EP3070270A1 - Système d'aube pour une turbomachine doté d'un dispositif d'étanchéité, roue directrice et turbomachine - Google Patents

Système d'aube pour une turbomachine doté d'un dispositif d'étanchéité, roue directrice et turbomachine Download PDF

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Publication number
EP3070270A1
EP3070270A1 EP14192595.8A EP14192595A EP3070270A1 EP 3070270 A1 EP3070270 A1 EP 3070270A1 EP 14192595 A EP14192595 A EP 14192595A EP 3070270 A1 EP3070270 A1 EP 3070270A1
Authority
EP
European Patent Office
Prior art keywords
vane
sealing device
slide plate
stator
guide vane
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
Application number
EP14192595.8A
Other languages
German (de)
English (en)
Other versions
EP3070270B1 (fr
Inventor
Alexander Böck
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.)
MTU Aero Engines AG
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MTU Aero Engines AG
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 MTU Aero Engines AG filed Critical MTU Aero Engines AG
Publication of EP3070270A1 publication Critical patent/EP3070270A1/fr
Application granted granted Critical
Publication of EP3070270B1 publication Critical patent/EP3070270B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
    • F01D11/001—Preventing or minimising internal leakage of working-fluid, e.g. between stages for sealing space between stator blade and rotor
    • 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
    • F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
    • 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
    • F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
    • F01D11/005—Sealing means between non relatively rotating elements
    • 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
    • F01D17/00—Regulating or controlling by varying flow
    • F01D17/10—Final actuators
    • F01D17/12—Final actuators arranged in stator parts
    • F01D17/14—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits
    • F01D17/16—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of nozzle vanes
    • F01D17/162—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of nozzle vanes for axial flow, i.e. the vanes turning around axes which are essentially perpendicular to the rotor centre line
    • 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
    • F01D9/00—Stators
    • F01D9/02—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles
    • F01D9/04—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles forming ring or sector
    • 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
    • F01D9/00—Stators
    • F01D9/02—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles
    • F01D9/04—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles forming ring or sector
    • F01D9/041—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles forming ring or sector using blades
    • 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
    • F01D9/00—Stators
    • F01D9/02—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles
    • F01D9/04—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles forming ring or sector
    • F01D9/042—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles forming ring or sector fixing blades to stators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F04D29/16—Sealings between pressure and suction sides
    • F04D29/161—Sealings between pressure and suction sides especially adapted for elastic fluid pumps
    • F04D29/164—Sealings between pressure and suction sides especially adapted for elastic fluid pumps of an axial flow wheel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/52—Casings; Connections of working fluid for axial pumps
    • F04D29/54—Fluid-guiding means, e.g. diffusers
    • F04D29/56—Fluid-guiding means, e.g. diffusers adjustable
    • F04D29/563—Fluid-guiding means, e.g. diffusers adjustable specially adapted for elastic fluid pumps

Definitions

  • the present invention relates to a guide vane for a turbomachine, with a sealing device at the radially inner end region of the guide vane according to the preamble of claim 1. Furthermore, the present invention relates to a stator according to claim 9 and a turbomachine according to claim 10.
  • turbomachinery efficiency is influenced by various factors and parameters.
  • flow losses due to bypass flows outside of the main flow through the runner and Leitradbeschaufelung reduce the efficiency.
  • Such bypass flows can be at least reduced in different ways in order to avoid loss of efficiency.
  • seals are arranged on blade arrangements of the turbomachine in order to reduce bypass flows.
  • An object of the present invention is to propose a further stator blade for a turbomachine which provides a sealing device at the radially inner end portion of the stator vane for sealing leakage flow between the stator vane and an inner ring connected to the stator vane. Furthermore, it is an object of the present invention to propose a corresponding stator and a turbomachine.
  • the object of the invention is achieved by a guide blade with the features of claim 1. It is further achieved by a stator with the features of claim 9 and a turbomachine with the features of claim 10.
  • a sealing device which is arranged movably with respect to the guide blade.
  • the sealing device is positionable in at least one open or closed arrangement for sealing the leakage flows.
  • the stator according to the invention has at least one guide vane according to the invention.
  • the stator may be a section of a compressor stage.
  • the stator can be referred to as Leitschaufelrad.
  • the inventive has at least one inventive stator.
  • the turbomachine may be a gas turbine or an aircraft engine.
  • Embodiments of the invention may include one or more of the features mentioned below.
  • the turbomachine is an axial flow machine, in particular a gas turbine.
  • the gas turbine can be an aircraft engine.
  • the vane is a vane of a compressor stage, such as a low pressure compressor stage and / or a high pressure compressor stage.
  • a plurality of guide vanes arranged in the circumferential direction of the turbomachine are connected to the inner ring.
  • the vanes and the inner ring connected to the vanes may be referred to as a vane ring or stator or stator ring.
  • the inner ring is provided and configured to be connected to a seal carrier.
  • the connection is in particular releasable again, for example by means of a web-groove connection.
  • the inner ring has a groove or a collar, on which the Leitschaufeh-ing the seal carrier is pushed in the circumferential direction.
  • the sealing device is translationally and / or rotationally (rotatably) arranged opposite the vane or positioned or mounted.
  • the sealing device may move in a direction perpendicular to the longitudinal axis of the vane.
  • the sealing device may move in the region of a vane platform at the radially inner end portion of the vane to at least reduce a leakage flow.
  • the sealing device is positioned in an open arrangement, where by an "open arrangement” is meant an open or open flow cross-section of a leakage flow which is not or at least not completely closed by the sealing device in this arrangement.
  • This position can be described as a mounting position. In the mounting position, the sealing device is not or not yet positioned in a manner to seal or reduce the leakage flow. Only after a movement (translational and / or rotatrisch) out of this mounting position, a leakage current is effectively at least partially reduced.
  • the seal assembly in some embodiments of the present invention is positioned in a closed configuration to seal the leakage flows.
  • the sealing device, or a portion of the sealing device at least partially closes a flow cross-section of a leakage flow.
  • the arrangement or position of the sealing device is referred to in the closed arrangement in some embodiments of the invention as a hook position.
  • the sealing device In the hook position, the sealing device may be moved or shifted so far until the sealing device rests as a stop on one or more hooks.
  • the hook can be referred to as a stop hook.
  • the sealing device In the hook position, the sealing device can close a gap or a region of a flow cross-section of a leakage flow. In the hook position, the sealing device can advantageously at least reduce the leakage flow.
  • the stop hook limited in some embodiments of the invention, the displacement of the sealing device.
  • the stop hook can be referred to as a safety hook.
  • the stop hook can also limit rotations of the sealing device.
  • the pivot point for limiting the movement of the sealing device by means of rotations may be inside or outside the sealing device. In other words, the sealing device may rotate about the pivot point of the stop hook or hooks.
  • the sealing device or portions of the sealing device is moved by means of the leakage flow.
  • the flow pressure of the leakage flow may be large enough to change the position of the sealing device.
  • This movement of the sealing device may be referred to as pressure-controlled movement.
  • the sealing device or at least a portion of the sealing device can be moved solely by the leakage flow.
  • the vane is rotatably mounted about a longitudinal axis of the vane.
  • the radially inner and / or outer ends of the vanes are provided with lugs or pins in which or around which the Turn vanes.
  • the radially outer pin may be referred to as an outer pin, the radially inner pin as an inner pin.
  • the inner pin may be arranged or guided in some embodiments of the invention in the inner ring.
  • bushings for example bearing bushes, in which the guide vanes rotate are arranged in the inner ring.
  • the sealing device is a plate or a slide plate.
  • the sealing device is in particular made of metal or has metal.
  • the sealing device has a bore or through-hole for flowing through at least part of the leakage flow.
  • the bore is arranged in particular perpendicular to the surface of the slide plate.
  • the sealing device and / or the vane has at least two stop hooks.
  • the stopper hooks may be arranged asymmetrically with respect to a center axis of the sealing device in a shifting direction of the sealing device.
  • the geometry of the stop hooks may be designed and optimized so that all possible positions of the sealing device, including possible boundary layers, prevent jamming of the sealing device in the guide vane.
  • the sealing device is pocket-shaped in a stator vane platform.
  • the vane and / or the sealing device is manufactured by a generative manufacturing process.
  • the generative manufacturing process may be a Selective Laser Melting (SLM) process.
  • Some or all embodiments according to the invention may have one, several or all of the advantages mentioned above and / or below.
  • the leakage flow in the connection region between the guide vane and the inner ring, which is in particular connected to a seal carrier in a stator can be advantageously at least reduced.
  • a reduction in the leakage flow can increase the efficiency of a turbomachine in which the stator is installed.
  • the seal carrier may have an inlet seal or be connected to an inlet seal.
  • influencing the flow of adjacent guide vanes in a guide wheel in the installed state can advantageously be at least reduced by at least reducing the leakage flow in the connection region between the guide vane and the inner ring.
  • Reducing the effect on the flow, in particular the leading vane leading edge flow, of adjacent vanes can result in an improvement in the flow around the adjacent vane and, thus, advantageously improves the vane flow efficiency.
  • Reducing the influence of the flow of adjacent vanes in the stator in the installed state can increase the pumping stability of a compressor stage into which the stator can be installed.
  • the guide vane according to the invention and / or the sealing device according to the invention can advantageously be produced inexpensively by means of a generative production method, in particular by means of selective laser melting.
  • Fig. 1 shows a section of a Leitradkranzes 100 in perspective view of the prior art.
  • the Leitradkranz 100 has a plurality of circumferentially u side by side arranged vanes 200.
  • the guide vanes 200 each have outer pins 1, which at the radially outer end with a housing of a turbomachine (in Fig. 1 not shown), in particular a gas turbine, are connected.
  • the radially inner end of the outer journal 1 is connected to the guide blade profiles 3.
  • the inner ring 7 and the seal carrier 9 are in particular divided into two semicircular segments, which are pushed into one another in the circumferential direction.
  • the seal carrier 9 may be connected to inlet seals or inlet sealing segments.
  • Fig. 2 shows a detail Fig. 1 in a sectional view with a Leitradschaufeltex 11 and the inner ring 7 according to the prior art.
  • the vane 200 is connected to the inner ring 7 by means of the pin 5 and a bushing 13.
  • the bush 13 is additionally inserted into a bore 15 of the inner ring 7.
  • the seal carrier 9 and the inner ring 7, both of which are designed in particular as semicircular segments, can be pushed one into the other in the circumferential direction.
  • the segments are secured by means of a locking pin 17 in the installed state against displacement of the seal carrier 9 and the inner ring 7 (relative to each other).
  • inlet seals 19 are connected, which are provided for forming a sealing gap between sealing tips 21, for example, a rotating shaft 23.
  • the inlet seals 19 are in particular segmented over the circumference.
  • a leakage flow 25 is formed, in particular between the guide blade platform 11 and the inner ring 7. The leakage flow 25 flows due to the pressure gradient from the pressure side of the blade profile to the suction side.
  • Fig. 3 shows the leakage flow 25 from Fig. 2 in perspective view with an adjacent guide vane 200 'according to the prior art.
  • a portion of the leakage stream 25 ' may be referred to as a blowing jet
  • the leakage stream 25' may be referred to as a blowing jet
  • Fig. 4a shows in a sectional view in a plane with the axes of circumferential direction u and axial direction a, perpendicular to the radial direction r, a guide vane 300 according to the invention with a sealing device 27 and two stop hooks 29 which are connected to the guide vane 300.
  • the sectional view of the Fig. 4a is approximately centrally in the radial direction r at the height of Leitradschaufelt 11 (see Fig. 6 ) arranged.
  • the vane profile 3 (see Fig. 6 ) is not visible in this section plane, but sketched dashed lines to illustrate the arrangement of the sealing device 27.
  • the pin 5 (radially inward with respect to the Leitradschaufelt 11) is also shown in dashed lines, as it is not visible in this sectional view. For example in Fig. 6a and 5b the pin 5 is shown.
  • the sealing device 27 is designed as a slide plate 27 in this embodiment.
  • the slide plate 27 can move in the circumferential direction u and in the axial direction a (displacement path 28), but not in the radial direction r (see Fig. 6 ). The movement is limited by the two stop hooks 29, on which the two paragraphs 31 of the slide plate 27 can rest.
  • the position of the slide plate 27 shown in Fig. 4a may be referred to as a mounting position.
  • the slide plate 27 can rotate within the described freedom of movement about a pivot point 33 of the stop hook 29 with a twist angle 30.
  • the slide plate 27 is shown in a hook position 35.
  • the maximum displacement of the slide plate 27 is achieved with respect to the starting position (mounting position).
  • the circle 37 represents the bore 37 in the inner ring 7 for receiving the Leitradschaufelt 11 of the guide vane 300 (see Fig. 1 and Fig. 2 ).
  • the bore 37 of the inner ring 7 may be offset or.
  • the dashed circle 39 represents a maximum displacement of the bore 37 due to wear.
  • the slide plate 27 can at least partially cover the gap 41 between the outer boundary 43 of the stator blade platform 11 and the bore 37 and thus a leakage flow 25 (see Fig. 3 ), at least partially, prevent.
  • FIG. 4a an access hole 45 is shown, which is arranged in the underside (radially inner side) of the Leitradschaufeltex 11.
  • the function of the access hole 45 is in Fig. 4b described.
  • Fig. 4b shows the slide plate 27 in a relation to the starting position or starting position (mounting position) shifted position in which the gap 41 is partially covered or closed by means of the slide plate 27.
  • This position can be referred to as a nominal position (in built-in condition and pressurized).
  • the slide plate 27 rests in the region 47 on the bore 37 of the inner ring 7.
  • the in Fig. 4b Upper paragraph 31 of the slide plate 27 abuts the upper stop hook 29.
  • lies the lower shoulder 31 does not abut the lower stop hook 29.
  • the slide plate 27 can from the starting position ( Fig. 4a ) in the shifted position ( Fig. 4b ) are moved and displaced by means of a flow flowing through the access bore 45 or the pressure force caused by this flow.
  • the direction of the compressive force of this flow is represented by the arrow 49.
  • Fig. 4c shows an alternative, displaced contour 51 (or contour withdrawal) of the slide plate 27. Due to the displaced contour 51, the abutting portion 47 'of the slide plate 27 moves on the bore of the inner ring 7 also.
  • the adjoining area 47 '(or adjacent point) shifts into Fig. 4c downward.
  • Other contour shapes could, for example, move the adjoining region 47 'further downwards or further upwards.
  • a displacement of the abutting portion 47 ' has an effect on the covered or closed region of the gap 41 between the bore 37 (or the worn bore 39) and the outer boundary of the Leitradschaufelon 43.
  • This may be particularly relevant and advantageous if the outflow of the Leakage leakage 25 (see Fig. 3 ) should be covered as precisely as possible, for example, to optimize the efficiency targeted.
  • the outflow area of the leakage outlet 25 can be changed and influenced by the rotation of the guide vane 400 according to the invention about its longitudinal axis 14.
  • the rotation of the guide vane 400 according to the invention or the position of the vane profile 3 with respect to its inflow can depend substantially on the flow conditions in the turbomachine, which is influenced, for example, by a full load or part load operating state.
  • Fig. 5a shows a further vane 300 'according to the invention.
  • the stop hooks 29 ' are offset (or reversed) with respect to the arrangement of the Fig. 4a-c arranged.
  • the paragraphs 31 'of the slide plate 27' are also arranged offset according to the stop hook 29 '.
  • the slide plate 27 ' is positioned in the home position or mounting position.
  • Fig. 5b shows the further guide vane 300 'according to the invention Fig. 5a in a pressurized position (or nominal position).
  • the slide plate 27 ' is in the region 47' to the bore 37 'at.
  • Fig. 6a shows the guide vane 300 of the invention from the Fig. 4a and Fig. 4b in a perspective view.
  • a slot 53 is visible in the stator blade platform 11 in which the slide plate 27 is movably arranged (in the plane with the axial direction a and the circumferential direction u). In the mounting position of the slide plate 27, the slide plate 27 is completely integrated in the slot 53 and does not protrude beyond the outer boundary 43 of the guide vane platform 11.
  • the slide plate 27 in a pressurized position of the slider plate 27, in which a pressing force from the radially inner side of the stator blade platform 11 (in FIG Fig. 6a hidden below the Leitradschaufelt 11) on which the slide plate 27 acts, the slide plate 27 may protrude from the slot 53, but not fall out. Falling out of the slide plate 27 is prevented by the stop hooks 29 on the guide vane 300 and the paragraphs 31 on the slide plate 27.
  • Fig. 6b shows the guide vane 300 according to the invention Fig. 6a seen in a rotated, perspective view from radially inward to radially outward.
  • Fig. 7a shows the guide vane 300 'of the invention Fig. 5a and Fig. 5b in perspective view.
  • the slide plate 27 ' protrudes beyond the outer boundary 43' of the stator blade platform 11 '. This is particularly the case when the slide plate 27 'in the installed state of the guide vane 300' is pressurized, that is, the slide plate 27 'is due to a pressurized flow (in particular a leakage current) through the access hole 45' moves outwardly or moved Service.
  • Fig. 7b shows the guide vane 300 'according to the invention Fig. 7a seen in a rotated perspective view from radially inward to radially outward, with the open access bore 45 '.
  • Fig. 8a shows three different embodiments of guide vanes 200, 300, 300 'in an inner ring 7 in perspective views.
  • the vane 200 corresponds to the prior art and was in Fig. 1 . Fig. 2 and Fig. 3 described.
  • the guide vane 300 according to the invention was in the Fig. 4a-c and Fig. 6a, b described, the guide vane 300 'according to the invention was in the Fig. 5a, b and Fig. 7a, b described.
  • Fig. 8b shows two guide vanes 300 according to the invention in a relation to the Fig. 8a changed adjustment angle.
  • the angle of the vane 300 about its longitudinal axis is referred to as the adjusting angle.
  • the vane profiles 3 of the guide vanes 300 are in Fig. 8b across from Fig. 8a further aligned in the circumferential direction u.
  • This changed setting angle has an influence on the slide plate 27.
  • the slide plate 27 of the vane 300 is moved in a direction oblique to the circumferential direction u and to the axial direction a, to seal the gap 41 (and the leakage current passing through the gap) by means of the slide plate 27.
  • the slide plate 27 is aligned in a direction almost parallel to the axial direction a to seal the gap 41.
  • Fig. 8c shows the arrangement of the guide vanes 300 according to the invention Fig. 8b in another perspective view.
  • At least one region of the guide blade platform 11 may protrude beyond the surface of the inner ring 7.
  • the constructive embodiments of the slide plate 27, the slot 53, the stop hook 29 and the paragraph 31 were carried out such that jamming is largely excluded and the function of the slide plate 27 is ensured. This is achieved in particular in that the stop hooks 29 with different design variants, such as the positioning of the pivot point of the stop hooks 33 (see Fig. 4a ).
  • the shape of the projecting beyond the outer boundary 43 of the Leitradschaufelt 11 region of the slide plate 27 and / or the positioning (depth) of the slide plate 27 with the corresponding abutment region 47 (see Fig. 4b and Fig. 4c ) be executed on the bore of the inner ring 37 such that this contact area 47 even at maximum Verstellwinkeln and maximum wear of the bore of the inner ring 37 (offset the inner ring bore) still comes about.
  • Fig. 9a shows a further guide vane 300 "according to the invention with a further sealing device 27" and two further stop hooks 29 "in a mounting position for inner ring mounting Fig. 8a to 8c ) are inserted or mounted.
  • the inner ring 7 is through the circle 37 or the bore 37 in Fig. 9a indicated.
  • the further sealing device 27 is designed as a slide plate 27".
  • Both the slide plate 27 "and the two other stop hooks 29" are structurally designed such that the slide plate 27 "can be pushed and mounted as an elastic element on or over the stop hooks 29". This assembly process is in the Fig. 11a to 11d described in more detail.
  • the further access hole 45 has, in contrast to the previously shown circular access hole 45 in the Fig. 4 to 8 , a rounded triangular shape.
  • This triangular shape has a relation to the circular cross-sectional shape larger cross-sectional shape to Flowing through fluid.
  • the pressure force caused by this flow can advantageously and better move the slide plate 27 "in the operating state or in use and at least partially close the gap 41 towards the inner ring 7.
  • the previously discussed leakage flow 25 can be at least partially reduced.
  • Fig. 9b shows the guide vane 300 "according to the invention Fig. 9a in the closed state.
  • the spool 27 In the closed state, unlike the open state or mounting state off Fig. 9a , the spool 27 "closes the gap 41 in certain areas. This area is structurally chosen such that a gap flow 25 or leakage flow 25 (see FIG Fig. 2 ) is at least partially reduced on the suction side of the blade profile 3.
  • the slider 27 is displaced as a result of the pressure force of the flow through the access hole 45 'in the direction of the displacement path 28 to the edge of the bore 37 of the inner ring 7.
  • the slider 27 " is located with the two paragraphs 31" on the stop hook 29 ".
  • this guide vane 300 "according to the invention corresponds to a variant which does not have a fulcrum 33 (see FIG Fig. 4a ) having.
  • the section plane BB is in Fig. 10c shown.
  • Fig. 10a shows the guide vane 300 "according to the invention from the Fig. 9b in a perspective view.
  • the stop hook 29 etc. the analogous discussion applies Fig. 6a ,
  • Fig. 10b shows the guide vane 300 "according to the invention from the Fig. 9b in another perspective view.
  • the discussion about Fig. 6b applies analogously to the modified embodiment of the slider 27 ", the stop hook 29" and other changed areas.
  • Fig. 10c shows the guide vane 300 "according to the invention from the Fig. 9b as a sectional view BB.
  • the access bore 45 ' is clearly visible within the vane platform 11 for moving the slide plate 27 ".
  • Fig. 11a shows the first step for mounting the slide plate 27 "on the stop hooks 29" of the guide vane platform 11 "of the guide vane 300" according to the invention.
  • the slide plate 27 " is attached to the upper stop hook 29" with the upper shoulder 31 "and hooked in. Subsequently, the lower shoulder 31" is first applied or applied to the lower stop hook 29 ".
  • Fig. 11b shows the second step for mounting the slide plate 27 "on the vane platform 11".
  • the slide plate 27 is moved or pushed in the direction of arrow 55 so that the lower shoulder 31" can be pushed over the stop hook 29 "by means of an elastic deformation of the slide plate 27".
  • This process can be referred to as "clip in”.
  • Fig. 11c shows the third step for mounting the slide plate 27 ".
  • the slide plate 27" is in the mounted position and the guide vane 300 "can be pushed onto or connected to the inner ring 7 (see FIG Fig. 8a to 8c ). In this mounting position, the gap 41 is not yet closed.
  • Fig. 11d shows the fourth step for assembling the slide plate 27 ", this step is no longer attributable to the actual assembly, in which step pressure is applied through the access bore 45 '(see FIG Fig. 10c ) for moving and closing the gap 41, at least in a partial region of the gap 41 (see Fig. 9b ). Subsequently, the slide plate 27 "bears against the bore 37 of the inner ring 7. This region is shown as the abutting region 47" of the slide plate 27 ".
  • the position of the slide plate 27 may be referred to as a sealing position.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP14192595.8A 2013-11-12 2014-11-12 Système d'aube pour une turbomachine doté d'un dispositif d'ètanchéité, roue directrice et turbomachine. Active EP3070270B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102013222980.1A DE102013222980A1 (de) 2013-11-12 2013-11-12 Leitschaufel für eine Strömungsmaschine mit einer Dichtungsvorrichtung, Leitrad sowie Strömungsmaschine

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EP3128132B1 (fr) * 2015-08-03 2019-03-27 MTU Aero Engines GmbH Élement annulaire d'aube directrice de turbomachine
DE102016207212A1 (de) * 2016-04-28 2017-11-02 MTU Aero Engines AG Leitschaufelkranz für eine Strömungsmaschine
US10801343B2 (en) * 2016-12-16 2020-10-13 Pratt & Whitney Canada Corp. Self retaining face seal design for by-pass stator vanes
DE102017211316A1 (de) 2017-07-04 2019-01-10 MTU Aero Engines AG Turbomaschinen-Dichtring
DE102018213983A1 (de) * 2018-08-20 2020-02-20 MTU Aero Engines AG Verstellbare Leitschaufelanordnung, Leitschaufel, Dichtungsträger und Turbomaschine
DE102019218909A1 (de) * 2019-12-04 2021-06-10 MTU Aero Engines AG Strömungsmaschine
DE102020210094A1 (de) 2020-08-10 2022-02-10 MTU Aero Engines AG Verstellbare Leitschaufelanordnung
US11725533B2 (en) * 2020-11-10 2023-08-15 Pratt & Whitney Canada Corp. Variable guide vane assembly and bushing ring therefor
US11814969B2 (en) 2021-07-21 2023-11-14 Pratt & Whitney Canada Corp. Gas turbine engine with low-pressure compressor bypass
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US10060278B2 (en) 2018-08-28
EP3070270B1 (fr) 2022-03-09
DE102013222980A1 (de) 2015-06-11
US20150192025A1 (en) 2015-07-09

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