EP2180195A2 - Turbomachine avec contrôle du jeu des aubes - Google Patents

Turbomachine avec contrôle du jeu des aubes Download PDF

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Publication number
EP2180195A2
EP2180195A2 EP09010618A EP09010618A EP2180195A2 EP 2180195 A2 EP2180195 A2 EP 2180195A2 EP 09010618 A EP09010618 A EP 09010618A EP 09010618 A EP09010618 A EP 09010618A EP 2180195 A2 EP2180195 A2 EP 2180195A2
Authority
EP
European Patent Office
Prior art keywords
ivh
randleitapparats
gap
profiles
blade
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Withdrawn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
EP09010618A
Other languages
German (de)
English (en)
Other versions
EP2180195A3 (fr
Inventor
Volker Dr. Gümmer
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.)
Rolls Royce Deutschland Ltd and Co KG
Original Assignee
Rolls Royce Deutschland Ltd and Co KG
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 Rolls Royce Deutschland Ltd and Co KG filed Critical Rolls Royce Deutschland Ltd and Co KG
Publication of EP2180195A2 publication Critical patent/EP2180195A2/fr
Publication of EP2180195A3 publication Critical patent/EP2180195A3/fr
Withdrawn legal-status Critical Current

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Classifications

    • 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
    • F04D29/522—Casings; Connections of working fluid for axial pumps especially adapted for elastic fluid pumps
    • F04D29/526—Details of the casing section radially opposing blade tips
    • 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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/68—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers
    • F04D29/681—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers especially adapted for elastic fluid pumps
    • F04D29/685—Inducing localised fluid recirculation in the stator-rotor interface

Definitions

  • the invention relates to a fluid flow machine with a running column intake according to claim 1.
  • a sketch of conventional slots and grooves 10 is in the 1a and 1b shows given.
  • Simple concepts known from the prior art of casing treatments in the form of slots and / or chambers in the annular channel wall offer an increase in the stability of the fluid flow machine.
  • the increase in stability is achieved due to the unfavorably chosen arrangement or shaping only at loss of efficiency.
  • the known solutions take part, a large space at the periphery of the annular channel the Strömungsarbeitsmaschine, are due to their shape only partially effective and / or are limited to the arrangement of a housing surrounded by a rotor blade row.
  • the present invention has for its object to provide a fluid flow machine of the type mentioned, which has a very effective boundary layer control in the blade tip area while avoiding the disadvantages of the prior art.
  • the invention thus relates to a blade row of a free blade end and tread flow machine, wherein at least a portion of the trough is retracted by a finite amount from the main flow path boundary into the main flow path, the trough no longer being traversed by the main flow path boundary at the retracted positions a traversed by the main flow and connected to the Hauptströmungspfadberandung Randleitapparat consisting of a series of straight or curved profiles is limited.
  • the nip draw according to the invention relates to arrangements with a running gap and relative movement between the vane end and main flow path boundary, both on the housing and on the hub of the turbomachine.
  • the present invention thus relates to fluid flow machines such as fans, compressors, pumps and fans, in both axial, semi-axial and radial designs.
  • the working medium or fluid may be gaseous or liquid.
  • the turbomachine may include one or more stages, each having a rotor and a stator, in some cases the stage is merely formed by a rotor.
  • the rotor consists of a number of blades, which are connected to the rotating shaft of the machine and deliver energy to the working fluid.
  • the rotor can be designed with or without shroud on the outer blade end.
  • the stator consists of a number of stationary blades, which can be designed on the hub side as the housing side with a fixed or free blade end.
  • the rotor drum and the blading are usually surrounded by a housing, in other cases, for. As in propellers or propellers, no housing exists.
  • the machine can also have a stator in front of the first rotor, a so-called leading wheel. At least one stator or Vorleitrad may - unlike the immovable fixation - be rotatably mounted to change the angle of attack. An adjustment is made for example by a spindle accessible from outside the annular channel.
  • the turbomachine may have at least one row of adjustable rotors.
  • the turbomachine according to the invention may have two counter-rotating shafts in multiple stages, so that the rotor blade rows change the direction of rotation from stage to stage. There are no stators between successive rotors.
  • the fluid flow machine can alternatively have a bypass configuration such that the single-flow annular channel divides behind a certain row of blades into two concentric annular channels, which in turn accommodate at least one additional row of blades.
  • Fig.2 shows examples according to the invention relevant flow machines.
  • the Figure 3 shows a prior art splitting assembly in the meridian plane formed by the axial direction x and the radial direction r in the region of the blade end of a blade row 5 of a fluid flow machine.
  • the nip 11 at the tip of the free blade end is located directly at the edge of the main flowpath 2, which is formed by a hub or housing assembly 6.
  • the gap 11 is formed by the inner or outer annular channel contour (hub or housing 6) of the fluid flow machine on one side and by the tip of a rotor or stator blade on the other side.
  • the Figure 4 shows in the same representation an example of a gap arrangement according to the invention in the meridian plane formed by the axial direction x and the radial direction r in the region of the blade end of a row of blades of a fluid flow machine.
  • the nip 11 at the tip of the free blade end is a finite distance from the main flow path boundary.
  • the running gap 11 By different distances of the running gap 11 from the main flow path boundary at the leading and trailing edges, the running gap is inclined with respect to the main flow path boundary and also with respect to the meridional flow.
  • the gap leakage flow is reduced and in particular a meridional return flow in the region of the running gap is suppressed.
  • an edge guiding apparatus In the gap formed between the running gap 11 and the main flow path boundary by drawing the running gap 11 into the main flow path is an edge guiding apparatus, consisting of a series of straight or curved profiles.
  • the Randleitapparat is firmly connected to the main flow path boundary forming component group.
  • a straight (as in Fig. 4 shown) or curved / kinked line course may be provided.
  • the Fig. 4b shows the definition according to the invention relevant characteristics of the running gap arrangement.
  • the insertion depth of the running gap 11 may vary according to the invention.
  • the definition of the parameters takes place with the aid of a reference straight line through the points P and S of the main flow path boundary, when the peripheral guide device is provided in the flow direction up to or beyond the trailing edge of the blade row.
  • the reference line is defined by the points P and N.
  • the trough insertion depth at the leading edge tV is defined as the distance of the front gap edge point M from the main flow path boundary measured in the direction perpendicular to the reference line.
  • the running nip depth at the trailing edge tH is defined as the distance of the trailing nip point N from the main flow path boundary as measured in the direction perpendicular to the reference line.
  • the length of the blade tip IVH is defined as the vertical distance of the trailing edge point H from the orthogonal to the reference straight line passing through the leading edge point V.
  • the leading edge offset dVM is defined as the vertical distance of the gap edge point M from the orthogonal line passing through the leading edge point V to the reference line.
  • the trailing edge offset dHN is defined as the vertical distance of the gap edge point N from the orthogonal line passing through the trailing edge point H to the reference line.
  • the current extension of Randleitapparates v is defined as the vertical distance of the contour point P of the main flow path boundary of the extending through the leading edge point V orthogonal to the reference line, and positive as drawn.
  • the current extension of the Randleitapparates w is defined as the vertical distance of the contour point S of Kleinströmungspfadberandung of the running through the leading edge point V orthogonal to the reference line, and positive as drawn.
  • the trough insertion depth at any point within the bladed region (between leading and trailing edges) of the blade row 5 is defined as the distance of the respective point from the main flowpath boundary measured in the direction perpendicular to the reference line.
  • the Fig. 5a shows two Laufspaltan extracten invention, in which the Randleitapparat 10 extends along the entire blade tip.
  • the Randleitapparat 10 extends along the entire blade tip.
  • a variant with a straight course of the main flow path boundary is shown at the top and a variant with a curved course of the main flow path boundary at the bottom.
  • the feed depth of the running gap is greater at the leading edge than at the trailing edge (tV> tH).
  • the view Z-Z is drawn in both variants.
  • the sectional plane Z-Z extends within the main flow path through the blades 5 located there, of which three are shown in the section shown.
  • the view then falls on the Randleitapparat 10, which consists of a series of slim straight sections 12 here.
  • the Randleitapparat 10 is firmly connected to the main flow path boundary.
  • the blades 5 of the blade row execute a (rotating) relative movement with respect to the edge guiding apparatus 10 and with respect to the main flow path boundary.
  • the main flow passes the arrangement from left to right, see thick arrow.
  • the flow through two adjacent passages of Randleitapparats 10 is indicated by a thin arrow.
  • the profiles and the passages of Randleitapparats 10 are running in this example.
  • the connecting line of the leading edge points V of the blades is indicated by VL and the connecting line of the trailing edge points H of the blades is indicated by HL.
  • VL and HL is the bladed region of the blade row 5, which also coincides in the example of the invention shown here substantially with the area occupied by the Randleitapparat 10 area.
  • the Fig. 5b shows two further inventively possible arrangements of Randleitapparats 10 in the off Fig. 5a known view ZZ.
  • On the left side of the Randleitapparat 10 consists of a series of curved profiles 12 of constant thickness.
  • the passage between two profiles 12 of the Randleitapparats 10 is significantly curved, such that the circumferential component of the flow when passing the Randleitapparats 10 in the direction of relative movement of the blade row 5 increases.
  • the stagger angle ⁇ R of the profiles of the Randleitapparates 10 and the stagger angle ⁇ S of the profiles of the blade row 5 have opposite sign in this case.
  • the stagger angle is measured between the meridian direction m and the chord line of the respective profile 12.
  • the stagger angle ⁇ R of the profiles of Randleitapparates 10 has in the indicated direction negative sign.
  • the stagger angle ⁇ S of the profiles of the blade row 5 has positive sign in the direction shown.
  • the longitudinal symmetry line of the profile is used to determine the stagger angle.
  • the rear gap edge point N of the Randleitapparats coincides here with the rear contour point S of the main flow path boundary. This gives the Randleitapparat 10 in meridian section according to the invention a favorable wedge-like shape.
  • the right side of the image shows the view Z-Z in the plane formed by the meridional direction m and the circumferential direction u.
  • the profiles 12 and the passages 13 of the Randleitapparats 10 are executed here again straight and the area occupied by the Randleitapparat 10 substantially coincides with the bladed region of the blade row 5 (between VL and HL).
  • the stagger angle ⁇ R of the profiles of the Randleitapparates and the stagger angle ⁇ S of the profiles of the blade row have the same sign in this case.
  • values of the staggering angle of Randleitapparatprofile in the range between -70 ° and 70 ° are possible (-70 ° ⁇ R ⁇ 70 °), but it is particularly favorable to provide values from the range -40 ° ⁇ R ⁇ 30 °.
  • the Fig. 7a shows two Laufspaltan extracten invention, in which the Randleitapparat 10 extends over the front part of the blade tip.
  • the rear gap edge point N is now located on the main flow path boundary and the contour point S lies within the bladed region of the blade row 5.
  • the depth of the feed gap 11 decreases to zero to point S.
  • the gap depth is thus zero in the area between the contour point S and the rear gap edge point N.
  • the Randleitapparat 10 has in meridian section according to the invention a favorable wedge-like shape.
  • the left-hand side of the picture above shows an arrangement according to the invention in which the main flow path boundary runs approximately rectilinearly and a break point K is provided in the blade tip due to the wedge-like shape of the edge guide apparatus 10 in the vicinity of the contour point S.
  • the running gap also runs with kink.
  • the lower left part of the picture shows an arrangement according to the invention, in which the main flow path boundary runs in such a swung manner that, despite the wedge-like shape of the edge guiding apparatus 10, a kink-free course of the blade tip and the running gap 11 can be provided.
  • the right side of the image shows the view ZZ in the plane formed by the meridian direction m and the circumferential direction u.
  • the profiles and the passages of Randleitapparats 10 are executed here curved and the area occupied by Randleitapparat 10 takes on the leading edge line VL starting only a part of the bladed region of the blade row 5 a.
  • the stagger angle ⁇ R of the profiles of the Randleitapparates 10 and the stagger angle ⁇ S of the profiles of the blade row 5 have here opposite sign.
  • the Fig. 7b shows two further inventively possible arrangements of Randleitapparats 10 in the off Fig. 7a known view ZZ.
  • the Randleitapparat 10 On the left side, the Randleitapparat 10 consists of a series of non-arched profiles of constant thickness.
  • the right side of the image Randleitapparat 10 On the right side of the image Randleitapparat 10 consists of a series curved profiles of constant thickness.
  • the passage between two profiles of Randleitapparats 10 is curved such that the circumferential component of the flow increases when passing the Randleitapparats 10 against the direction of the relative movement of the blade row 5.
  • the Fig. 7c shows two further inventively possible arrangements of Randleitapparats 10 in the off Fig. 7a known view ZZ.
  • the Randleitapparat On the left side of the image, the Randleitapparat consists of a series of non-arched wedge-like profiles with maximum thickness at their trailing edge. The displacement effect increases continuously here in the flow direction.
  • the Randleitapparat 10 On the right side, the Randleitapparat 10 consists of a series of non-arched thick profiles with maximum displacement effect in its middle part. In both image halves 10, the longitudinal axis of symmetry is drawn for a profile of Randleitapparates, which is to be used in this type of profiles for determining the staggering angle.
  • the Fig. 8 shows a favorable nip arrangement according to the invention, in which the Randleitapparat 10 extends in the meridian section (xr plane) only along the front third of the blade tip, according to the following proviso: w ⁇ 0.33 IVH.
  • the right side of the image shows the view ZZ in the plane formed by the meridian direction m and the circumferential direction u.
  • the profiles and the passages of Randleitapparats 10 are made here short and straight.
  • the Fig. 9 shows a further advantageous nip arrangement according to the invention. As shown in the left half of the image in the meridian section (xr plane), the running gap runs parallel to the machine axis.
  • the front contour point P of the main flow path boundary is also provided clearly upstream of the front gap edge point M, so that a clear current extension of the Randleitapparates 10 v of about 0.4 ⁇ IVH results.
  • the leading edge of the Randleitapparatprofile no longer runs, as in solutions according to the invention shown above, substantially orthogonal to the running gap or Hauptströmungspfadberandung, but (corresponding to an aerodynamic sweep) obliquely to the running gap and obliquely to Hauptströmungspfadberandung.
  • the right side of the image shows the view Z-Z in a known manner.
  • the profiles and the passages of Randleitapparats 10 are executed here curved.
  • the Randleitapparat 10 assumes due to the intended sweep an area upstream of the leading edge line VL and a portion of the bladed region of the blade row 5 a.
  • the Fig. 10 shows further inventively favorable Laufspaltan extracten with a low gap inclination angle.
  • the gap inclination angle ⁇ is measured between the longitudinal axis of the turbomachine and a straight line through the points V and H when the blade tip has no kink, see left half of the picture.
  • the gap inclination angle ⁇ is measured between the longitudinal axis of the fluid flow machine and a straight line through the points V and K when the blade tip has a break point K, see right half of the figure. ⁇ is positive as shown.
  • the gap inclination angle has an amount of less than 8 ° (-8 ° ⁇ ⁇ 8 °).
  • a gap arrangement according to the invention is shown with an arranged in the front region of the blade row 5 Randleitapparat 10 and adjoining in the flow direction Anstreifbelag 14 which is provided in the rear part of the bladed region of the blade row 5.
  • Anstreifbelag 14 which is provided in the rear part of the bladed region of the blade row 5.
  • Fig. 12 Also shown is a gap arrangement according to the invention with an edge guide device 10 arranged in the front region of the blade row and an abradable coating 14 adjoining in the flow direction, which is provided in the rear part of the bladed region of the blade row 5.
  • the Randleitapparat 10 in Compared to Anstreifbelag 14 to take something back, going to the fact that the running gap 11 in the region of Randleitapparats 10 is greater than in the region of the squeal 14th
  • the present invention allows a significantly higher aerodynamic load capacity of rotors and stators in turbomachines, with constant or increased efficiency. A reduction in the number of parts and the component weight of more than 20% can be achieved. Using the concept in the high-pressure compressor of an aircraft engine with around 25,000 pounds of thrust results in a reduction in specific fuel consumption of up to 0.5%.
EP09010618.8A 2008-10-21 2009-08-18 Turbomachine avec contrôle du jeu des aubes Withdrawn EP2180195A3 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102008052401A DE102008052401A1 (de) 2008-10-21 2008-10-21 Strömungsarbeitsmaschine mit Laufspalteinzug

Publications (2)

Publication Number Publication Date
EP2180195A2 true EP2180195A2 (fr) 2010-04-28
EP2180195A3 EP2180195A3 (fr) 2015-09-09

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Family Applications (1)

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EP09010618.8A Withdrawn EP2180195A3 (fr) 2008-10-21 2009-08-18 Turbomachine avec contrôle du jeu des aubes

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US (1) US8690523B2 (fr)
EP (1) EP2180195A3 (fr)
DE (1) DE102008052401A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011157927A1 (fr) 2010-06-17 2011-12-22 Snecma Compresseur et turbomachine a rendement optimise.
EP2514975A3 (fr) * 2011-04-20 2014-06-11 Rolls-Royce Deutschland Ltd & Co KG Turbomachine
US9512727B2 (en) 2011-03-28 2016-12-06 Rolls-Royce Deutschland Ltd & Co Kg Rotor of an axial compressor stage of a turbomachine
US9822795B2 (en) 2011-03-28 2017-11-21 Rolls-Royce Deutschland Ltd & Co Kg Stator of an axial compressor stage of a turbomachine

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ITTO20110362A1 (it) * 2011-04-26 2012-10-27 Denso Corp Gruppo ventilatore per veicoli
FR2981131B1 (fr) * 2011-10-07 2013-11-01 Turbomeca Compresseur centrifuge equipe d'un marqueur de mesure d'usure et procede de suivi d'usure utilisant ce marqueur
CN102817873B (zh) * 2012-08-10 2015-07-15 势加透博（北京）科技有限公司 航空发动机压气机的梯状间隙结构
EP2971547B1 (fr) * 2013-03-12 2020-01-01 United Technologies Corporation Stator en porte-à-faux comportant une caractéristique de déclenchement de tourbillon
US10294862B2 (en) * 2015-11-23 2019-05-21 Rolls-Royce Corporation Turbine engine flow path
US10465539B2 (en) * 2017-08-04 2019-11-05 Pratt & Whitney Canada Corp. Rotor casing
US10876423B2 (en) * 2018-12-28 2020-12-29 Honeywell International Inc. Compressor section of gas turbine engine including hybrid shroud with casing treatment and abradable section

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Publication number Priority date Publication date Assignee Title
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FR2961564A1 (fr) * 2010-06-17 2011-12-23 Snecma Compresseur et turbomachine a rendement optimise
RU2568355C2 (ru) * 2010-06-17 2015-11-20 Снекма Компрессор и газотурбинный двигатель с оптимизированным коэффициентом полезного действия
US9488179B2 (en) 2010-06-17 2016-11-08 Snecma Compressor and a turbine engine with optimized efficiency
US9512727B2 (en) 2011-03-28 2016-12-06 Rolls-Royce Deutschland Ltd & Co Kg Rotor of an axial compressor stage of a turbomachine
US9822795B2 (en) 2011-03-28 2017-11-21 Rolls-Royce Deutschland Ltd & Co Kg Stator of an axial compressor stage of a turbomachine
EP2514975A3 (fr) * 2011-04-20 2014-06-11 Rolls-Royce Deutschland Ltd & Co KG Turbomachine
US9816528B2 (en) 2011-04-20 2017-11-14 Rolls-Royce Deutschland Ltd & Co Kg Fluid-flow machine

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Publication number Publication date
DE102008052401A1 (de) 2010-04-22
US8690523B2 (en) 2014-04-08
EP2180195A3 (fr) 2015-09-09
US20100098536A1 (en) 2010-04-22

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