EP0335299A1 - Schwingungsdämpfung für Axialbeschaufelungen - Google Patents

Schwingungsdämpfung für Axialbeschaufelungen Download PDF

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Publication number
EP0335299A1
EP0335299A1 EP89105367A EP89105367A EP0335299A1 EP 0335299 A1 EP0335299 A1 EP 0335299A1 EP 89105367 A EP89105367 A EP 89105367A EP 89105367 A EP89105367 A EP 89105367A EP 0335299 A1 EP0335299 A1 EP 0335299A1
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EP
European Patent Office
Prior art keywords
hollow body
damping
blades
hollow
vibration 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.)
Withdrawn
Application number
EP89105367A
Other languages
German (de)
English (en)
French (fr)
Inventor
Renate Müller
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
SEMM-TEC GmbH
Original Assignee
SEMM-TEC GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by SEMM-TEC GmbH filed Critical SEMM-TEC GmbH
Publication of EP0335299A1 publication Critical patent/EP0335299A1/de
Withdrawn legal-status Critical Current

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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
    • 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
    • F01D5/14—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
    • F01D5/22—Blade-to-blade connections, e.g. for damping vibrations
    • F01D5/24—Blade-to-blade connections, e.g. for damping vibrations using wire or the like
    • 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 vibration damping for axial blades, in particular axially flow-through turbines and compressors, summarized below as turbomachines, with hollow and closed binding pins in the area of the free blade ends, which contain an attenuator and are aligned perpendicular to the centrifugal force, and vibration damping for blades with shroud or plate or support wing, in particular axially flowed through turbomachines with closed cavities provided perpendicular to the direction of centrifugal force in the shroud or in the support wings with a damping fluid.
  • blades Due to disturbances in the form of pressure or speed variations, axial blading is excited to vibrate. In order to withstand the additional loads resulting from the vibrations, blade materials with high strength values are required. In order to avoid damage caused by high centrifugal loads with superimposed alternating amplitudes, blades must be made relatively short and with a thick profile. For a high energy conversion, however, these should be made long and thin with respect to the profile, which cannot usually be achieved to the desired extent due to strength requirements.
  • the blade vibrations are reduced by suitable measures, the loads are also reduced and the blade profile can be designed to be more flow and energy-efficient (more economical due to higher energy conversion per stage) because of the lower demands on the vibration resistance.
  • the blades can advantageously be connected to one another by means of a shroud or, if the mechanical loads are too high, can be coupled to one another by means of a binding wire or by loosely inserted binding pins.
  • the dangerous resonance point must be known beforehand in order to achieve a positive effect, because with the one-mass transducer (as well as with a multi-mass transducer) a new vibration system is created that also has higher amplitudes in certain speed ranges can have under the same excitation conditions.
  • This point is problematic in that resonance frequency - especially in the case of coupled blading with couplings over the disc or coupling elements such as binding pin, shroud, etc. - cannot be calculated precisely enough.
  • Another proposal (GB 943023) relates to binding pins that are filled with material - here lead balls - that is liquid at operating temperature. In the case of vibratory movements, friction becomes effective, which leads to loss of vibrational energy.
  • the disadvantage of this construction is that the liquid material is freely movable in the cavity and therefore has only a slight damping effect.
  • the liquid column can also be regarded as an oscillating point mass, which in turn creates a one-mass oscillator (possibly also a multi-mass oscillator) with the disadvantages already mentioned above.
  • the invention has for its object to provide a vibration damping, the construction of which is easy to manufacture, if possible, the blade is not additionally loaded and is practically wear-free.
  • the object is achieved in that in the case of binding pins while maintaining the moment of inertia (bending strength), the hollow binding pin is provided with a large inner surface and, in the case of cover tape or plate or with supporting wings, the cavity is provided with a large inner surface.
  • the free blade end which has the maximum amplitude of the deflection (and thus also the maximum vibration speed or maximum vibration accelerations) when the free-standing blade vibrates, is provided with a hollow body or a hollow body is arranged in the region of the free end.
  • a damping medium is located in the hollow body, the hollow body advantageously being only partially filled with the damping medium.
  • the damping medium can only move relative to the hollow body within the hollow body, which has a large inner surface, due to its own inertia and due to a toughness which is effective in a shear flow, so that frictional energy is released from the blading, so that the blading can be effectively removed.
  • the hollow body advantageously connects at least two adjacent blades to one another. This also prevents opposing movements of the blades in the longitudinal direction of the binding pin and thus stiffening the blades.
  • the hollow body is designed as a sleeve.
  • the cavity lies in the neutral fiber of the sleeve, which has several advantages: If the hollow body is designed as a binding pin for connecting two blades, the binding pin is subjected to bending due to its longitudinal load due to its own weight in the centrifugal force field. This bending stress is significantly lower in the case of sleeves compared to a solid cylinder with the same outside diameter, because the material in the area of the neutral fiber represents a load without any significant increase in the bending stiffness to contribute this component. The same mode of action is obtained with a hollow cover band.
  • the binding pin designed as a sleeve e.g. a hollow binding pin, which usually can absorb lighter damping medium compared to the material of the hollow body, without it having to be significantly reinforced.
  • a small outside diameter is of great importance insofar as the flow cross section is reduced by it and consequently losses in efficiency have to be accepted.
  • the hollow bodies can advantageously on the blades in a recess provided in the circumferential direction, e.g. a borehole.
  • a hollow body on both longitudinal sides of the blades e.g. in the form of a support wing, be attached so that the blades or the like through holes. be weakened.
  • the bores are advantageously introduced into the blades at an angle and laterally offset from the circumferential line, because the free length of the binding pin is shortened and the load thus drops significantly, or the pin can be designed with a smaller outer diameter. If two blades are connected to a hollow body designed as a binding pin, this extends from somewhat in front of the rear edge of the one blade to a point somewhat behind the front edge of the other blade. In addition to bending vibrations, torsional vibrations are also impeded or damped by such a zigzag binding.
  • the loose insertion of the hollow body into the receptacles of the blades also causes additional damping at relatively low speeds due to the use of micro-friction in the interface between the hollow body and the blade.
  • the simple replacement of damaged hollow bodies is also advantageous.
  • a further embodiment provides that a hollow body containing a damping medium is arranged in the area of the shroud.
  • This hollow body can be attached to the shroud or integrated in the shroud.
  • the hollow body is advantageously designed as a circumferential recess, e.g. Bore or the like .. This reduces the weight of the shroud, which leads to a lower static stress on the shroud and the blade itself.
  • several parallel recesses can also be made in the cover band, so that the bending load on the cantilever cover band can be further reduced in a targeted manner and a larger friction surface is available for the damping medium.
  • the hollow body has a continuous threaded bore on the inside to enlarge the surface. This effect is also achieved by a surface that is rough on the inside in a different way.
  • a simple sealing of the hollow body is achieved in that it is sealed on both sides with closure elements in a fluid-tight manner.
  • closure elements can be simple screw plugs, which can also serve as an axial securing means if the binding sleeves are loosely inserted.
  • the closure elements prevent the damping medium from escaping, which would not lead to a reduction in the damping capacity, but could also be disadvantageous in some applications from a system perspective.
  • the damping medium can be a liquid, e.g. Oil or sodium at a higher temperature can be a granulate or a mixture of the two.
  • the viscosities of the liquids are matched to the working temperature and the required damping in the machine.
  • baffles can be used as a labyrinth spiral, wire mesh or the like. be trained.
  • Fig. 1 shows a section with two blades (1 and 2) from an impeller (3) which rotates at an angular velocity Omega.
  • a hollow body (5) in the form of a binding pin (6) is arranged in the area of the free blade ends (4).
  • This binding pin (6) is fixed loosely or rigidly in recesses (7), which are designed, for example, as bores (8), on the blades (1 and 2) and connects the two blades (1 and 2) to one another.
  • the binding pin (6) is hollow in the manner of a sleeve (10), which can be achieved, for example, by means of a through hole.
  • each has an internal thread (13) which serves to fix a closure element (14) which closes the cavity of the binding pin (6).
  • the closure element (14) which is designed as a screw-in closure plug (15), also serves, by means of its closure plug (16) projecting beyond the binding pin (6), as an axial securing means against falling out of the recesses (7) of the blades (1 and 2).
  • Fig. 2 shows a blade (17) which has a shroud (18) at its free blade end (4).
  • the cover band (18) forms the hollow body (5), which contains the damping medium (9).
  • the cavity (19) is e.g. formed by a through hole (23).
  • screwable plugs (20) serve as closure elements (14).
  • FIG. 3 shows an impeller (3) in which the blades (1 and 2) have hollow bodies (5) in the form of support vanes (22) attached to the blade profile (21). These support wings (22) are also hollow and contain the damping medium (9). For centering and mutual support, the support wings (22) have wedge-like or groove-like ends that are braced against one another, but without hindering temperature and centrifugal expansion in the circumferential direction.
  • the blades (1 and 2) can also be provided with hollow bodies (5) which penetrate the blades (1 and 2) in the manner of a binding pin and the blades (1 and 2) each on the opposite Blade profiles (21), as shown in Fig. 3, protrude (not shown).
  • Figures 4a to 4c show sections of the hollow body (5), in particular the nature of the inner surface (24) of the cavity.
  • the inner surface (24) is formed by an internal thread (25). This has the advantage that both the threads for the screw-in closure elements (14) and a rough surface (24) of the cavity are created in one operation.
  • the inner surface (24) is roughened artificially or is already present in a rough form due to a correspondingly rough manufacturing process. Due to the roughness, a good transfer of the change in movement of the blades (1, 2 and 17) to the damping medium (9) is effected.
  • this damping medium (9) can fill the cavity of the hollow body (5) to more than 50% (see FIG. 4b) or equal to / less than 50% (see FIG. 4a); in addition to the effect of damping other aspects such as weight loading or shifting are taken into account.
  • the inner surface 24) of the hollow body (5) is mechanically almost smooth, so that an effective transmission of the movement of the blades (1, 2 and 17) to the damping medium (9) hardly takes place due to the lack of surface unevenness.
  • the transmission is achieved in that in the cavity, e.g. can be a bore (8), a chicane (25) for the damping medium (9) is embedded in the form of a wire mesh and this is partially surrounded by the damping medium (9) and flows through.
  • FIGS. 5a and 5b show advantageous arrangements of hollow bodies (5) designed as binding pins (6).
  • two adjacent blades (1 and 2) are connected to one another by means of the binding pin (6) by penetrating one blade (1 or 2) in the region of its rear edge (26) and the other end of the binding pin (6) in the area of the front edge (27) of the adjacent other blade (2 or 1).
  • the recesses (7), e.g. Bores (8) in the blades (1 and 2) laterally offset to the circumferential line (28) and are inclined relative to it by an angle ⁇ . Attaching the hollow body (5) in this way has the advantage that the blades (1 and 2) are directly or indirectly connected to one another and also torsional portions of the blades (1 and 2) can be hindered and damped.
  • the hollow bodies (5) e.g. Tie pins (6), each alternately offset from the circumferential line (28), wherein the distances (a and b) of the hollow body (5) to the circumferential line can be the same or different.
  • the longitudinal axis of the hollow body is perpendicular to the direction of centrifugal force and parallel to the main direction of vibration of the blades (1 and 2).

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Vibration Dampers (AREA)
EP89105367A 1988-03-28 1989-03-25 Schwingungsdämpfung für Axialbeschaufelungen Withdrawn EP0335299A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3810537A DE3810537A1 (de) 1988-03-28 1988-03-28 Schwingungsdaempfung fuer axialbeschaufelungen
DE3810537 1988-03-28

Publications (1)

Publication Number Publication Date
EP0335299A1 true EP0335299A1 (de) 1989-10-04

Family

ID=6350907

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89105367A Withdrawn EP0335299A1 (de) 1988-03-28 1989-03-25 Schwingungsdämpfung für Axialbeschaufelungen

Country Status (2)

Country Link
EP (1) EP0335299A1 (enrdf_load_stackoverflow)
DE (1) DE3810537A1 (enrdf_load_stackoverflow)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5215442A (en) * 1991-10-04 1993-06-01 General Electric Company Turbine blade platform damper
WO1998012449A3 (en) * 1996-09-17 1998-07-02 Damping system for vibrating members
EP2947271A1 (en) * 2014-05-22 2015-11-25 United Technologies Corporation Airfoil with fluid damper and methods of making
US20160305278A1 (en) * 2015-04-15 2016-10-20 Siemens Energy, Inc. Energy damping system for gas turbine engine stationary vane
DE102020215479A1 (de) 2020-12-08 2022-06-09 Siemens Energy Global GmbH & Co. KG Neuartiges Dämpfungselement für Dampfturbinenschaufeln
CN116591827A (zh) * 2022-02-14 2023-08-15 通用电气公司 用于俯仰控制飞行器的部分跨度护罩

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10309595A1 (de) * 2003-03-05 2004-09-16 Rolls-Royce Deutschland Ltd & Co Kg Rotorschaufel mit viskoser Vibrationsdämpfung

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE471359C (de) * 1925-06-10 1929-02-11 Anders Haakansson Nach Art einer Fluessigkeitsbremse wirkende Bremse
GB545671A (en) * 1940-01-10 1942-06-08 Westinghouse Electric Int Co Improvements in or relating to hydraulic damping devices
US2349187A (en) * 1941-03-08 1944-05-16 Westinghouse Electric & Mfg Co Vibration dampener
CH272378A (de) * 1949-02-17 1950-12-15 Escher Wyss Ag Beschaufelung an Rotoren von axial durchströmten, verwundene Schaufeln aufweisenden Kreiselmaschinen, insbesondere von Dampf-, Gasturbinen und Verdichtern.
US2877980A (en) * 1954-09-28 1959-03-17 Stalker Dev Company Vibration dampers for gas turbine wheels and the like
US2984453A (en) * 1957-03-25 1961-05-16 Westinghouse Electric Corp Vibration damper for blading in elastic fluid apparatus
GB943023A (en) * 1959-04-18 1963-11-27 Gutehoffnungshuette Sterkrade Improvements in or relating to blade arrangements in turbines and compressors
GB1271363A (en) * 1968-08-01 1972-04-19 Rolls Royce Improvements in or relating to rotor blades for fluid flow machines

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE862158C (de) * 1943-10-05 1953-01-08 Brown Ag Schwingungsdaempfer fuer die Schaufeln von Turbomaschinen
GB1037951A (en) * 1964-05-15 1966-08-03 Ass Elect Ind Improvements in or relating to rotor discs of axial-flow turbo-machines
DE2142691C3 (de) * 1971-08-26 1980-10-02 Siemens Ag, 1000 Berlin Und 8000 Muenchen Anordnung zur Schwingungsdämpfung bei freistehenden Turbinenschaufeln
JPS5395406A (en) * 1977-02-02 1978-08-21 Hitachi Ltd Connection structure for vane

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE471359C (de) * 1925-06-10 1929-02-11 Anders Haakansson Nach Art einer Fluessigkeitsbremse wirkende Bremse
GB545671A (en) * 1940-01-10 1942-06-08 Westinghouse Electric Int Co Improvements in or relating to hydraulic damping devices
US2349187A (en) * 1941-03-08 1944-05-16 Westinghouse Electric & Mfg Co Vibration dampener
CH272378A (de) * 1949-02-17 1950-12-15 Escher Wyss Ag Beschaufelung an Rotoren von axial durchströmten, verwundene Schaufeln aufweisenden Kreiselmaschinen, insbesondere von Dampf-, Gasturbinen und Verdichtern.
US2877980A (en) * 1954-09-28 1959-03-17 Stalker Dev Company Vibration dampers for gas turbine wheels and the like
US2984453A (en) * 1957-03-25 1961-05-16 Westinghouse Electric Corp Vibration damper for blading in elastic fluid apparatus
GB943023A (en) * 1959-04-18 1963-11-27 Gutehoffnungshuette Sterkrade Improvements in or relating to blade arrangements in turbines and compressors
GB1271363A (en) * 1968-08-01 1972-04-19 Rolls Royce Improvements in or relating to rotor blades for fluid flow machines

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5215442A (en) * 1991-10-04 1993-06-01 General Electric Company Turbine blade platform damper
WO1998012449A3 (en) * 1996-09-17 1998-07-02 Damping system for vibrating members
US6224341B1 (en) 1996-09-17 2001-05-01 Edge Innovations & Technology, Llc Damping systems for vibrating members
EP2947271A1 (en) * 2014-05-22 2015-11-25 United Technologies Corporation Airfoil with fluid damper and methods of making
US20160305278A1 (en) * 2015-04-15 2016-10-20 Siemens Energy, Inc. Energy damping system for gas turbine engine stationary vane
US9777594B2 (en) * 2015-04-15 2017-10-03 Siemens Energy, Inc. Energy damping system for gas turbine engine stationary vane
DE102020215479A1 (de) 2020-12-08 2022-06-09 Siemens Energy Global GmbH & Co. KG Neuartiges Dämpfungselement für Dampfturbinenschaufeln
EP4012159A1 (de) * 2020-12-08 2022-06-15 Siemens Energy Global GmbH & Co. KG Dämpfungselement für dampfturbinenschaufeln
CN116591827A (zh) * 2022-02-14 2023-08-15 通用电气公司 用于俯仰控制飞行器的部分跨度护罩

Also Published As

Publication number Publication date
DE3810537C2 (enrdf_load_stackoverflow) 1992-06-17
DE3810537A1 (de) 1989-10-19

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