US3493169A - Bleed for compressor - Google Patents

Bleed for compressor Download PDF

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Publication number
US3493169A
US3493169A US733871A US3493169DA US3493169A US 3493169 A US3493169 A US 3493169A US 733871 A US733871 A US 733871A US 3493169D A US3493169D A US 3493169DA US 3493169 A US3493169 A US 3493169A
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US
United States
Prior art keywords
rotor
passages
compressor
bleed
axial
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.)
Expired - Lifetime
Application number
US733871A
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English (en)
Inventor
Robert N Abild
Charles B Mayer
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.)
RTX Corp
Original Assignee
United Aircraft Corp
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 United Aircraft Corp filed Critical United Aircraft Corp
Application granted granted Critical
Publication of US3493169A publication Critical patent/US3493169A/en
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/02—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps having non-centrifugal stages, e.g. centripetal
    • F04D17/025—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps having non-centrifugal stages, e.g. centripetal comprising axial flow and radial flow stages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
    • F02C6/04—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output
    • F02C6/06—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output providing compressed gas
    • F02C6/08—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output providing compressed gas the gas being bled from the gas-turbine compressor
    • 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
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/284—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/02—Surge control
    • F04D27/0207—Surge control by bleeding, bypassing or recycling fluids
    • F04D27/0215—Arrangements therefor, e.g. bleed or by-pass valves
    • 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
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/32—Rotors specially for elastic fluids for axial flow pumps
    • F04D29/321—Rotors specially for elastic fluids for axial flow pumps for axial flow compressors

Definitions

  • a feature of the invention is the -bleeding olf of air or other gas from the centrifugal last stage of a multistage compressor through axial passages in the centrifugal rotor located at the point where the rotor turns the flow from axial toward radial ow, thereby to develop the total pressure available in the fluid being compressed at this point.
  • the centrifugal compressor rotor has axially extending, forwardly open passages therein to receive a part of the axially flowing compressible fluid in the compressor, these passages being located at a point where the rotor begins to impart a radial ilow to the gaseous Huid.
  • the dynamic pressure of the fluid is converted into static pressure within these passages for an effectively higher total pressure.
  • Suitably arranged passages in the rotor direct the gaseous fluid to a plenum chamber adjacent to or surrounded by the rotor.
  • the single gure is a longitudinal sectional view through the compressor.
  • the compressor shown has a casing 2 with a number of rows of axial flow stator vanes 4 projecting inwardly therefrom and alternating with rows of blades 6 on the rotor 8-. Gaseous fluid entering the inlet 10 is compressed by these alternating blades and vanes and is discharged in an axial direction into the last or centrifugal stage 12.
  • This stage includes a rotor 14 having a curved surface 16 that is substantially axial at the inlet and merges to a radial surface at the outlet. This surface has a plurality of vanes 18 projecting therefrom toward a cooperating curved surface 20 on the casing. From the rotor 14 the fluid being compressed is discharged through a diffuser 22.
  • the rotor is supported in spaced bearings 24 and 26.
  • the bearing 24 is supported through a series of struts 28 and a support disk and the bearing 26 is located at the inner perphery of a support 32 extending inwardly from the casing at the diffuser 22.
  • a seal ring 34 on the rotor and a cooperating ring 36 on the support 32 define a chamber 38 communicating through ports 40 in the rotor with a second chamber 42 within the rotor.
  • the centrifugal rotor has axially extending passages 44 located. at a point where the curved surface 16 has begun to approach a radial direction and open forwardly in such a way that a part of the gaseous uid moving in an axial direction from the last row of stator vanes 4 will enter these passages thereby providing at this point a total pressure that is the sum of the static pressure in this part of the compressor and the dynamic or velocity pressure resulting from the axial motion of the fluid.
  • intersecting radial passages 46 guide the bleed fluid radially inward to the chamber 42 and thence to chamber 38. From these chambers the bleed fluid is utilized as desired either in being circulated to the turbine which drives the compressor for cooling the vanes or blades of the turbne, or for any other particular use 'for which the gaseous fluid is adapted.
  • the centrifugal stage is just beginning its compression function during which the temperature of the fluid is substantially increased as a result of the compressing operation.
  • the bleed passages above described are located to bleed the fluid at a point where the pressure is relatively high but before the fluid is heated too much by the compressing function of the centrifugal stage.
  • the centrifugal rotor 14 may be ⁇ made in the form of two disks 14a and 14h, the former having the inlet portion of the rotor and the latter having the outlet portion.
  • the radial passages 46 are formed in one or both of the mating surfaces of these disks, being located in the specific arrangement in disk 14b. In this way the passages 46 may terminate at the intersection with passages 44 and need not break through radially into the curved surface 16. Suitable bolts, not shown, may hold the disks together or they may otherwise be secured together after the formation of the passages therein.
  • a multistage compressor having at least one axial ilow entry stage defining an annular axial flow path and a final centrifugal stage, said compressor comprising a rotor having at least one row of axial flow blading and a centrifugal rotor having an arcuate surface downstream of the axial blading, a stator having at least one axial stage of stator vanes and an arcuate wall downstream thereof cooperting with the centrifugal rotor, said centrifugal stage changing the flow of gas being compressed from an axial direction to a substantially radial direction, and bleed passages in said centrifugal rotor having the inlet ends thereof extending substantially axially of the rotor and terminating at said arcuate surface at a point where the arcuate wall extends substantially axially and forms an extension of the inner wall of the axial flow path and where the gas flow is substantially axial from the axial stage whereby the gas enters the bleed passage with no significant change in the direction of ow.
  • centrifugal rotor is made up of two mating discs in one of which the axially extending bleed passages are formed, and in the mating surfaces of which radial passages are formed to intersect at their outer ends with the axially extending bleed passages.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US733871A 1968-06-03 1968-06-03 Bleed for compressor Expired - Lifetime US3493169A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US73387168A 1968-06-03 1968-06-03

Publications (1)

Publication Number Publication Date
US3493169A true US3493169A (en) 1970-02-03

Family

ID=24949451

Family Applications (1)

Application Number Title Priority Date Filing Date
US733871A Expired - Lifetime US3493169A (en) 1968-06-03 1968-06-03 Bleed for compressor

Country Status (4)

Country Link
US (1) US3493169A (enrdf_load_stackoverflow)
DE (1) DE1926423A1 (enrdf_load_stackoverflow)
FR (1) FR2010030A1 (enrdf_load_stackoverflow)
GB (1) GB1239196A (enrdf_load_stackoverflow)

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3775023A (en) * 1971-02-17 1973-11-27 Teledyne Ind Multistage axial flow compressor
US4503668A (en) * 1983-04-12 1985-03-12 The United States Of America As Represented By The Secretary Of The Air Force Strutless diffuser for gas turbine engine
US4687412A (en) * 1985-07-03 1987-08-18 Pratt & Whitney Canada Inc. Impeller shroud
US4979587A (en) * 1989-08-01 1990-12-25 The Boeing Company Jet engine noise suppressor
US5253472A (en) * 1990-02-28 1993-10-19 Dev Sudarshan P Small gas turbine having enhanced fuel economy
US5832715A (en) * 1990-02-28 1998-11-10 Dev; Sudarshan Paul Small gas turbine engine having enhanced fuel economy
US20120036865A1 (en) * 2009-04-06 2012-02-16 Turbomeca Air bleed having an inertial filter in the tandem rotor of a compressor
US8307943B2 (en) 2010-07-29 2012-11-13 General Electric Company High pressure drop muffling system
US8430202B1 (en) 2011-12-28 2013-04-30 General Electric Company Compact high-pressure exhaust muffling devices
US8511096B1 (en) 2012-04-17 2013-08-20 General Electric Company High bleed flow muffling system
US8550208B1 (en) 2012-04-23 2013-10-08 General Electric Company High pressure muffling devices
US9399951B2 (en) 2012-04-17 2016-07-26 General Electric Company Modular louver system

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2700739A1 (de) * 1977-01-10 1978-07-13 Schumacher Ii Verteil- und glaettwerkzeug fuer maurer, verputzer und maler
FR2491549B1 (fr) * 1980-10-08 1985-07-05 Snecma Dispositif de refroidissement d'une turbine a gaz, par prelevement d'air au niveau du compresseur
DE19840034C2 (de) * 1998-09-02 2002-06-13 Rw Ruedel Werner Patentverwert Reibebrett mit Wechselsohle

Citations (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE276593C (enrdf_load_stackoverflow) *
US1151964A (en) * 1913-08-12 1915-08-31 Laval Steam Turbine Co Balancing of centrifugal pumps.
US1323412A (en) * 1919-12-02 schorr
US1473802A (en) * 1921-10-26 1923-11-13 Superior Mfg Company Centrifugal pump with self-centering runner
FR643177A (fr) * 1926-10-28 1928-09-11 Procédé et appareil pour l'élévation de la puissance d'aspiration dans les pompes rotatives
DE518179C (de) * 1929-09-20 1931-02-12 Hans Reinecke Entlastung der innerhalb der rueckseitigen Dichtungsringe der Laufraeder umlaufenderhydraulischer Maschinen befindlichen Raeume
US1871747A (en) * 1929-07-05 1932-08-16 Dempster Mill Mfg Company Impeller for centrifugal pumps
US2283176A (en) * 1937-11-29 1942-05-19 Turbo Engineering Corp Elastic fluid mechanism
GB619722A (en) * 1946-12-20 1949-03-14 English Electric Co Ltd Improvements in and relating to boundary layer control in fluid conduits
US2620123A (en) * 1946-05-31 1952-12-02 Continental Aviat & Engineerin Cooling system for combustion gas turbines
US2682991A (en) * 1949-02-04 1954-07-06 English Electric Co Ltd Gas turbine
US2709567A (en) * 1948-12-27 1955-05-31 Garrett Corp Turbine rotor bearing with cooling and lubricating means
US2709893A (en) * 1949-08-06 1955-06-07 Laval Steam Turbine Co Gas turbine power plant with heat exchanger and cooling means
US3104092A (en) * 1961-07-06 1963-09-17 United Aircraft Corp Compressor rotor construction

Patent Citations (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE276593C (enrdf_load_stackoverflow) *
US1323412A (en) * 1919-12-02 schorr
US1151964A (en) * 1913-08-12 1915-08-31 Laval Steam Turbine Co Balancing of centrifugal pumps.
US1473802A (en) * 1921-10-26 1923-11-13 Superior Mfg Company Centrifugal pump with self-centering runner
FR643177A (fr) * 1926-10-28 1928-09-11 Procédé et appareil pour l'élévation de la puissance d'aspiration dans les pompes rotatives
US1871747A (en) * 1929-07-05 1932-08-16 Dempster Mill Mfg Company Impeller for centrifugal pumps
DE518179C (de) * 1929-09-20 1931-02-12 Hans Reinecke Entlastung der innerhalb der rueckseitigen Dichtungsringe der Laufraeder umlaufenderhydraulischer Maschinen befindlichen Raeume
US2283176A (en) * 1937-11-29 1942-05-19 Turbo Engineering Corp Elastic fluid mechanism
US2620123A (en) * 1946-05-31 1952-12-02 Continental Aviat & Engineerin Cooling system for combustion gas turbines
GB619722A (en) * 1946-12-20 1949-03-14 English Electric Co Ltd Improvements in and relating to boundary layer control in fluid conduits
US2709567A (en) * 1948-12-27 1955-05-31 Garrett Corp Turbine rotor bearing with cooling and lubricating means
US2682991A (en) * 1949-02-04 1954-07-06 English Electric Co Ltd Gas turbine
US2709893A (en) * 1949-08-06 1955-06-07 Laval Steam Turbine Co Gas turbine power plant with heat exchanger and cooling means
US3104092A (en) * 1961-07-06 1963-09-17 United Aircraft Corp Compressor rotor construction

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3775023A (en) * 1971-02-17 1973-11-27 Teledyne Ind Multistage axial flow compressor
US4503668A (en) * 1983-04-12 1985-03-12 The United States Of America As Represented By The Secretary Of The Air Force Strutless diffuser for gas turbine engine
US4687412A (en) * 1985-07-03 1987-08-18 Pratt & Whitney Canada Inc. Impeller shroud
US4979587A (en) * 1989-08-01 1990-12-25 The Boeing Company Jet engine noise suppressor
US6047540A (en) * 1990-02-28 2000-04-11 Dev; Sudarshan Paul Small gas turbine engine having enhanced fuel economy
US5832715A (en) * 1990-02-28 1998-11-10 Dev; Sudarshan Paul Small gas turbine engine having enhanced fuel economy
US5253472A (en) * 1990-02-28 1993-10-19 Dev Sudarshan P Small gas turbine having enhanced fuel economy
US20120036865A1 (en) * 2009-04-06 2012-02-16 Turbomeca Air bleed having an inertial filter in the tandem rotor of a compressor
JP2012522938A (ja) * 2009-04-06 2012-09-27 ターボメカ 圧縮機のタンデムロータに内部フィルタを有する抽気
US9611862B2 (en) * 2009-04-06 2017-04-04 Turbomeca Air bleed having an inertial filter in the tandem rotor of a compressor
US8307943B2 (en) 2010-07-29 2012-11-13 General Electric Company High pressure drop muffling system
US8430202B1 (en) 2011-12-28 2013-04-30 General Electric Company Compact high-pressure exhaust muffling devices
US8511096B1 (en) 2012-04-17 2013-08-20 General Electric Company High bleed flow muffling system
US9399951B2 (en) 2012-04-17 2016-07-26 General Electric Company Modular louver system
US8550208B1 (en) 2012-04-23 2013-10-08 General Electric Company High pressure muffling devices

Also Published As

Publication number Publication date
DE1926423A1 (de) 1969-12-11
FR2010030A1 (enrdf_load_stackoverflow) 1970-02-13
GB1239196A (enrdf_load_stackoverflow) 1971-07-14

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