EP0520259A1 - Keying of rotor blades - Google Patents
Keying of rotor blades Download PDFInfo
- Publication number
- EP0520259A1 EP0520259A1 EP92109959A EP92109959A EP0520259A1 EP 0520259 A1 EP0520259 A1 EP 0520259A1 EP 92109959 A EP92109959 A EP 92109959A EP 92109959 A EP92109959 A EP 92109959A EP 0520259 A1 EP0520259 A1 EP 0520259A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- blade
- rotor
- blades
- vertical
- groove
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 238000007373 indentation Methods 0.000 abstract 2
- 238000006073 displacement reaction Methods 0.000 description 4
- 238000005452 bending Methods 0.000 description 3
- 238000010586 diagram Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 239000012530 fluid Substances 0.000 description 3
- 230000007704 transition Effects 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
Images
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
- F01D5/30—Fixing blades to rotors; Blade roots ; Blade spacers
- F01D5/3023—Fixing blades to rotors; Blade roots ; Blade spacers of radial insertion type, e.g. in individual recesses
- F01D5/303—Fixing blades to rotors; Blade roots ; Blade spacers of radial insertion type, e.g. in individual recesses in a circumferential slot
- F01D5/3038—Fixing blades to rotors; Blade roots ; Blade spacers of radial insertion type, e.g. in individual recesses in a circumferential slot the slot having inwardly directed abutment faces on both sides
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S416/00—Fluid reaction surfaces, i.e. impellers
- Y10S416/50—Vibration damping features
Definitions
- the invention relates to a blade attachment in the drum rotor of an axially flow-through turbomachine, in which the blades are fastened in rows with their feet in circumferential blade grooves with lateral support teeth.
- Such blade attachments are usually found in compressor and turbine rotors. With each rotor revolution, the rotating blade grooves change their axial dimension due to the rotor deflection and the amplitude of the bending vibrations. The dimensional change takes place with an amplitude, which depends on the respective construction. If the amplitude exceeds a certain level, damage to the blade roots or rotor rotations can result from frictional fatigue.
- the corresponding parts of the first turbomachine stage in multi-stage machines are particularly at risk since the mutual relief provided by adjacent blade grooves is not given here. As a result, significantly greater relative displacement amplitudes occur in this first vane groove than in the subsequent vane grooves. This fact is explained in FIGS. 2 and 3 to be described later.
- the invention tries to avoid all these disadvantages. It is based on the task of taking a measure in rotors of the type mentioned at the beginning in which the axial displacement and the asymmetrical deformation of at least the first bladed groove are reduced and in which the forces are clearly supported.
- the blade groove provided at least for the first row of blades is an L-groove with two vertical wings and a horizontal spike, and in that the blade root consists essentially of a vertical and only one lateral horizontal web.
- the high-pressure rotor 20 is provided with thirteen rows of runners.
- the individual blades consisting of blade 21 with cover plate 22 and blade root 23, are inserted in circumferential blade grooves, which are numbered from 1 to 13 on the steam inlet side and on the steam outlet side.
- Dash-dotted is the flow-limiting contour 23 of the cylinder, not shown, which also carries the 13 rows of guide vanes.
- the blade feet 23 have a hammer head shape on. The centrifugal forces and bending moments acting on the blade during operation are guided into the rotor by means of shoulders via appropriately configured support teeth of the blade groove.
- the deformation of the blade groove is shown in FIG. 2 using a rotor cutout.
- the masses Ao and Au are taken at the transition between the vertical and horizontal side wall of the recess. This transition lies opposite the most stressed point of the hammer head, which is why the vertical and horizontal bars of the blade root are usually rounded.
- the blade groove 1 is according to Figure 4 with two vertical wings 31 and. 32 and a horizontal tine 33 formed.
- the airfoil 31 is flush with the rotor surface; the wing 32 is in the region of the groove base with the formation of a backward rotation.
- the blade root 34 consists of a vertical and a lateral horizontal web. With its vertical boundaries, it bears against the wings 31 and 32 during operation; with the horizontal bar of the lateral web, it rests on the carrying prong 33.
- the forces acting on the blade attachments shown in FIGS. 4 and 5 are composed of the radially acting centrifugal force F F and the steam force F D acting on the airfoil, which characterizes the bending moment M D.
- the latter is also influenced by that the focus of the load-bearing cross-sections is not in the line of attack of the centrifugal forces.
- the steam forces are introduced into the rotor via the axial surfaces 31 and 32 and in the circumferential direction via the mutual support of the adjacent blade roots.
- the forces exerted by the neighboring blade roots on the blade root under consideration are denoted by F S.
- Their axial components are also introduced into the rotor via the axial surfaces 31 and 32.
- the invention is not limited to the example shown and described.
- the blade grooves and feet of all blade rows can of course be equipped with the new measure.
- the new fastening is basically suitable for all high-pressure high-pressure blading in which the fluid forces outweigh the centrifugal forces, regardless of whether the blades now have free-standing or bound blade tips.
- the measure is advantageously used in the case of predordined blades, since here too it helps to clarify the introduction of the moments caused by the torsion into the rotor.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Turbine Rotor Nozzle Sealing (AREA)
Abstract
Description
Die Erfindung betrifft eine Laufschaufelbefestigung im Trommelrotor einer axial durchströmten Turbomaschine, in welchem die Schaufeln mit ihren Füssen reihenweise in umlaufenden Schaufelnuten mit seitlichen Tragzacken befestigt sind.The invention relates to a blade attachment in the drum rotor of an axially flow-through turbomachine, in which the blades are fastened in rows with their feet in circumferential blade grooves with lateral support teeth.
Derartige Schaufelbefestigungen finden sich in der Regel bei Verdichter- und Turbinenrotoren. Bei jeder Rotorumdrehung verändern die umlaufenden Schaufelnuten ihre axiale Dimension infolge der Rotordurchbiegung und der Ampitude der Biegeschwingungen. Die Dimensionsänderung erfolgt mit einer Amplitude, welche von der jeweiligen Konstruktion abhängt. Überschreitet die Amplitude ein gewisses Mass, so können an den Schaufelfüssen oder an den Rotoreindrehungen Schäden durch Reibermüdung entstehen. Besonders gefährdet sind die entsprechenden Partien der ersten Turbomaschinenstufe bei mehrstufigen Maschinen, da hier die gegenseitige Entlastung durch benachbarte Schaufelnuten nicht gegeben ist. Demzufolge treten in dieser ersten Schaufelnut deutlich grössere relative Verschiebeamplituden auf als in den darauffolgenden Schaufelnuten. Dieser Sachverhalt ist in später zu beschreibenden Fig. 2 und 3 erläutert.Such blade attachments are usually found in compressor and turbine rotors. With each rotor revolution, the rotating blade grooves change their axial dimension due to the rotor deflection and the amplitude of the bending vibrations. The dimensional change takes place with an amplitude, which depends on the respective construction. If the amplitude exceeds a certain level, damage to the blade roots or rotor rotations can result from frictional fatigue. The corresponding parts of the first turbomachine stage in multi-stage machines are particularly at risk since the mutual relief provided by adjacent blade grooves is not given here. As a result, significantly greater relative displacement amplitudes occur in this first vane groove than in the subsequent vane grooves. This fact is explained in FIGS. 2 and 3 to be described later.
Daneben treten bei Temperaturänderungen, beim Anfahren, bei Laständerungen oder bei betrieblichen Schwankungen in der ersten Schaufelnut starke asymmetrische Verschiebungen auf, die zu lokal überhöhten Flächenpressungen in den Tragzacken der Schaufelfüsse der ersten Laufreihe führen.In addition, strong asymmetrical displacements occur when there are changes in temperature, when starting up, when there is a change in load or when there are operational fluctuations in the first vane groove, which lead to locally excessive surface pressures in the tines of the vane feet in the first row.
Scliesslich treten bei mechanischen Hammerkopf-Schaufelfussbefestigungen, welche durch Fliehkräfte in radialer Richtung und durch Fluidkräfte in Axial- und in Umfangsrichtung belastet werden, und bei denen die Kräfte über zwei oder mehrere Zacken auf den Rotor übertragen werden, infolge Herstellungstoleranzen Probleme mit dem gleichzeitigen Anliegen und Tragen aller beteiligten Flächen auf.Finally, mechanical hammer head blade root attachments, which are loaded by centrifugal forces in the radial direction and by fluid forces in the axial and circumferential directions, and in which the forces are transmitted to the rotor via two or more teeth, have problems with the simultaneous contact and due to manufacturing tolerances Apply all areas involved.
Die Erfindung versucht all diese Nachteile zu vermeiden. Es ihr die Aufgabe zugrunde, bei Rotoren der eingangs genannten Art eine Massnahme zu treffen, bei der die Axialverschiebung und die asymmetrische Deformation zumindest der ersten beschaufelten Nut herabgemindert wird und bei denen eine eindeutige Abstützung der Kräfte stattfindet.The invention tries to avoid all these disadvantages. It is based on the task of taking a measure in rotors of the type mentioned at the beginning in which the axial displacement and the asymmetrical deformation of at least the first bladed groove are reduced and in which the forces are clearly supported.
Erfindungsgemäss wird dies dadurch erreicht, dass die zumindest für die erste Schaufelreihe vorgesehene Schaufelnut eine L-Nut mit zwei senkrechten Tragflächen und einem waagerechten Tragzacken ist und dass der Schaufelfuss im wesentlichen aus einem senkrechten und nur einem seitlichen waagerechten Steg besteht.According to the invention, this is achieved in that the blade groove provided at least for the first row of blades is an L-groove with two vertical wings and a horizontal spike, and in that the blade root consists essentially of a vertical and only one lateral horizontal web.
Der Vorteil der Erfindung ist neben der vorherrschenden Klarheit über die Kräfteverhältnisse noch darin zu sehen, dass nur die tragenden Flächen der Nuteindrehung und des Schaufelfusses, d.h. insgesamt weniger Flächen als bisher mit der üblichen Genauigkeit zu fertigen sind.The advantage of the invention, in addition to the prevailing clarity about the force relationships, can also be seen in the fact that only the load-bearing surfaces of the slot turning and of the blade root, ie a total of fewer surfaces than previously, can be produced with the usual accuracy.
In der Zeichnung ist ein Ausführungsbeispiel der Erfindung anhand des Hochdruckrotors einer axialdurchströmten Dampfturbine schematisch dargestellt.
Es zeigen:
- Fig.1
- eine teilweise geschnittene Teilansicht eines beschaufelten Trommelrotors;
- Fig.2
- die eingangs erwähnte, zur Verdeutlichung stark übertriebene Dimensionsänderung einer umlaufenden Nut anlässlich der Rotordurchbiegung;
- Fig.3
- Ein Schaubild, welches das Mass der resultierenden Durchbiegungs-Amplitude in der jeweiligen Schaufelnut zeigt;
- Fig.4
- einen Teillängschnitt durch eine erfimdungsgemässe Schaufelnut;
- Fig.5
- eine Prinzipskizze anhand einer teilweisen Abwicklung eines Zylinderschnittes gemäss Limie V-V in Fig 4.
Show it:
- Fig. 1
- a partial sectional view of a bladed drum rotor;
- Fig. 2
- the above-mentioned, greatly exaggerated dimensional change of a circumferential groove on the occasion of the rotor deflection;
- Fig. 3
- A diagram which shows the measure of the resulting deflection amplitude in the respective blade groove;
- Fig. 4
- a partial longitudinal section through an inventive blade groove;
- Fig. 5
- a schematic diagram based on a partial development of a cylinder cut according to Limie VV in Fig. 4.
Es sind nur die für das Verständnis der Erfindung wesentlichen Elemente gezeigt. Nicht dargestellt sind von der Anlage beispielsweise sämtliche nichtrotierenden Teile sowie die Wellenenden mitsamt der Lagerung. Die Strömungsrichtung des Arbeitsmittels ist mit einem Pfeil bezeichnet.Only the elements essential for understanding the invention are shown. The system does not show, for example, all non-rotating parts and the shaft ends together with the bearing. The direction of flow of the working fluid is indicated by an arrow.
Gemäss Fig.1 ist der Hochdruckrotor 20 mit dreizehn Laufreihen versehen. Die einzelnen Schaufeln, bestehend aus Schaufelblatt 21 mit Deckplatte 22 und Schaufelfuss 23, sind in umlaufenden Schaufelnuten eingesetzt, welche dampfeintrittseitig bis dampfaustrittseitig von 1 bis 13 durchnumeriert sind. Strichpunktiert ist die strömungsbegrenzende Kontur 23 des nichtdargestellten Zylinders, welcher die ebenfalls 13 Reihen Leitschaufeln trägt. Die Schaufelfüsse 23 weisen Hammerkopfform auf. Die während des Betriebes auf die Schaufel wirkenden Fliehkräfte und Biegemomente werden mittels Schultern über entsprechend konfigurierte Tragzacken der Schaufelnut in den Rotor geleitet.1, the high-
In Fig.2 ist anhand eines Rotorauschnitts die Deformation der Schaufelnut gezeigt. Die Masse Ao und Au sind am Übergang zwischen senkrechter und waagerechter Seitenwand der Eindrehung genommen. Dieser Übergang liegt der spannungsmässig am meisten belasteten Stelle des Hammerkopfes gegenüber, weshalb in der Regel der senkrechte und der waagerechte Balken des Schaufelfusses mit einer Ausrundung versehen sind.The deformation of the blade groove is shown in FIG. 2 using a rotor cutout. The masses Ao and Au are taken at the transition between the vertical and horizontal side wall of the recess. This transition lies opposite the most stressed point of the hammer head, which is why the vertical and horizontal bars of the blade root are usually rounded.
In Fig.3 ist die Amplitude A als arithmetischer Mittelwert der beiden Distanzen Ao und Au für jede der 13 Schaufelnuten angegeben. Ohne Gegenmassnahme liegt der Wert A1 der Axialverschiebung der ersten Schaufelnut beträchtlich höher als jene der benachbarten Schaufelnuten.3 shows the amplitude A as the arithmetic mean of the two distances Ao and Au for each of the 13 blade grooves. Without countermeasures, the value A1 of the axial displacement of the first blade groove is considerably higher than that of the adjacent blade grooves.
Hier setzt nun die Erfindung ein, welche darin besteht, dass sowohl die Nuteindrehung als auch der Schaufelfuss im wesentlichen in L-Form ausgebildet werden. Die Schaufelnut 1 ist gemäss Fig.4 mit zwei senkrechten Tragflächen 31 resp. 32 sowie einem waagerechten Tragzacken 33 ausgebildet. Die Tragfläche 31 ist bündig mit der Rotoroberfläche; die Tragfläche 32 befindet sich unter Bildung einer Hinterdrehung im Bereich des Nutengrundes. Der Schaufelfuss 34 besteht aus einem senkrechten und einem seitlichen waagerechten Steg. Mit seinen senkrechten Begrenzungen liegt er während des Betriebes an den Tragflächen 31 und 32 an; mit dem waagerechten Balken des seitlichen Steges liegt er am Tragzacken 33 an.This is where the invention comes in, which consists in the fact that both the slot turning and the blade root are essentially L-shaped. The blade groove 1 is according to Figure 4 with two
Die aus den Fig.4 und 5 ersichtlichen, auf die Schaufelbefestigungen einwirkenden Kräfte setzten sich im einfachsten Falle zusammen aus der radial wirkenden Fliehkraft FF, und der am Schaufelblatt angreifenden Dampfkraft FD, welche das Biegemoment MD prägt. Letzteres wird auch dadurch beeinflusst, dass die Schwerpunkte der tragenden Querschnitte nicht in der Angriffslinie der Fliehkräfte liegen. Die Dampfkräfte werden über die Axialflächen 31 und 32 in den Rotor eingeleitet sowie in Umfangsrichtung über die gegenseitige Abstützung der benachbarten Schaufelfüsse. Die von den benachbarten Schaufelfüssen auf den betrachteten Schaufelfuss ausgeübten Kräfte sind mit FS bezeichnet. Ihre axialen Komponenten werden ebenfalls über die Axialflächen 31 und 32 in den Rotor eingeleitet.In the simplest case, the forces acting on the blade attachments shown in FIGS. 4 and 5 are composed of the radially acting centrifugal force F F and the steam force F D acting on the airfoil, which characterizes the bending moment M D. The latter is also influenced by that the focus of the load-bearing cross-sections is not in the line of attack of the centrifugal forces. The steam forces are introduced into the rotor via the
Die von den Nutwandungen ausgeübten entsprechenden Reaktionskräfte sind mit R₃₁, R₃₂ und R₃₃ bezeichnet.The corresponding reaction forces exerted by the groove walls are denoted by R₃₁, R₃₂ and R₃₃.
Die Wirkung der neuen Massnahme ist im Schaubild der Fig.3 ersichtlich. Die relativ grossen Flankenbewegungen mit der Amplitude A1 sind nunmehr reduziert auf ca. das halbe Mass A1'. Eine weitere günstige Nebenwirkung ist darin zu sehen, dass über die Axialflächen 31 und 32 anlässlich des Betriebes auftretende Schwingungsbeanspruchungen direkt und eindeutig in den Rotor eingeleitet werden und zwar mit stark verringerter Kerbwirkung gegenüber klassischen Hammerkopfformen, bei denen die durch Schwingungen verursachte Kräfte erst vom senkrechten in die seitlichen Stege umgeleitet werden müssen.The effect of the new measure can be seen in the diagram in Fig. 3. The relatively large flank movements with the amplitude A1 are now reduced to approximately half the dimension A1 '. Another favorable side effect can be seen in the fact that vibrational stresses occurring during operation during the operation are directly and unambiguously introduced into the rotor, with a significantly reduced notch effect compared to classic hammer head shapes, in which the forces caused by vibrations only move from the vertical to the the side bars must be diverted.
Selbstverständlich ist die Erfindung nicht auf das dargestellte und beschriebene Beispiel beschränkt. In Abweichung zur gezeigten Anordnung können selbstverständlich die Schaufelnuten und Füsse sämtlicher Schaufelreihen mit der neuen Massnahme ausgerüstet werden. Als Richtlinie kann angegeben werden, dass sich die neue Befestigung grundsätzlich eignet für alle hochbelasteten Hochdruckbeschaufelungen, bei denen die Fluidkräfte die Fliehkräfte überwiegen und zwar unabhängig davon, ob die Schaufeln nun freistehende oder gebundene Schaufelspitzen aufweisen. Desweiteren wird die Massnahme mit Vorteil bei vortordierten Schaufeln eingesetzt, da sie auch hier zur Klärung der Einleitung der infolge der Torsion verursachten Momente in den Rotor beiträgt.Of course, the invention is not limited to the example shown and described. In deviation from the arrangement shown, the blade grooves and feet of all blade rows can of course be equipped with the new measure. As a guideline, it can be stated that the new fastening is basically suitable for all high-pressure high-pressure blading in which the fluid forces outweigh the centrifugal forces, regardless of whether the blades now have free-standing or bound blade tips. Furthermore, the measure is advantageously used in the case of predordined blades, since here too it helps to clarify the introduction of the moments caused by the torsion into the rotor.
Claims (1)
dadurch gekennzeichnet,
dass die zumindest für die erste Schaufelreihe vorgesehene Schaufelnut (1) eine L-Nut mit zwei senkrechten Tragflächen (31, 32) und einem waagerechten Tragzacken (33) ist und dass der Schaufelfuss (34) im wesentlichen aus einem senkrechten und nur einem seitlichen waagerechten Steg besteht.Blade attachment in the drum rotor of an axially flow-through turbomachine, in which the blades are fastened in rows with their feet (23, 34) in circumferential blade grooves (1-13) with lateral support teeth,
characterized,
that the blade groove (1) provided at least for the first row of blades is an L-groove with two vertical wings (31, 32) and a horizontal support prong (33) and that the blade root (34) consists essentially of a vertical and only one lateral horizontal Web exists.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CH1925/91 | 1991-06-28 | ||
| CH192591 | 1991-06-28 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP0520259A1 true EP0520259A1 (en) | 1992-12-30 |
| EP0520259B1 EP0520259B1 (en) | 1994-09-21 |
Family
ID=4221804
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP92109959A Expired - Lifetime EP0520259B1 (en) | 1991-06-28 | 1992-06-13 | Keying of rotor blades |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US5236308A (en) |
| EP (1) | EP0520259B1 (en) |
| JP (1) | JPH05187203A (en) |
| DE (1) | DE59200524D1 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0695856A1 (en) * | 1994-08-03 | 1996-02-07 | Societe Nationale D'etude Et De Construction De Moteurs D'aviation "Snecma" | Compressor disc with asymmetric circumferencial groove |
| EP0707136A1 (en) * | 1994-10-14 | 1996-04-17 | ABB Management AG | Drum rotor for an axial flow turbomachine |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0658168A (en) * | 1992-08-06 | 1994-03-01 | Hitachi Ltd | Compressor for gas turbine and gas turbine |
| EP2282010A1 (en) * | 2009-06-23 | 2011-02-09 | Siemens Aktiengesellschaft | Rotor blade for an axial flow turbomachine |
| DE102010053141B4 (en) * | 2009-12-07 | 2018-10-11 | General Electric Technology Gmbh | Turbine aggregate with possible over-rotation of the foot of a blade to the installation of a last blade |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE691800C (en) * | 1938-07-30 | 1940-06-06 | Siemens Schuckertwerke Akt Ges | Blading for steam or gas turbines in particular with radial pressure |
| US2295012A (en) * | 1941-03-08 | 1942-09-08 | Westinghouse Electric & Mfg Co | Turbine blading |
| US2327839A (en) * | 1940-03-26 | 1943-08-24 | Bbc Brown Boveri & Cie | Turbine construction |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE570754C (en) * | 1933-02-20 | Siemens Schuckertwerke Akt Ges | Blade attachment for steam or gas turbines | |
| US888500A (en) * | 1907-10-23 | 1908-05-26 | Bergmann Elek Citats Werke Ag | Turbine. |
| US1466324A (en) * | 1922-06-07 | 1923-08-28 | Gen Electric | Elastic-fluid turbine |
| US3475108A (en) * | 1968-02-14 | 1969-10-28 | Siemens Ag | Blade structure for turbines |
-
1992
- 1992-06-13 EP EP92109959A patent/EP0520259B1/en not_active Expired - Lifetime
- 1992-06-13 DE DE59200524T patent/DE59200524D1/en not_active Expired - Fee Related
- 1992-06-18 US US07/900,921 patent/US5236308A/en not_active Expired - Fee Related
- 1992-06-26 JP JP4169423A patent/JPH05187203A/en active Pending
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE691800C (en) * | 1938-07-30 | 1940-06-06 | Siemens Schuckertwerke Akt Ges | Blading for steam or gas turbines in particular with radial pressure |
| US2327839A (en) * | 1940-03-26 | 1943-08-24 | Bbc Brown Boveri & Cie | Turbine construction |
| US2295012A (en) * | 1941-03-08 | 1942-09-08 | Westinghouse Electric & Mfg Co | Turbine blading |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0695856A1 (en) * | 1994-08-03 | 1996-02-07 | Societe Nationale D'etude Et De Construction De Moteurs D'aviation "Snecma" | Compressor disc with asymmetric circumferencial groove |
| FR2723397A1 (en) * | 1994-08-03 | 1996-02-09 | Snecma | TURBOMACHINE COMPRESSOR DISK WITH ASYMMETRIC CIRCULAR GORGE |
| EP0707136A1 (en) * | 1994-10-14 | 1996-04-17 | ABB Management AG | Drum rotor for an axial flow turbomachine |
| DE4436727A1 (en) * | 1994-10-14 | 1996-04-18 | Abb Management Ag | Drum rotor for an axially flowed turbo machine |
| US5575623A (en) * | 1994-10-14 | 1996-11-19 | Abb Management Ag | Drum rotor for an axial-flow turbomachine |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH05187203A (en) | 1993-07-27 |
| US5236308A (en) | 1993-08-17 |
| DE59200524D1 (en) | 1994-10-27 |
| EP0520259B1 (en) | 1994-09-21 |
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