealing the flow-limiting wall of a turbine housing.
  • the rotating blades are for a specific one Field of operating conditions designed without resonance. Due to varying operating conditions, e.g. Changes in volume flow of the flowing work equipment or back pressure operation in the border area, the blades become vibrations stochastically excited. In the case of vibration resonance, these lead mechanical stresses for blade failure.
  • the invention has for its object a device for vibration damping for turbine blades at the beginning shown type, in which each shovel individually and is steamed smoothly.
  • the advantages of the invention can be seen, inter alia, in the fact that the blades are not coupled to contact surfaces of damping devices rubbing against one another, such as cover plates, damper wires or bolts.
  • the blades are individually damped without friction and thus free of wear. It is also advantageous that, when axially installed in a turbine wheel, the assembly of individual blades is simplified, since no tangential damping structures of adjacent blades overlap one another.
  • blade cover plates be made of aluminum, because with this choice of material good electrical properties with low specific Connect weight. Centrifugal forces in the order of magnitude, as they occur with known cover plate damping because of the much smaller and therefore lighter cover plate construction of the invention reduced to. this means reduced mechanical stress for the turbine blade.
  • FIG. 1 shows a section of a turbine housing 1, which is radially opposite a blade end 8 of a turbine rotor blade 2.
  • the blade shown is an end blade, for example an LP steam turbine.
  • a ring 4 made of permanent magnetic material is attached at a designated point on the turbine housing 1 around a not shown, bladed turbine wheel.
  • This magnetic ring 4 consists of partial rings 6, which are combined in a housing 5 made of austenitic steel and fastened with this in the turbine housing 1.
  • the magnetic ring 4 is divided into three partial rings 6 with alternating magnetic polarization 7a, b, c, the polarization scheme SNS being present.
  • the turbine blade 2 which is located radially opposite the magnetic ring 4, has a cover plate 3 at its blade end 8, as shown in FIG. 2.
  • this cover plate 3 When viewed from the top, this cover plate 3 has approximately the shape of a rhombus, the acute-angled corners of which are flattened parallel to the direction of rotation 9 of the turbine blades 2 .
  • the blades 2 are free-standing, ie the cover plates 3 of adjacent blades 2 are dimensioned such that they are not tangentially overlapping and do not touch one another.
  • a preferred alloy for the permanent magnet ring 4 is cobalt samarium (Co-Sm). Because of its good electrical properties and the low specific weight for metals, it is advantageous to manufacture the blade cover plate 3 from aluminum. The low specific weight enables the cover plate 3 of the blades 2 subjected to centrifugal force to be made light. The good electrical conductivity of the aluminum favors the eddy currents and thus, as mentioned above, the damping behavior.
  • the invention is not limited to the exemplary embodiment shown and described.
  • the number of partial rings 6 involved in the magnetic ring 4 and their magnetic polarization 7a, b, c are also conceivable in a different configuration, although a different magnet material could also be preferred to the Co-Sm.
  • the partial rings 6 can also be designed as electrically fed toroidal coils.
  • the design of the blade cover plate 3 is also conceivable from a material other than aluminum. Taking into account the higher specific weight of ferromagnetic metals and their alloys, these materials are also extremely suitable for the production of the cover plates. Their magnetic properties are outstanding here, which means a considerable reduction in the magnetic air gap between a cover plate and the flow-limiting wall. The dissipated vibration energy can thus be increased by favoring the magnetic flux in the cover plate.
  • the invention can also be used in a damping manner in the case of shroud-wheel-bound paddle wheels.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
  • Vibration Prevention Devices (AREA)

Description

TECHNISCHES GEBIETTECHNICAL AREA

Die Erfindung betrifft eine Einrichtung zur Dämpfung von Schaufelschwingungen einer axial durchströmten Turbomaschine, bei welcher die Enden der rotierenden Schaufeln gegen die strömungsbegrenzende Wand eines Turbinengehäuses dichten.The invention relates to a device for damping Blade vibrations of an axially flowed turbomachine, where the ends of the rotating blades against the sealing the flow-limiting wall of a turbine housing.

STAND DER TECHNIKSTATE OF THE ART

Bei Turbomaschinen sind die rotierenden Schaufeln für ein bestimmtes Feld der Betriebsbedingungen resonanzfrei ausgelegt. Durch variierende Betriebsbedingungen, z.B. Volumenstromänderungen des strömenden Arbeitsmittels oder Gegendruckbetrieb im Grenzbereich, werden die Schaufeln stochastisch zu Schwingungen angeregt. Im Fall von Schwingungsresonanz führen diese mechanischen Beanspruchungen zum Versagen der Schaufeln.In turbomachinery, the rotating blades are for a specific one Field of operating conditions designed without resonance. Due to varying operating conditions, e.g. Changes in volume flow of the flowing work equipment or back pressure operation in the border area, the blades become vibrations stochastically excited. In the case of vibration resonance, these lead mechanical stresses for blade failure.

Zur Dämpfung dieser Schwingungen sind verschiedene Einrichtungen entwickelt worden, die die Schaufeln aneinander koppeln und damit schwingungsdämpfend wirken. Bekannte Konzepte sind beispielsweise Dämpferdrähte, Dämpferbolzen, Schaufeldeckplatten, sowie angeschmiedete Nocken mit Stiften.
Derartige Einrichtungen für die Dämpfung von Schaufelschwingungen sind bekannt aus DE B 1 299 004 und US 3 185 441. Dabei sind die Einsatzbereiche der vorgeschlagenen Dämpfungsmittel beschränkt. Bohrungen für die Aufnahme von Dämpferdrähten oder Dämpferbolzen beeinträchtigen die Festigkeit der Schaufelprofile, und die Dämpferdrähte und -bolzen selbst verschlechtern die Strömungseigenschaften des strömenden Arbeitmittels.
Hohe Fliehkräfte treten nachteilig ins Gewicht bei der Dämpfung mittels Schaufeldeckplatten, die benachbarte Schaufelköpfe zu einem geschlossenen Ring aneinanderkoppeln und durch Reibschluss dämpfend wirken. Die Ausführung und Bearbeitung dieser Schaufeldeckplatten, sowie die Schaufelmontage mit diesen Deckplatten ist wegen der geforderten Massgenauigkeit aufwendig und teuer.
Hinzu kommt, dass bei den Dämpfungseinrichtungen, die auf Reibschluss benachbarter Schaufeln basieren, durch eine Abnützung der Kontaktflächen, die geforderte Dämpfung beeinträchtigt wird und somit Revisionen nötig sind.Various devices have been developed to dampen these vibrations, which couple the blades to one another and thus have a vibration-damping effect. Known concepts are, for example, damper wires, damper bolts, blade cover plates and forged cams with pins.
Such devices for damping blade vibrations are known from DE B 1 299 004 and US 3 185 441. The fields of use of the proposed damping means are limited. Bores for receiving damper wires or damper bolts impair the strength of the blade profiles, and the damper wires and bolts themselves impair the flow properties of the flowing working fluid.
High centrifugal forces adversely affect damping by means of blade cover plates, which couple adjacent blade heads together to form a closed ring and have a damping effect due to frictional engagement. The execution and processing of these blade cover plates, as well as the blade assembly with these cover plates, is complex and expensive because of the required dimensional accuracy.
In addition, the damping devices that are based on the frictional engagement of adjacent blades, due to wear on the contact surfaces, impair the required damping and therefore require revisions.

Außerdem ist aus dem Stand der Technik z.Bsp. das Dokument US-A-5 490 759 bekannt.In addition, for example. the document US-A-5 490 759 is known.

DARSTELLUNG DER ERFINDUNGPRESENTATION OF THE INVENTION

Der Erfindung liegt die Aufgabe zugrunde, eine Einrichtung zur Schwingungsdämpfung für Turbinenschaufeln der eingangs genannten Art darzustellen, bei der jede Schaufel individuell und reibungslos gedämpft wird.The invention has for its object a device for vibration damping for turbine blades at the beginning shown type, in which each shovel individually and is steamed smoothly.

Erfindungsgemäss wird dies dadurch erreicht, dass auf der strömungsbegrenzenden Wand des Turbinengehäuses in radialer Richtung gegenüber den Schaufelenden ein Ring aus permanentmagnetischem Material angebracht ist, der aus mindestens einem oder mehreren Teilringen gleicher oder unterschiedlicher magnetischer Polarisation besteht, und dass die Schaufelenden mit je einer Deckplatte versehen sind, welche aus einem elektrisch gut leitenden Material besteht.According to the invention this is achieved in that on the flow-limiting wall of the turbine housing in radial A ring made of permanent magnetic towards the blade ends Material is made up of at least one or several partial rings of the same or different magnetic polarization exists and that the blade ends are each provided with a cover plate which consists of a there is good electrical conductivity.

Die Vorteile der Erfindung sind unter anderem darin zu sehen, dass die Schaufeln nicht gekoppelt sind an Kontaktflächen von aneinander reibenden Dämpfungseinrichtungen wie Deckplatten, Dämpferdrähte oder -bolzen. Bei der vorgeschlagenen Dämpfungseinrichtung werden die Schaufeln reibungs- und damit verschleissfrei individuell gedämpft.
Vorteilhaft ist ferner, dass bei axialem Einbau in ein Turbinenrad die Montage einzelner Schaufeln vereinfacht ist, da keine tangentialen Dämpfungskonstruktionen benachbarter Schaufeln einander überlappen.The advantages of the invention can be seen, inter alia, in the fact that the blades are not coupled to contact surfaces of damping devices rubbing against one another, such as cover plates, damper wires or bolts. In the proposed damping device, the blades are individually damped without friction and thus free of wear.
It is also advantageous that, when axially installed in a turbine wheel, the assembly of individual blades is simplified, since no tangential damping structures of adjacent blades overlap one another.

Es ist besonders zweckmässig, wenn die Schaufeldeckplatten aus Aluminium gefertigt werden, da sich bei dieser Materialwahl gute elektrische Eigenschaften mit geringem spezifischen Gewicht verbinden. Auch Fliehkräfte in der Grössenordnung, wie sie bei bekannten Deckplattendämpfungen vorkommen, treten wegen den wesentlich kleineren und damit leichteren Deckplattenkonstruktion der Erfindung reduziert auf. Dies bedeutet für die Turbinenschaufel eine verminderte mechanische Beanspruchung.It is particularly useful if the blade cover plates be made of aluminum, because with this choice of material good electrical properties with low specific Connect weight. Centrifugal forces in the order of magnitude, as they occur with known cover plate damping because of the much smaller and therefore lighter cover plate construction of the invention reduced to. this means reduced mechanical stress for the turbine blade.

KURZE BESCHREIBUNG DER ZEICHNUNGBRIEF DESCRIPTION OF THE DRAWING

In der Zeichnung ist ein Ausführungsbeispiel der Erfindung vereinfacht dargestellt.
Es zeigen:

Fig.1
einen Teillängsschnitt einer Schaufelspitze mit einem radial gegenüberliegenden Magnetring;
Fig.2
einen Schnitt nach Linie II-II gemäss Fig.1.
In the drawing, an embodiment of the invention is shown in simplified form.
Show it:
Fig. 1
a partial longitudinal section of a blade tip with a radially opposite magnetic ring;
Fig. 2
a section along line II-II according to Fig.1.

Es sind nur die für das Verständnis der Erfindung wesentlichen Elemente gezeigt.
Nicht dargestellt in der Zeichnung ist ein Turbinenschaufelfuss und eine Montageansicht der Schaufel in einem Turbinenrad. Only the elements essential for understanding the invention are shown.
Not shown in the drawing is a turbine blade root and an assembly view of the blade in a turbine wheel.

WEG ZUR AUSFÜHRUNG DER ERFINDUNGWAY OF CARRYING OUT THE INVENTION

In Fig.1 ist von einem Turbinengehäuse 1 ein Ausschnitt gezeigt, der einem Schaufelende 8 einer Turbinenlaufschaufel 2 radial gegenüberliegt. Wie aus dem Überschallschaufelprofil in Fig.2 erkennbar, handelt es sich bei der dargestellten Schaufel um eine Endschaufel, beispielsweise einer ND-Dampfturbine. In Umfangsrichtung ist an bezeichneter Stelle des Turbinengehäuses 1 um ein nicht dargestelltes, beschaufeltes Turbinenrad ein Ring 4 aus permanentmagnetischem Material angebracht. Dieser Magnetring 4 besteht aus Teilringen 6, die in einem Gehäuse 5 aus austenitischem Stahl zusammengefasst sind und mit diesem im Turbinengehäuse 1 befestigt sind. Dabei ist der Magnetring 4 in drei Teilringe 6 mit einander abwechselnder magnetischer Polarisation 7a,b,c unterteilt, wobei das Polarisationsschema SNS vorliegt.
Die dem Magnetring 4 radial gegenüberliegende Turbinenschaufel 2 hat an deren Schaufelende 8, wie Fig. 2 zeigt, eine Deckplatte 3. Diese Deckplatte 3 weist bei radialer Draufsicht annähernd die Form eines Rhombus auf, dessen spitzwinklige Ecken parallel zur Rotationsrichtung 9 der Turbinenschaufeln 2 abgeflacht sind. Die Schaufeln 2 sind freistehend, d.h., die Deckplatten 3 benachbarter Schaufeln 2 sind so bemessen, dass sie tangential nicht überlappend sind und einander nicht berühren.1 shows a section of a turbine housing 1, which is radially opposite a blade end 8 of a turbine rotor blade 2. As can be seen from the supersonic blade profile in FIG. 2, the blade shown is an end blade, for example an LP steam turbine. In the circumferential direction, a ring 4 made of permanent magnetic material is attached at a designated point on the turbine housing 1 around a not shown, bladed turbine wheel. This magnetic ring 4 consists of partial rings 6, which are combined in a housing 5 made of austenitic steel and fastened with this in the turbine housing 1. The magnetic ring 4 is divided into three partial rings 6 with alternating magnetic polarization 7a, b, c, the polarization scheme SNS being present.
The turbine blade 2, which is located radially opposite the magnetic ring 4, has a cover plate 3 at its blade end 8, as shown in FIG. 2. When viewed from the top, this cover plate 3 has approximately the shape of a rhombus, the acute-angled corners of which are flattened parallel to the direction of rotation 9 of the turbine blades 2 . The blades 2 are free-standing, ie the cover plates 3 of adjacent blades 2 are dimensioned such that they are not tangentially overlapping and do not touch one another.

Bei Rotation des nicht dargestellten Turbinenrades in Rotationsrichtung 9 bleibt das magnetische Feld 10 des Permanentmagnetringes 4 für die Schaufeldeckplatte 3 solange konstant, wie die Schaufel 2 keine Schwingbewegung ausübt. Schwingt jedoch die Turbinenschaufel 2, so ist der magnetische Fluss in der Schaufeldeckplatte 3 zeitlich veränderlich. Dieser zeitlich veränderlicher Magnetfluss induziert in der Schaufeldeckplatte 3 Wirbelströme, die zur Produktion von Joule'scher Wärme führen. Diese Energiedissipation hat eine Dämpfung der Schaufelschwingung zur Folge. Die Joule'sche Wärme und damit der Dämpfungseffekt wächst mit der elektrischen Leitfähigkeit des Deckplattenmaterials.When the turbine wheel, not shown, rotates in the direction of rotation 9 remains the magnetic field 10 of the permanent magnet ring 4 constant for the blade cover plate 3, how the blade 2 does not oscillate. Swings however the turbine blade 2, the magnetic flux is in the blade cover plate 3 can be changed over time. This timed Variable magnetic flux induced in the blade cover plate 3 eddy currents used to produce Joule'scher Conduct heat. This energy dissipation has a damping of Blade vibration results. The Joule warmth and therefore the damping effect increases with the electrical conductivity of the cover plate material.

Eine bevorzugte Legierung für den Permanentmagnetring 4 ist Cobalt-Samarium (Co-Sm).
Wegen seiner guten elektrischen Eigenschaften und dem für Metalle geringen spezifischen Gewicht ist es von Vorteil, die Schaufeldeckplatte 3 aus Aluminium zu fertigen.
Das geringe spezifische Gewicht ermöglicht eine leichte Ausführung der Deckplatte 3 der fliehkraftbelasteten Schaufeln 2. Die gute elektrische Leitfähigkeit des Aluminiums begünstigt die Wirbelströme und damit, wie oben erwähnt, das Dämpfungsverhalten.A preferred alloy for the permanent magnet ring 4 is cobalt samarium (Co-Sm).
Because of its good electrical properties and the low specific weight for metals, it is advantageous to manufacture the blade cover plate 3 from aluminum.
The low specific weight enables the cover plate 3 of the blades 2 subjected to centrifugal force to be made light. The good electrical conductivity of the aluminum favors the eddy currents and thus, as mentioned above, the damping behavior.

Selbstverständlich ist die Erfindung nicht auf das gezeigte und beschriebene Ausführungsbeispiel beschränkt. So ist die Anzahl der am Magnetring 4 beteiligten Teilringe 6 und deren magnetische Polarisation 7a,b,c auch in anderer Konfiguration denkbar, wobei auch ein anderer Magnetwerkstoff dem Co-Sm vorgezogen werden könnte.
Weiterhin sind die Teilringe 6 auch als elektrisch gespeiste Ringkernspulen ausführbar.
Im Sinne der Erfindung ist die Ausführung der Schaufeldeckplatte 3 auch aus einem anderen Material als Aluminium denkbar. Unter Inkaufnahme des höheren spezifischen Gewichts von ferromagnetischen Metallen und ihren Legierungen, eignen sich diese Materialien ebenfalls ausserordentlich gut für die Fertigung der Deckplatten. Herausragend sind hier ihre magnetischen Eigenschaften, welche eine erhebliche Verkleinerung des magnetischen Luftspalts zwischen einer Deckplatte und der strömungsbegrenzenden Wand bedeutet. Die dissipierte Schwingungsenergie kann somit durch eine Begünstigung des magnetischen Flusses in der Deckplatte erhöht werden. Selbstverständlich kann die Erfindung auch bei deckbandgebundenen Schaufelrädern zusätzlich dämpfend eingesetzt werden. Of course, the invention is not limited to the exemplary embodiment shown and described. The number of partial rings 6 involved in the magnetic ring 4 and their magnetic polarization 7a, b, c are also conceivable in a different configuration, although a different magnet material could also be preferred to the Co-Sm.
Furthermore, the partial rings 6 can also be designed as electrically fed toroidal coils.
In the sense of the invention, the design of the blade cover plate 3 is also conceivable from a material other than aluminum. Taking into account the higher specific weight of ferromagnetic metals and their alloys, these materials are also extremely suitable for the production of the cover plates. Their magnetic properties are outstanding here, which means a considerable reduction in the magnetic air gap between a cover plate and the flow-limiting wall. The dissipated vibration energy can thus be increased by favoring the magnetic flux in the cover plate. Of course, the invention can also be used in a damping manner in the case of shroud-wheel-bound paddle wheels.

BEZUGSZEICHENLISTEREFERENCE SIGN LIST

11
TurbinengehäuseTurbine casing
22nd
Schaufelshovel
33rd
SchaufeldeckplatteBucket cover plate
44th
Ring aus permanentmagnetischem MaterialRing made of permanent magnetic material
55
austenistisches Stahlgehäuseaustenistic steel case
66
permanentmagnetischer Teilringpermanent magnetic ring
7a,c7a, c
magnetische Polarisation S eines Teilringsmagnetic polarization S of a partial ring
7b7b
magnetische Polarisation N eines Teilringsmagnetic polarization N of a partial ring
88th
SchaufelendeBlade end
99
Rotationsrichtung der Turbinenschaufeln in radialer DraufsichtDirection of rotation of the turbine blades in radial Top view
1010th
Magnetfeldlinien des PermanentmagnetringesMagnetic field lines of the permanent magnet ring

Claims (6)

  1. Device for damping blade vibrations of an axial-flow turbomachine, in which the ends (8) of the rotating blades (2) form a seal towards the flow-limiting wall of a turbine casing (1), characterized in that a ring (4) of permanently magnetic material is attached to the flow-limiting wall of the turbine casing (1) in the radial direction opposite the blade ends (8), which ring (4) consists of at least one or more sectional rings (6) of the same or different magnetic polarization (7a,b), and in that the blade ends (8) are each provided with a cover plate (3) which is made of a material which is a good electrical conductor.
  2. Device according to Claim 1, characterized in that the permanent-magnet ring (4) consists of three sectional rings (6) having the polarization scheme NSN or SNS, and in that this permanent-magnet ring (4) is surrounded by a nonmagnetic housing (5).
  3. Device according to Claim 1, characterized in that adjacent cover plates (3) of the blades (2) do not touch one another.
  4. Device according to Claim 1, characterized in that the cover plates (3) of the blades (2) are produced from aluminium.
  5. Device according to Claim 1, characterized in that the cover plates (3) of the blades (2) are produced from a ferromagnetic material.
  6. Use of the device according to Claim 1 in turbomachines having free-standing blades (2).
EP96810059A 1995-02-17 1996-01-29 Vibration damping for turbine blades Expired - Lifetime EP0727564B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19505389 1995-02-17
DE19505389A DE19505389A1 (en) 1995-02-17 1995-02-17 Vibration damping for turbine blades

Publications (2)

Publication Number Publication Date
EP0727564A1 EP0727564A1 (en) 1996-08-21
EP0727564B1 true EP0727564B1 (en) 1998-11-04

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US (1) US5709527A (en)
EP (1) EP0727564B1 (en)
JP (1) JPH08240103A (en)
KR (1) KR960031759A (en)
CN (1) CN1140230A (en)
CA (1) CA2162933A1 (en)
DE (2) DE19505389A1 (en)
ES (1) ES2126374T3 (en)
HU (1) HU218551B (en)
PL (1) PL312681A1 (en)

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JPS61108802A (en) * 1984-11-02 1986-05-27 Mitsubishi Heavy Ind Ltd Fluid rotary machine
DE3667521D1 (en) * 1985-08-31 1990-01-18 Bbc Brown Boveri & Cie DEVICE FOR DAMPING VIBRATION VIBRATIONS IN TURBO MACHINES.
DE3741451A1 (en) * 1986-12-10 1988-06-23 Nippon Seiko Kk HYDROSTATIC STORAGE SYSTEM
DE59205948D1 (en) * 1991-10-17 1996-05-15 Asea Brown Boveri Device and method for reducing one or more resonant vibrations of rotor blades in turbomachines
US5490759A (en) * 1994-04-28 1996-02-13 Hoffman; Jay Magnetic damping system to limit blade tip vibrations in turbomachines

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2072755A1 (en) 2007-12-21 2009-06-24 Siemens Aktiengesellschaft Magnetic device for dampening blade vibration in turbo engines
US8568088B2 (en) 2007-12-21 2013-10-29 Siemens Aktiengesellschaft Magnetic device for damping blade vibrations in turbomachines

Also Published As

Publication number Publication date
EP0727564A1 (en) 1996-08-21
PL312681A1 (en) 1996-08-19
JPH08240103A (en) 1996-09-17
ES2126374T3 (en) 1999-03-16
DE19505389A1 (en) 1996-08-22
KR960031759A (en) 1996-09-17
DE59600750D1 (en) 1998-12-10
HU218551B (en) 2000-10-28
HU9503685D0 (en) 1996-02-28
HUT76395A (en) 1997-08-28
US5709527A (en) 1998-01-20
CA2162933A1 (en) 1996-08-18
CN1140230A (en) 1997-01-15

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