EP1515001B1 - Blade to blade connection in a turbomachine - Google Patents
Blade to blade connection in a turbomachine Download PDFInfo
- Publication number
- EP1515001B1 EP1515001B1 EP04104236.7A EP04104236A EP1515001B1 EP 1515001 B1 EP1515001 B1 EP 1515001B1 EP 04104236 A EP04104236 A EP 04104236A EP 1515001 B1 EP1515001 B1 EP 1515001B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- support surface
- pressure body
- projection
- contour
- turbomachine
- 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.)
- Not-in-force
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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
- 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
- F01D5/225—Blade-to-blade connections, e.g. for damping vibrations by shrouding
-
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2250/00—Geometry
- F05D2250/20—Three-dimensional
- F05D2250/23—Three-dimensional prismatic
- F05D2250/232—Three-dimensional prismatic conical
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2250/00—Geometry
- F05D2250/20—Three-dimensional
- F05D2250/24—Three-dimensional ellipsoidal
- F05D2250/241—Three-dimensional ellipsoidal spherical
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2260/00—Function
- F05D2260/96—Preventing, counteracting or reducing vibration or noise
Definitions
- the present invention relates to a binding of blades of a turbomachine with the features of the preamble of claim 1.
- Out DE 35 17 283 C2 is a blade binding of the type mentioned, are provided in the lugs, which extend in the circumferential direction, are rigidly connected in pairs with a blade and are supported in each case via at least one pressure body to the circumferentially adjacent approach.
- each pressure body on a support side facing the associated approach to a holding contour which projects into a receptacle formed on the associated approach and is supported therein in the circumferential direction and transversely thereto.
- each pressure body on a side facing the adjacent approach support side on a flat support surface, which is supported on a surface of the adjacent approach associated flat counter-support surface.
- the holding contours of the pressure hull are each formed as a cone.
- the associated receptacles are also formed as a cone, wherein the cone of the retaining contour, however, has a different conicity than the cone of the receptacle. This ensures that manufacturing tolerances of the seat and the pressure body by slight plastic deformation on the outer edge of the cone holder and the Konushaltekontur can be compensated.
- the counter support surface on which the support surface of the pressure hull is supported may be formed in a development of the known blade binding by the support surface of a counter-pressure body, which is identical to the pressure hull.
- the known blade binding works optimally when only relative movements occur during operation of the turbomachine, which run parallel to the support surface.
- the support surface can then slide on the mating support surface.
- not only parallel relative movements occur between the approaches to be supported or to be connected to one another.
- twisting and twisting of the blades and thus of the lugs may occur, resulting in particular in increased vibration loading of the blade tie.
- Rotational movements between the lugs lead to a line or point load of the respective pressure body receptacle, which can lead to a brittle fracture of the hard pressure body or to tearing of the pressure body seat.
- US 4,257,743 shows a coupling device with two approaches, one of which is provided with a fixed pressure body in the form of a hemispherical projection and the other with a hemispherical retaining contour for loosely receiving the hemispherical projection when the adjacent blades are mounted.
- JP 63 132801 U and JP H01 152003 U in that the retaining contour of the pressure body and the contour of the associated receptacle can be formed as complementary cylindrical sections.
- EP202531 a blade binding with cone-shaped pressure bodies.
- the object is to provide an improved embodiment for a blade binding of the type mentioned, which makes it possible to compensate for manufacturing tolerances, games, elastic deformation and similar factors exclusively by a sliding movement.
- the invention is based on the general idea of forming the retaining contour of the pressure hull and the contour of the associated receptacle as complementary ball sections and rigidly fixing the counterpressure elements with respect to their longitudinal center axis, so that the counterpressure body can serve as an abutment for the pressure hull supporting thereon.
- the pressure body is supported flat on the associated approach.
- a ball head bearing of the pressure hull is formed on the associated approach, which allows the pressure hull to rotate its support surface around the ball center.
- the rotatably mounted pressure body can compensate for these relative movements, so that a flat power transmission between the mutually supported or interconnected Ansälzen is always achievable.
- Changing angular positions of the moving blades or of the lugs effect an automatic adjustment of the movably mounted pressure bodies in the case of the bucket binding according to the invention. Voltage peaks are thereby avoided.
- the friction damping is fully accentuated by the flat system. There are no high-frequency tilting movements.
- the ball portion of the retaining contour on a ball center, while the support surface is circular and has a circle center.
- the pressure body is then designed so that a straight line which extends through both the center of the circle and through the center of the sphere, is perpendicular to the support surface plane.
- the pressure body is rotationally symmetrical with respect to these straight lines.
- the counter support surface which is assigned to the adjacent approach and on which the supporting surface of the pressure hull is supported in a planar manner, can be formed, for example, by the support surface of a counterpressure body t, which is held on the adjacent projection.
- the counter-pressure body can not carry out tumbling movements with respect to the normal direction of its counter-support surface. In this way, all compensatory movements are performed exclusively by the ball-bearing pressure body. This ensures that the movable pressure body with appropriate twists of the approaches again and again adjusted by itself to its original position.
- both the retaining contour of the counter-pressure body and the associated receptacle are formed as a cone or a truncated cone, both truncated cones have the same conicity.
- both truncated cones have the same conicity.
- the counter-pressure body is fixed rigidly with respect to its longitudinal central axis at the base and can thereby serve as an abutment for the pressure body supported thereon.
- Fig. 1a and 1b are blades 1 of a turbomachine not shown otherwise equipped with two, lying on different sides of the blade lugs 2.
- These lugs 2 extend in a direction indicated by an arrow circumferential direction 3, in which the blades rotate 1 during operation of the turbomachine.
- the lugs 2 are rigidly connected to the respective blade 1 and in particular can form an integral part of the respective blade 1.
- the lugs 2 are designed in the form of support wings, which have aerodynamic profiles and are usually arranged between the radial ends of the blades 1.
- the lugs 2 can also be designed as cover plates or cover bands, which are connected to the radially outer ends of the Blades 1 are arranged.
- the lugs 2 can also be other binding elements.
- the lugs 2 are not supported directly on each other at their end faces 4, but indirectly via at least one pressure body 7 (cf. Fig. 2 ).
- these pressure body 7 are for simplicity of illustration in the Fig. 1 a and 1 b are not reproduced.
- sectional views of Fig. 2 are each the opposite end portions of a pair of lugs 2, which support each other at least during operation of the turbomachine, reproduced in section, while arranged in this area pressure body 7 is not shown cut. It is clear that the sectional view of the Fig. 2 to 4 may also correspond to a section around the section line II in the plane of the drawing Fig. 1 b rotated by 90 °.
- each pressure body 7 has a spherical holding side 8 and a flat support side 9. While the holding side 8 faces that projection 2 to which the respective pressure body 7 is assigned (according to FIGS Fig. 2 in each case the right-hand projection 2), the support side 9 faces the projection 2 which is adjacent in the circumferential direction 3 (ie according to FIG Fig. 2 in each case the left approach 2). On the holding side 8 a down or projecting holding contour 10 is formed.
- the approach 2, which is associated with the pressure body 7, has on its end face 4 a receptacle 11 into which the holding contour 10 of the pressure body 7 is inserted.
- the retaining contour 10 thus protrudes into the receptacle 11 and can are supported in the circumferential direction 3 and transverse to the circumferential direction 3, according to the invention, the holding contour 10 is now formed as a ball portion.
- the receptacle 11 is also formed as a ball section.
- the ball sections have the same radius R, whereby the ball portion of the retaining contour 10 is flat on the ball portion of the receptacle 11 to the plant.
- the pressure body 7 according to the invention thereby forms a kind of ball joint, which is mounted in a joint socket about a spherical center 12 movably on the associated projection 2.
- the joint socket is formed here by the receptacle 11.
- the radii of pressure body 7 and receptacle 11 may also differ slightly from one another.
- the pressure body 7 has on its support side 9 a flat support surface 13. As shown in Fig. 2 it emerges, the pressure body 7 is supported at least during operation of the turbomachine with its support surface 13 on a mating support surface 14 which is associated with the adjacent support wing 2.
- the counter-support surface 14 is also configured so that the support surfaces 13 and 14 rest flat against one another.
- the pressure body 7 of the invention between the interconnected lugs 2 comparatively large forces F transmitted in the circumferential direction 3.
- forces F transmitted in the circumferential direction 3.
- by the friction and coupling moments M between adjacent blades 1 can be transmitted via the interconnected lugs 2.
- Due to the movable mounting of the pressure hull 7 on the associated approach 2 also Drehver einen or twists between adjacent blades 1 and between mutually supported lugs 2 can be compensated.
- the blade binding according to the invention can thus compensate for the rotational movements and different angular positions of the lugs 2 possibly occurring during operation, in particular during startup and shutdown, without resulting in greater elastic or even plastic deformation.
- the geometry of the support body 7 is suitably chosen so that the support surface 13 is configured circular and has a circle center point 15.
- the spherical holding contour 10 is matched to the flat support surface 13, that a straight line 16, which extends through both the center of the circle 15 and through the ball center 12, is perpendicular to the plane of the support surface 13. This results in a rotational symmetry for the pressure body 7, so that the storage achieved thereby acts in all directions as it were.
- the counter support surface 14 may also be formed on a special abutment element 17.
- This abutment element 17 is fixed to the front side 4 of the adjacent projection 2, in particular by soldering or welding.
- the abutment member 17 is designed as a plate which is inserted into the end face 4 of the adjacent lug 2 and disposed therein sunk.
- the counter-support surface 14 is also formed on a counter-pressure member 18.
- the counterpressure body 18 has - just like the pressure body 7 - a support side 19 with a flat support surface which forms the counter support surface 14.
- the counter pressure element 18 is also provided with a holding side 20 on which a holding contour 21 is formed.
- the holding contour 21 of the counterpressure body 18 is inserted into a corresponding receptacle 22, which is formed in the adjacent projection 2.
- the shaping of the retaining contour 21 of the counterpressure body 18 and the cooperating receptacle 22 are matched to one another such that the counter support surface 14 of the counter-pressure member 18 is fixed spatially relative to the associated approach 2.
- the retaining contour 21 is formed as a cone, while fitting the associated receptacle 22 is designed as a cone, which has the same taper as the cone of the retaining contour 21. Consequently, the retaining contour 21 of the counterpressure body 18 abuts flat against the receptacle 22. Although it is in principle still possible to rotate the counter-pressure member 18 about its longitudinal central axis, but the plane of its counter-support surface 14 remains invariant relative to the associated approach 2.
- the support surfaces 13 and / or the counter support surfaces 14 may be provided with a low-friction coating (not shown). At the same time, the frictional forces occurring in the plane of the support surfaces 13 and the counter support surfaces 14 can be reduced by this measure.
- the pressure bodies 7 or the counterpressure bodies 18 may be formed from a suitable hard metal, at least in a section having the support surface 13 or the counter support surface 14.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Turbine Rotor Nozzle Sealing (AREA)
Description
Die vorliegende Erfindung betrifft eine Bindung von Laufschaufeln einer Turbomaschine mit den Merkmalen des Oberbegriffs des Anspruchs 1.The present invention relates to a binding of blades of a turbomachine with the features of the preamble of
Aus
Die bekannte Laufschaufelbindung funktioniert optimal, wenn im Betrieb der Turbomaschine ausschließlich Relativbewegungen auftreten, die parallel zur Stützfläche verlaufen. Die Stützfläche kann dann an der Gegenstützfläche abgleiten. In der Praxis treten jedoch nicht nur parallel geführte Relativbewegungen zwischen den aneinander abzustützenden bzw, miteinander zu verbindenden Ansätzen auf. Insbesondere beim Hochfahren einer Turbine oder bei bestimmten Schwachlast-Betriebsphasen, z.B. während der Ventilation in der letzten Turbinenstufe, kann es zu Verwindungen und Verdrehungen der Laufschaufeln und somit der Ansätze kommen, was insbesondere zu einer verstärkten Schwingungsbeanspruchung der Schaufelbindung führt. Drehbewegungen zwischen den Ansätzen führen jedoch zu einer Linien- oder Punktbelastung der jeweiligen Druckkörperaufnahme, was zu einem Sprödbruch des harten Druckkörpers bzw. zur Anrissbildung des Druckkörpersitzes führen kann.The known blade binding works optimally when only relative movements occur during operation of the turbomachine, which run parallel to the support surface. The support surface can then slide on the mating support surface. In practice, however, not only parallel relative movements occur between the approaches to be supported or to be connected to one another. In particular, when starting up a turbine or at certain light load operating phases, e.g. During ventilation in the last turbine stage, twisting and twisting of the blades and thus of the lugs may occur, resulting in particular in increased vibration loading of the blade tie. Rotational movements between the lugs, however, lead to a line or point load of the respective pressure body receptacle, which can lead to a brittle fracture of the hard pressure body or to tearing of the pressure body seat.
Des weiteren offenbaren
Ferner offenbart die
Der Erfindung, wie sie in den Ansprüchen gekennzeichnet ist, liegt die Aufgabe zugrunde, für eine Laufschaufelbindung der eingangs genannten Art eine verbesserte Ausführungsform anzugeben, die es erlaubt, Fertigungstoleranzen, Spiele, elastische Verformung und ähnliche Faktoren ausschliesslich durch eine Gleitbewegung auszugleichen.The invention, as characterized in the claims, the object is to provide an improved embodiment for a blade binding of the type mentioned, which makes it possible to compensate for manufacturing tolerances, games, elastic deformation and similar factors exclusively by a sliding movement.
Erfindungsgemäß wird diese Aufgabe durch den Gegenstand des unabhängigen Anspruchs gelöst. Vorteilhafte Ausführungsformen sind Gegenstand der abhängigen Ansprüche.According to the invention, this object is achieved by the subject matter of the independent claim. Advantageous embodiments are the subject of the dependent claims.
Die Erfindung beruht auf dem allgemeinen Gedanken, die Haltekontur des Druckkörpers und die Kontur der zugehörigen Aufnahme als komplementäre Kugelabschnitte auszubilden und die Gegendruckkörper bezüglich ihrer Längsmittelachse starr am Ansatz zu fixieren, so dass der Gegendruckkörper dadurch als Widerlager für den sich daran abstützenden Druckkörper dienen kann. Durch diese Bauweise wird zum einen erreicht, dass der Druckkörper flächig am zugehörigen Ansatz abgestützt ist. Zum anderen wird durch diese Maßnahme eine Kugelkopflagerung des Druckkörpers am zugehörigen Ansatz ausgebildet, die es dem Druckkörper ermöglicht, seine Stützfläche um den Kugelmittelpunkt zu drehen. Im Falle von grösseren Einstelldrehbewegungen der Ansätze bzw. der Laufschaufeln, zum Beispiel während des Hochfahrens auf Nenndrehzahl, können die drehbar gelagerten Druckkörper diese Relativbewegungen ausgleichen, so dass stets eine flächige Kraftübertragung zwischen den aneinander abgestützten bzw. miteinander verbundenen Ansälzen erzielbar ist. Sich ändernde Winkellagen der Laufschaufeln bzw. der Ansätze bewirken bei der erfindungsgemäßen Aufschaufelbindung eine selbsttätige Einstellung der beweglich gelagerten Druckkörper. Spannungsspitzen werden dadurch vermieden. Im Betrieb bei Nenndrehzahl kommt dagegen die Reibdämpfung durch die flächige Anlage voll zur Geltung. Es entstehen keine hochfrequenten Kippbewegungen.The invention is based on the general idea of forming the retaining contour of the pressure hull and the contour of the associated receptacle as complementary ball sections and rigidly fixing the counterpressure elements with respect to their longitudinal center axis, so that the counterpressure body can serve as an abutment for the pressure hull supporting thereon. By this construction is achieved on the one hand, that the pressure body is supported flat on the associated approach. On the other hand, by this measure, a ball head bearing of the pressure hull is formed on the associated approach, which allows the pressure hull to rotate its support surface around the ball center. In the case of larger Einstelldrehbewegungen the lugs or the blades, for example, during startup at rated speed, the rotatably mounted pressure body can compensate for these relative movements, so that a flat power transmission between the mutually supported or interconnected Ansälzen is always achievable. Changing angular positions of the moving blades or of the lugs effect an automatic adjustment of the movably mounted pressure bodies in the case of the bucket binding according to the invention. Voltage peaks are thereby avoided. In operation at nominal speed, on the other hand, the friction damping is fully accentuated by the flat system. There are no high-frequency tilting movements.
Bei einer bevorzugten Ausführungsform weist der Kugelabschnitt der Haltekontur einen Kugelmittelpunkt auf, während die Stützfläche kreisförmig ist und einen Kreismittelpunkt besitzt. Der Druckkörper ist dann so gestaltet, dass eine Gerade, die sich sowohl durch den Kreismittelpunkt als auch durch den Kugelmittelpunkt erstreckt, senkrecht auf der Stützflächenebene steht. Mit anderen Worten, der Druckkörper ist bezüglich dieser Geraden rotationssymmetrisch aufgebaut. Durch diese Ausgestaltung können quasi beliebig räumlich orientierte Drehungen und Verwindungen der Ansätze bzw. der Laufschaufeln ausgeglichen werden.In a preferred embodiment, the ball portion of the retaining contour on a ball center, while the support surface is circular and has a circle center. The pressure body is then designed so that a straight line which extends through both the center of the circle and through the center of the sphere, is perpendicular to the support surface plane. In other words, the pressure body is rotationally symmetrical with respect to these straight lines. As a result of this configuration, virtually any spatially oriented rotations and twists of the projections or of the rotor blades can be compensated.
Die Gegenstützfläche, die dem benachbarten Ansatz zugeordnet ist und an weicher sich die Stützfläche des Druckkörpers flächig abstützt, kann beispielsweise durch die Stützfläche eines Gegendruckkörpers gebildet sein t, der am benachbarten Ansatz gehaltert ist. Bevorzugt wird jedoch eine Ausführungsform, bei welcher der Gegendruckkörper bezüglich der Normalenrichtung seiner Gegenstützfläche keine Taumelbewegungen durchführen kann. Auf diese Weise werden sämtliche Ausgleichsbewegungen ausschließlich von dem kugelgelagerte Druckkörper durchgeführt. Hierdurch wird erreicht, dass sich der bewegliche Druckkörper bei entsprechenden Verdrehungen der Ansätze immer wieder von selbst in seine Ausgangslage zurück verstellt. Bei einer Ausführungsform wird dieser Zweck erreicht, indem sowohl die Haltekontur des Gegendruckkörpers als auch die zugehörige Aufnahme als Konus bzw. als Kegelstumpf ausgebildet sind, wobei beide Kegelstümpfe dieselbe Konizität besitzen. Auf diese Weise kommt es zum einen zur einer flächigen Anlage des Gegendruckkörpers am zugehörigen Ansatz. Zum anderen ist der Gegendruckkörper bezüglich seiner Längsmittelachse starr am Ansatz fixiert und kann dadurch als Widerlager für den sich daran abstützenden Druckkörper dienen.The counter support surface, which is assigned to the adjacent approach and on which the supporting surface of the pressure hull is supported in a planar manner, can be formed, for example, by the support surface of a counterpressure body t, which is held on the adjacent projection. However, preference is given to an embodiment in which the counter-pressure body can not carry out tumbling movements with respect to the normal direction of its counter-support surface. In this way, all compensatory movements are performed exclusively by the ball-bearing pressure body. This ensures that the movable pressure body with appropriate twists of the approaches again and again adjusted by itself to its original position. In one embodiment, this purpose is achieved by both the retaining contour of the counter-pressure body and the associated receptacle are formed as a cone or a truncated cone, both truncated cones have the same conicity. In this way, on the one hand, there is a surface contact of the counter-pressure element at the associated approach. On the other hand, the counter-pressure body is fixed rigidly with respect to its longitudinal central axis at the base and can thereby serve as an abutment for the pressure body supported thereon.
Weitere wichtige Merkmale und Vorteile der erfindungsgemäßen Laufschaufelbindung ergeben sich aus den Unteransprüchen, aus den Zeichnungen und aus der zugehörigen Figurenbeschreibung anhand der Zeichnungen.Further important features and advantages of the blade connection according to the invention will become apparent from the dependent claims, from the drawings and from the associated description of the figures with reference to the drawings.
Bevorzugte Ausführungsbeispiele der Erfindung sind in den Zeichnungen dargestellt und werden in der nachfolgenden Beschreibung näher erläutert, wobei sich gleiche Bezugszeichen auf gleiche oder ähnliche oder funktional gleiche Bauteile beziehen. Es zeigen jeweils schematisch,
- Fig. 1a, 1b
- je eine Draufsicht auf einen Schaufelkranzausschnitt im Außerbetriebszustand (1a) und im Betriebszustand (1b),
- Fig. 2
- einen Schnitt gemäß einer Schnittlinie II - II in
Fig. 1b durch zwei miteinander verbundene Ansätze,
- Fig. 1a, 1b
- each a plan view of a blade ring cut-out in the inoperative state (1a) and in the operating state (1b),
- Fig. 2
- a section along a section line II - II in
Fig. 1b through two interconnected approaches,
Entsprechend den
Im Außerbetriebszustand gemäß
Abweichend von den
In den Schnittansichten der
Entsprechend der
Des weiteren besitzt der Druckkörper 7 an seiner Stützseite 9 eine ebene Stützfläche 13. Wie aus der
Wie aus der
Die erfindungsgemäße Laufschaufelbindung kann somit die im Betrieb, vor allem beim An- und Abfahren, möglicherweise anfallenden Drehbewegungen und unterschiedlichen Winkelstellungen der Ansätze 2 ausgleichen, ohne dass es dabei zu größeren elastischen oder sogar zu plastischen Verformungen kommt.The blade binding according to the invention can thus compensate for the rotational movements and different angular positions of the
Die Geometrie des Stützkörpers 7 ist zweckmäßig so gewählt, dass die Stützfläche 13 kreisförmig ausgestaltet ist und einen Kreismittelpunkt 15 besitzt. Die kugelförmige Haltekontur 10 ist dabei so auf die ebene Stützfläche 13 abgestimmt, dass eine Gerade 16, die sowohl durch den Kreismittelpunkt 15 als auch durch den Kugelmittelpunkt 12 verläuft, senkrecht auf der Ebene der Stützfläche 13 steht. Hierdurch ergibt sich eine Rotationssymmetrie für den Druckkörper 7, so dass die hierdurch erzielte Lagerung in allen Raumrichtungen gleichsam wirkt.The geometry of the
Alternativ dazu kann gemäß der in Fig. 3 gezeigten Ausführungsform die Gegenstützfläche 14 auch an einem speziellen Widerlagerelement 17 ausgebildet sein. Dieses Widerlagerelement 17 ist an der Stirnseite 4 des benachbarten Ansatzes 2 befestigt, insbesondere durch Löten oder Schweißen. Bei der hier gezeigten Ausführungsform ist das Widerlagerelement 17 als Platte ausgestaltet, die in die Stirnseite 4 des benachbarten Ansatzes 2 eingesetzt und darin versenkt angeordnet ist.Alternatively, according to the embodiment shown in FIG. 3, the
Bei der Ausführungsform gemäss
Um die ebenen Stützflächen 13 der Druckkörper 7 und die damit zusammenwirkenden Gegenstützflächen 14 vor Verschleiß zu schützen, können die Stützflächen 13 und/oder die Gegenstützflächen 14 mit einer reibungsarmen Beschichtung versehen sein (nicht dargestellt). Gleichzeitig können durch diese Maßnahme die in der Ebene der Stützflächen 13 bzw. der Gegenstützflächen 14 auftretenden Reibungskräfte reduziert werden.In order to protect the flat support surfaces 13 of the
Zusätzlich oder alternativ kann zur Verschleißreduzierung vorgesehen sein, die Druckkörper 7 bzw. die Gegendruckkörper 18 zumindest in einem die Stützfläche 13 bzw. die Gegenstützfläche 14 aufweisenden Abschnitt aus einem geeigneten Hartmetall auszubilden.Additionally or alternatively, to reduce wear, it is possible for the
- 11
- Laufschaufelblade
- 22
- Ansatz/StützflügelApproach / support wings
- 33
- Umfangsrichtungcircumferentially
- 44
- Stirnseite von 2Front side of 2
- 55
- Spaltgap
- 66
- Momentmoment
- 77
- Druckkörperpressure vessels
- 88th
- Halteseite von 7Holding side of 7
- 99
- Stützseite von 7Support side of 7
- 1010
- Haltekontur von 8Holding contour of 8
- 1111
- Aufnahmeadmission
- 1212
- KugelmittelpunktBall center
- 1313
- Stützfläche von 9Support surface of 9
- 1414
- GegenstützflächeAgainst support surface
- 1515
- KreismittelpunktCircle center
- 1616
- GeradeJust
- 1818
- GegendruckkörperPilot head
- 1919
- Stützseite von 18Support side of 18
- 2020
- Halteseite von 18Holding side of 18
- 2121
- Haltekontur von 20Holding contour of 20
- 2222
- Aufnahmeadmission
- RR
- Radiusradius
- FF
- Kraftforce
- MM
- Kopplungsmomentcouple moment
Claims (2)
- Connecting arrangement for rotor blades (1) of a turbomachine, with projections (2), which extend in the circumferential direction (3), are rigidly connected in pairs to a rotor blade (1) and, at least during operation of the turbomachine, are respectively supported by at least one pressure body (7) on the projection (2) which is adjacent in the circumferential direction (3),- each pressure body (7) having a securing contour (10) on a securing face (8) which faces toward the associated projection (2), which securing contour (10) protrudes into an acceptance feature (11) configured on the associated projection (2) and is supported in the circumferential direction (3) and transverse to it, in the acceptance feature (11),- each pressure body (7) having a plane support surface (13) on a support face (9) which faces toward the adjacent projection (2), which support surface (13) has, at least during operation of the turbomachine, area support on a plane mating surface (14) which is associated with the adjacent projection (2),- at least one pressure body (7), whose securing contour (10) is configured as a spherical segment, being associated with each pair of mutually supporting projections (2),- the associated acceptance feature (11) being likewise configured as a spherical segment whose radius (R) is at least approximately of the same magnitude as the radius (R) of the spherical segment of the securing contour (10),- in that the mating support surface (14) is formed by the support surface of a mating pressure body (18) which, with its securing contour (21), protrudes into an acceptance feature (22) configured in the adjacent projection (2),- the securing contour (21) of the mating pressure body (18) being configured as a cone, and the associated acceptance feature (22) being likewise configured as a cone whose conicity is of equal magnitude to the conicity of the cone of the securing contour (21).
- Rotor blade connecting arrangement according to Claim 1, characterized in that the support surface (13) and/or the mating support surface (14) is/are embodied with low friction and to be wear-resistant.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10342207 | 2003-09-12 | ||
DE10342207A DE10342207A1 (en) | 2003-09-12 | 2003-09-12 | Blade binding of a turbomachine |
Publications (3)
Publication Number | Publication Date |
---|---|
EP1515001A2 EP1515001A2 (en) | 2005-03-16 |
EP1515001A3 EP1515001A3 (en) | 2012-07-04 |
EP1515001B1 true EP1515001B1 (en) | 2016-11-09 |
Family
ID=34129785
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP04104236.7A Not-in-force EP1515001B1 (en) | 2003-09-12 | 2004-09-02 | Blade to blade connection in a turbomachine |
Country Status (6)
Country | Link |
---|---|
US (1) | US7140841B2 (en) |
EP (1) | EP1515001B1 (en) |
JP (1) | JP2005090506A (en) |
CN (1) | CN100374688C (en) |
DE (1) | DE10342207A1 (en) |
ZA (1) | ZA200407296B (en) |
Families Citing this family (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2436597A (en) * | 2006-03-27 | 2007-10-03 | Alstom Technology Ltd | Turbine blade and diaphragm |
US20090202344A1 (en) * | 2008-02-13 | 2009-08-13 | General Electric Company | Rotating assembly for a turbomachine |
EP2116693A1 (en) * | 2008-05-07 | 2009-11-11 | Siemens Aktiengesellschaft | Rotor for a turbomachine |
EP2213837A1 (en) * | 2009-01-29 | 2010-08-04 | Siemens Aktiengesellschaft | Turbine blade system |
JP5491325B2 (en) * | 2010-08-26 | 2014-05-14 | 三菱重工業株式会社 | Rotor blade and rotating machine |
EP3653838A1 (en) * | 2012-09-25 | 2020-05-20 | United Technologies Corporation | Airfoil array with airfoils that differ in geometry and include mistake-proof features |
US10465531B2 (en) | 2013-02-21 | 2019-11-05 | General Electric Company | Turbine blade tip shroud and mid-span snubber with compound contact angle |
US9464530B2 (en) | 2014-02-20 | 2016-10-11 | General Electric Company | Turbine bucket and method for balancing a tip shroud of a turbine bucket |
JP5836410B2 (en) * | 2014-02-27 | 2015-12-24 | 三菱重工業株式会社 | Rotor blade and rotating machine |
EP3085890B1 (en) * | 2015-04-22 | 2017-12-27 | Ansaldo Energia Switzerland AG | Blade with tip shroud |
FR3137121B1 (en) * | 2022-06-22 | 2024-06-21 | Safran Aircraft Engines | Bladed assembly with inter-platform connection by interposed rolling element |
Family Cites Families (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2283901A (en) * | 1940-03-16 | 1942-05-26 | Westinghouse Electric & Mfg Co | Turbine blading |
US2942843A (en) * | 1956-06-15 | 1960-06-28 | Westinghouse Electric Corp | Blade vibration damping structure |
JPS5632441B2 (en) * | 1973-11-30 | 1981-07-28 | ||
JPS54125307A (en) * | 1978-03-24 | 1979-09-28 | Toshiba Corp | Connecting device for turbine movable blades |
JPS572405A (en) * | 1980-06-05 | 1982-01-07 | Hitachi Ltd | Rotary blade connector of axial-flow rotary machine |
US4407634A (en) * | 1981-09-08 | 1983-10-04 | Northern Engineering Industries Plc | Axial-flow steam turbine wheel |
DE3211073A1 (en) * | 1982-03-25 | 1983-10-06 | Kraftwerk Union Ag | DEVICE FOR VIBRATION DAMPING ON A LEAD Vane |
JPS6149103A (en) * | 1984-08-16 | 1986-03-11 | Toshiba Corp | Turbine rotor blade linking equipment |
DE3517283A1 (en) * | 1985-05-14 | 1986-11-20 | MAN Gutehoffnungshütte GmbH, 4200 Oberhausen | BINDING BLADES OF A THERMAL TURBO MACHINE |
JPS63132801U (en) * | 1987-02-20 | 1988-08-30 | ||
JPH0622083Y2 (en) * | 1988-04-12 | 1994-06-08 | 三菱重工業株式会社 | Stub damper |
WO2003014529A1 (en) * | 2001-08-03 | 2003-02-20 | Hitachi, Ltd. | Turbine moving vane |
-
2003
- 2003-09-12 DE DE10342207A patent/DE10342207A1/en not_active Ceased
-
2004
- 2004-09-02 EP EP04104236.7A patent/EP1515001B1/en not_active Not-in-force
- 2004-09-08 JP JP2004261398A patent/JP2005090506A/en not_active Withdrawn
- 2004-09-09 US US10/936,575 patent/US7140841B2/en not_active Expired - Fee Related
- 2004-09-10 ZA ZA2004/07296A patent/ZA200407296B/en unknown
- 2004-09-13 CN CNB2004100752300A patent/CN100374688C/en not_active Expired - Fee Related
Non-Patent Citations (1)
Title |
---|
None * |
Also Published As
Publication number | Publication date |
---|---|
CN1594841A (en) | 2005-03-16 |
EP1515001A3 (en) | 2012-07-04 |
JP2005090506A (en) | 2005-04-07 |
US7140841B2 (en) | 2006-11-28 |
US20050111983A1 (en) | 2005-05-26 |
EP1515001A2 (en) | 2005-03-16 |
CN100374688C (en) | 2008-03-12 |
DE10342207A1 (en) | 2005-04-07 |
ZA200407296B (en) | 2005-08-31 |
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