EP1793089A2 - Method and apparatus for reducing axial compressor blade tip flow - Google Patents

Method and apparatus for reducing axial compressor blade tip flow Download PDF

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Publication number
EP1793089A2
EP1793089A2 EP06125091A EP06125091A EP1793089A2 EP 1793089 A2 EP1793089 A2 EP 1793089A2 EP 06125091 A EP06125091 A EP 06125091A EP 06125091 A EP06125091 A EP 06125091A EP 1793089 A2 EP1793089 A2 EP 1793089A2
Authority
EP
European Patent Office
Prior art keywords
airfoil
tip
channel
blade
air
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.)
Ceased
Application number
EP06125091A
Other languages
German (de)
French (fr)
Other versions
EP1793089A3 (en
Inventor
Zhifeng Dong
John Joseph Rahaim
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.)
General Electric Co
Original Assignee
General Electric Co
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 General Electric Co filed Critical General Electric Co
Publication of EP1793089A2 publication Critical patent/EP1793089A2/en
Publication of EP1793089A3 publication Critical patent/EP1793089A3/en
Ceased legal-status Critical Current

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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
    • F01D11/08—Preventing or minimising internal leakage of working-fluid, e.g. between stages for sealing space between rotor blade tips and stator
    • F01D11/10—Preventing or minimising internal leakage of working-fluid, e.g. between stages for sealing space between rotor blade tips and stator using sealing fluid, e.g. steam
    • 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
    • F04D29/66—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
    • 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
    • F04D29/684—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers especially adapted for elastic fluid pumps by fluid injection
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2240/00—Components
    • F05D2240/20—Rotors
    • F05D2240/30—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor
    • F05D2240/307—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor related to the tip of a rotor blade

Definitions

  • This invention relates to a method and apparatus for reducing axial compressor tip flow in airfoils, such as blades and vanes.
  • Blade tip flow in the compressor area of a turbine engine results in loss of compressor efficiency and stall margin.
  • flow recirculation in seal cavities along the inner flow path between the vanes and blades also degrades compressor performance.
  • One prior art solution for reducing tip flow is to reduce the blade tip clearance. This is done by a variety of means, including control of the casing and vane interface using mechanical and/or thermal methods. These methods can cause tip rubbing, excess wear and loss of engine efficiency.
  • a method of reducing air flow between a tip of a turbine airfoil rotating in a closely-spaced apart casing comprises the step of providing in the airfoil a radially-extending channel having an inlet opening proximate a base of the airfoil and an exit opening on the airfoil tip. Air is extracted and pressurized from a region proximate the base of the airfoil, introduced into the channel and conveyed through the channel to the airfoil tip. The air exits the channel through the exit openings in the airfoil tip into an area between the airfoil tip and casing under sufficient pressure to resist axial air flow from a pressure side to a suction side of the airfoil.
  • Another aspect of the invention provides a method of reducing air flow between a tip of a turbine airfoil rotating in a closely-spaced apart casing, comprising the steps of providing a first radially-extending channel having an inlet opening proximate a base of the airfoil on a leading edge side thereof, and an exit opening on the airfoil tip, and providing a second radially-extending channel having an inlet opening proximate the base of the airfoil on a trailing edge side thereof, and an exit opening on the airfoil tip.
  • the air is extracted from a region proximate the base of the airfoil into the channel and pumped through the channel to the airfoil tip.
  • the air exits the channel through the exit openings in the airfoil tip into an area between the airfoil tip and casing under sufficient pressure to resist axial air flow from a pressure side to a suction side of the airfoil.
  • a turbine machine compressor airfoil comprising a airfoil base, a airfoil tip, and an air flow channel extending radially from an air inlet opening in the airfoil proximate the airfoil base to an exit opening in the airfoil tip for providing a air blockage against an axial flow of air from the pressure side of the airfoil to the suction side of the airfoil to thereby reduce compressor airfoil tip flow.
  • FIG. 1 a partial section of the axial compressor section of a turbine engine T1 illustrating a method and apparatus for controlling axial compressor blade tip flow according to the present invention is illustrated in Figure 1.
  • the turbine engine “T1” includes compressor blades 10-14 and intermediately-positioned stator vanes 15-19 in a casing C1.
  • the compressor blades 10-14 include respective leading edges 10A-14A.
  • blade 10 is shown in enlarged detail for clarity, and is also exemplary of blades 11-14.
  • Air is extracted and pressurized from the area of the leading edge side 10A of the blade 10 through holes 10B in a disk 20.
  • the holes 10B communicate with a channel 10C that extends radially outwardly through the blade 10 to the tip where it exits through holes 10D.
  • the channel 10C may branch out before exiting the tip of the blade 10.
  • the size of the channel 10C and the location and number of the branches is determined empirically based on blade size, shape and volume, and engine performance, rating, tip clearance and similar factors. Note in the drawings that the tip clearance is sufficiently small in relation to the scale of the drawings that actual representation of the tip clearance cannot be shown.
  • a turbine engine “T2” includes compressor blades 30-34 and intermediately-positioned stator vanes 35-39 in a casing C2.
  • the compressor blades 30-34 include respective trailing edges 30A-34A.
  • blade 31 is shown in enlarged detail for clarity, and is exemplary of blades 30 and 32-34. Air is extracted from the area of the trailing edge side 31A of the blade 31 through holes 31B in the disk rim 40.
  • the holes 31B communicate with a channel 31C that extends radially outwardly through the blade 31 to the tip where it preferably branches before exiting through holes 31D.
  • a turbine engine “T3” includes compressor blades 50-54 and intermediately-positioned stator vanes 55-59 in a casing C3.
  • the compressor blades 50-54 include respective leading edges 50A-54A and respective trailing edges 50B-54B.
  • FIG. 6 illustrates a blade 52 that is shown in enlarged detail for clarity, and is exemplary of blades 51 and 52-54. Air is extracted from both the areas of the leading edge side 52A and trailing edge side 52B of blade 52 through holes 52C and 52D in the disk rim 60.
  • the holes 52C and 52D communicate with channels 52E and 52F, respectively, that extend radially outwardly through the blade 52 to the tip, where they preferably branch before exiting through holes 52G.
  • the air discharged at the blade tip reduces or prevents blade tip flow by aerodynamically blocking air flow in the region of the tip clearance between the blade tip and the casing. Air from the inner flow path is brought to the tip clearance, as described above, to form this air block. The pressure of the extracted air increases due to the compressor rotor pumping and, when exiting the blade at the tip, resists air flow across the blade tip from the pressure side to the suction side.
  • the methods described above can be applied to both low pressure compressors (boosters) and high pressure compressors. There is no chargeable flow loss when these methods are utilized. Furthermore, by reducing air flow by aerodynamic air blockage rather than by a tight running clearance between the blade tips and the casing, a larger assembly clearance between the blade tips and the casing can be established and maintained. Blade tip rubs are thus reduced, as is recirculation in the inner flow path between the vane and the blade. The extracted air is continuously pumped from the inner flow path to the blade tip, thus providing a continuous air blockage to the blade tip at all times during engine operation.
  • the methods described in this application also have application in blisk (blade integrated disk), skewed or circumferential dovetailed blades.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

A turbine machine (T1) of the type having a high pressure compressor positioned in a casing is provided with a plurality of rotating compressor blades (10-14) with at least one air channel (10C-14C) formed in the blades (10-14) for air flow communication from the base to the tip for extracting and pressurizing air from an inner area proximate the disk (20) and conveying the extracted and pressurized air into an area between the blade tip and casing (C1) for blocking air flow across the tips of the blades (10-14).

Description

  • This invention relates to a method and apparatus for reducing axial compressor tip flow in airfoils, such as blades and vanes. Blade tip flow in the compressor area of a turbine engine results in loss of compressor efficiency and stall margin. In addition, flow recirculation in seal cavities along the inner flow path between the vanes and blades also degrades compressor performance. One prior art solution for reducing tip flow is to reduce the blade tip clearance. This is done by a variety of means, including control of the casing and vane interface using mechanical and/or thermal methods. These methods can cause tip rubbing, excess wear and loss of engine efficiency.
  • According to one aspect of the invention, a method of reducing air flow between a tip of a turbine airfoil rotating in a closely-spaced apart casing is provided, and comprises the step of providing in the airfoil a radially-extending channel having an inlet opening proximate a base of the airfoil and an exit opening on the airfoil tip. Air is extracted and pressurized from a region proximate the base of the airfoil, introduced into the channel and conveyed through the channel to the airfoil tip. The air exits the channel through the exit openings in the airfoil tip into an area between the airfoil tip and casing under sufficient pressure to resist axial air flow from a pressure side to a suction side of the airfoil.
  • Another aspect of the invention provides a method of reducing air flow between a tip of a turbine airfoil rotating in a closely-spaced apart casing, comprising the steps of providing a first radially-extending channel having an inlet opening proximate a base of the airfoil on a leading edge side thereof, and an exit opening on the airfoil tip, and providing a second radially-extending channel having an inlet opening proximate the base of the airfoil on a trailing edge side thereof, and an exit opening on the airfoil tip. The air is extracted from a region proximate the base of the airfoil into the channel and pumped through the channel to the airfoil tip. The air exits the channel through the exit openings in the airfoil tip into an area between the airfoil tip and casing under sufficient pressure to resist axial air flow from a pressure side to a suction side of the airfoil.
  • In another aspect of the invention a turbine machine compressor airfoil is provided, comprising a airfoil base, a airfoil tip, and an air flow channel extending radially from an air inlet opening in the airfoil proximate the airfoil base to an exit opening in the airfoil tip for providing a air blockage against an axial flow of air from the pressure side of the airfoil to the suction side of the airfoil to thereby reduce compressor airfoil tip flow.
  • Various aspects and embodiments of the invention are described below in conjunction with the following drawings, in which:
    • Figure 1 is a fragmentary cross-section of an axial flow compressor section of a turbine engine illustrating one embodiment of the invention;
    • Figure 2 is an enlarged fragmentary cross-section of a portion of the compressor shown in Figure 1;
    • Figure 3 is a fragmentary cross-section of the compressor section of a turbine engine illustrating another embodiment of the invention;
    • Figure 4 is an enlarged fragmentary cross-section of a portion of the compressor shown in Figure 3;
    • Figure 5 is a fragmentary cross-section of the compressor section of a turbine engine illustrating yet another embodiment of the invention; and
    • Figure 6 is an enlarged fragmentary cross-section of a portion of the compressor shown in Figure 5.
  • Referring now specifically to the drawings, a partial section of the axial compressor section of a turbine engine T1 illustrating a method and apparatus for controlling axial compressor blade tip flow according to the present invention is illustrated in Figure 1. The turbine engine "T1" includes compressor blades 10-14 and intermediately-positioned stator vanes 15-19 in a casing C1. The compressor blades 10-14 include respective leading edges 10A-14A.
  • As is shown in Figure 2, blade 10 is shown in enlarged detail for clarity, and is also exemplary of blades 11-14. Air is extracted and pressurized from the area of the leading edge side 10A of the blade 10 through holes 10B in a disk 20. The holes 10B communicate with a channel 10C that extends radially outwardly through the blade 10 to the tip where it exits through holes 10D. Note that the channel 10C may branch out before exiting the tip of the blade 10. The size of the channel 10C and the location and number of the branches is determined empirically based on blade size, shape and volume, and engine performance, rating, tip clearance and similar factors. Note in the drawings that the tip clearance is sufficiently small in relation to the scale of the drawings that actual representation of the tip clearance cannot be shown.
  • Referring now to Figure 3, a turbine engine "T2" includes compressor blades 30-34 and intermediately-positioned stator vanes 35-39 in a casing C2. The compressor blades 30-34 include respective trailing edges 30A-34A.
  • In Figure 4, blade 31 is shown in enlarged detail for clarity, and is exemplary of blades 30 and 32-34. Air is extracted from the area of the trailing edge side 31A of the blade 31 through holes 31B in the disk rim 40. The holes 31B communicate with a channel 31C that extends radially outwardly through the blade 31 to the tip where it preferably branches before exiting through holes 31D.
  • Referring now to Figure 5, a turbine engine "T3" includes compressor blades 50-54 and intermediately-positioned stator vanes 55-59 in a casing C3. The compressor blades 50-54 include respective leading edges 50A-54A and respective trailing edges 50B-54B.
  • Figure 6 illustrates a blade 52 that is shown in enlarged detail for clarity, and is exemplary of blades 51 and 52-54. Air is extracted from both the areas of the leading edge side 52A and trailing edge side 52B of blade 52 through holes 52C and 52D in the disk rim 60. The holes 52C and 52D communicate with channels 52E and 52F, respectively, that extend radially outwardly through the blade 52 to the tip, where they preferably branch before exiting through holes 52G.
  • In each of the embodiments described above, the air discharged at the blade tip reduces or prevents blade tip flow by aerodynamically blocking air flow in the region of the tip clearance between the blade tip and the casing. Air from the inner flow path is brought to the tip clearance, as described above, to form this air block. The pressure of the extracted air increases due to the compressor rotor pumping and, when exiting the blade at the tip, resists air flow across the blade tip from the pressure side to the suction side.
  • The methods described above can be applied to both low pressure compressors (boosters) and high pressure compressors. There is no chargeable flow loss when these methods are utilized. Furthermore, by reducing air flow by aerodynamic air blockage rather than by a tight running clearance between the blade tips and the casing, a larger assembly clearance between the blade tips and the casing can be established and maintained. Blade tip rubs are thus reduced, as is recirculation in the inner flow path between the vane and the blade. The extracted air is continuously pumped from the inner flow path to the blade tip, thus providing a continuous air blockage to the blade tip at all times during engine operation.
  • The methods described in this application also have application in blisk (blade integrated disk), skewed or circumferential dovetailed blades.
  • A method and apparatus for controlling axial compressor blade tip flow is described above. Various details of the invention may be changed without departing from its scope. Furthermore, the foregoing description of the preferred embodiment of the invention and the best mode for practicing the invention are provided for the purpose of illustration only and not for the purpose of limitation--the invention being defined by the claims.
    • Parts List
  • T1 turbine machine
    T2 turbine machine
    T3 turbine machine
    C1 casing
    C3 casing
    10 blades
    10A leading edge
    10B inlet openings
    10C channel
    10D exit openings
    11 blades
    11C channel
    12 blades
    12C channel
    13 blades
    13C channel
    14 blades
    14C channel
    15 stationary vanes
    16 stationary vanes
    17 stationary vanes
    18 stationary vanes
    19 stationary vanes
    20 disk
    31 blade
    31A trailing edge
    31B inlet opening
    31C channel
    31D exit opening
    50 blade
    50A leading edge
    50B trailing edge
    50C inlet opening
    50D inlet opening
    50F channel
    52 blade
    52A leading edge
    52B trailing edge
    52C inlet opening
    52D inlet opening
    52E first channel
    52F second channel
    52G exit holes

Claims (10)

  1. A turbine machine (T1) of the type having a high pressure compressor positioned in a casing (C1), a plurality of rotating compressor blades (10-14) having respective blade tips, respective blade bases affixed to a central disk (20), and a plurality of stationary vanes (15-19) positioned between respective ones of the blades (10-14), comprising at least one air channel (10C, 11C, 12C, 13C, 14C) formed in respective ones of the blades (10-14) for air flow communication from the base to the tip for extracting and pressurizing air from an inner area proximate the disk (20) and conveying the extracted and pressurized air through the channel (10C, 11C, 12C, 13C, 14C) into an area between the blade tip and casing (C1) for blocking air flow from a tip of the blades (10-14).
  2. A turbine machine (T1) according to claim 1, wherein the channel (10C) exits the blade tip through a respective plurality of exit holes (10D).
  3. A turbine machine (T1) according to claim 1 or claim 2, wherein the channel (10C) includes an air inlet (10B) opening in on leading edge (10A) of the blade (10).
  4. A turbine machine (T2) according to any preceding claim, wherein the channel (31 C) includes an air inlet opening (31B) on a trailing edge (31A) side of the blade (31).
  5. A turbine machine (T3) according to any preceding claim, wherein the channel (50F) includes an air inlet opening (50C) in on a leading edge (50A) side and an air inlet opening (50D) on a trailing edge (50B) side of the blade (50).
  6. A turbine machine (T3) according to any preceding claim, and including a first channel (52E) having an air inlet opening (52C) on a leading edge (52A) side of the blade (52) and a second channel (52F) having an air inlet opening (52D) on a trailing edge (52B) side of the blade (52).
  7. A turbine machine (T1) according to any preceding claim, wherein the channel (50F) includes a plurality of exit holes (52G) in the blade tip.
  8. A method of reducing air flow between a tip of a turbine airfoil (10) rotating in a closely-spaced apart casing (C1), comprising the steps of:
    (a) providing in the airfoil (10) a radially-extending channel (10C) having an inlet opening (10B) proximate a base of the airfoil (10) and an exit opening (10D) on the airfoil tip;
    (b) extracting and pressurizing air from a region proximate the base of the airfoil (10) into the channel (10C);
    (c) conveying the air through the channel (10C) to the airfoil tip; and
    (d) discharging the air through the exit openings (10D) in the airfoil tip into an area between the airfoil tip and casing (C1) under sufficient pressure to resist axial air flow across the tip of the airfoil (10).
  9. A method according to claim 8, wherein the step of providing a radially-extending channel (10C) having an inlet opening (10B) proximate a base of the airfoil (10) and an exit opening (10D) on the airfoil tip includes the step of forming the inlet opening (10B) on a leading edge (10A) side of the airfoil (10).
  10. A method according to claim 8 or claim 9, wherein the step of providing a radially-extending channel (31C) having an inlet opening (31B) proximate a base of the airfoil (31) and an exit opening (31D) on the airfoil tip includes the step of forming the inlet opening (31B) on a trailing edge (31A) side of the blade (31).
EP06125091A 2005-11-30 2006-11-30 Method and apparatus for reducing axial compressor blade tip flow Ceased EP1793089A3 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US11/164,636 US20070122280A1 (en) 2005-11-30 2005-11-30 Method and apparatus for reducing axial compressor blade tip flow

Publications (2)

Publication Number Publication Date
EP1793089A2 true EP1793089A2 (en) 2007-06-06
EP1793089A3 EP1793089A3 (en) 2007-10-24

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EP06125091A Ceased EP1793089A3 (en) 2005-11-30 2006-11-30 Method and apparatus for reducing axial compressor blade tip flow

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US (1) US20070122280A1 (en)
EP (1) EP1793089A3 (en)
JP (1) JP2007154887A (en)
CN (1) CN101008402A (en)
CA (1) CA2569177A1 (en)

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GB2452297B (en) * 2007-08-30 2010-01-06 Rolls Royce Plc A compressor
CN102628452A (en) * 2012-03-21 2012-08-08 朱晓义 Air compressor and automobile engine
EP2250347B1 (en) * 2008-02-28 2017-11-29 MTU Aero Engines GmbH Axial compressor with a device for redirecting a leakage flow

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CN103925244B (en) * 2014-04-02 2017-03-15 清华大学 A kind of big flow high load axial compressor and fan for 300MW F level heavy duty gas turbines
JP6468532B2 (en) * 2015-04-27 2019-02-13 三菱日立パワーシステムズ株式会社 Compressor rotor, compressor, and gas turbine

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EP0278434A2 (en) 1987-02-06 1988-08-17 Wolfgang P. Weinhold A blade, especially a rotor blade
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Cited By (4)

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Publication number Priority date Publication date Assignee Title
GB2452297B (en) * 2007-08-30 2010-01-06 Rolls Royce Plc A compressor
EP2250347B1 (en) * 2008-02-28 2017-11-29 MTU Aero Engines GmbH Axial compressor with a device for redirecting a leakage flow
CN102628452A (en) * 2012-03-21 2012-08-08 朱晓义 Air compressor and automobile engine
CN102628452B (en) * 2012-03-21 2014-07-16 朱晓义 Air compressor and automobile engine

Also Published As

Publication number Publication date
CN101008402A (en) 2007-08-01
JP2007154887A (en) 2007-06-21
EP1793089A3 (en) 2007-10-24
CA2569177A1 (en) 2007-05-30
US20070122280A1 (en) 2007-05-31

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