US20090238677A1 - Centrifugal compressor with air extraction and return at the casing - Google Patents

Centrifugal compressor with air extraction and return at the casing Download PDF

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Publication number
US20090238677A1
US20090238677A1 US12/320,113 US32011309A US2009238677A1 US 20090238677 A1 US20090238677 A1 US 20090238677A1 US 32011309 A US32011309 A US 32011309A US 2009238677 A1 US2009238677 A1 US 2009238677A1
Authority
US
United States
Prior art keywords
centrifugal compressor
casing
rotor
extraction
flow
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.)
Abandoned
Application number
US12/320,113
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English (en)
Inventor
Carsten Clemen
Volker Guemmer
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
Assigned to ROLLS-ROYCE DEUTSCHLAND LTD & CO KG reassignment ROLLS-ROYCE DEUTSCHLAND LTD & CO KG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: CLEMEN, CARSTEN, GUEMMER, VOLKER
Publication of US20090238677A1 publication Critical patent/US20090238677A1/en
Abandoned 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
    • F04D29/66—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
    • 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
    • F04D27/023—Details or means for fluid extraction
    • 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
    • F04D27/0238—Details or means for fluid reinjection
    • 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
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/4213—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps suction ports
    • 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
    • F04D29/682—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers especially adapted for elastic fluid pumps by fluid extraction

Definitions

  • the present invention relates to a centrifugal compressor with a rotor which is rotatably borne in a casing.
  • Centrifugal compressors are known from the state of the art, for example from specification U.S. Pat. No. 3,643,675.
  • centrifugal compressors While centrifugal compressors are capable of producing very high pressure ratios, they have the disadvantage that their efficiency is inferior to that of axial-flow compressors with the same pressure ratio. This is, among others, due to the fact that the rotor gap between rotor and casing ( FIG. 2 ) in relation to the blade height is very large as it must be capable, among others, of taking up the axial movement of the rotor to avoid contact between rotor and casing. The larger the rotor gap, the larger the gap losses and the lower the efficiency. Furthermore, the rotor gap limits the surge limit of the compressor, and the maximum obtainable pressure ratio of the compressor and the high-loss gap flow lead to blockage near the casing, inhomogeneity of the flow into the diffuser and an increase in diffuser losses.
  • centrifugal compressor of the type specified at the beginning which, while being simply designed and featuring high efficiency, can be manufactured easily and cost-effectively and avoids the disadvantages of the state of the art.
  • FIG. 1 (Prior Art) is a schematic sketch of a known centrifugal compressor
  • FIG. 2 (Prior Art) is a schematic sketch of a known centrifugal compressor rotor
  • FIG. 3 shows a centrifugal compressor rotor with exhaustion (extraction) in accordance with the present invention
  • FIG. 4 shows a centrifugal compressor rotor with injection in accordance with the present invention
  • FIG. 5 shows a coupling of exhaustion (extraction) and injection in accordance with the present invention
  • FIG. 6 shows a coupling of exhaustion and injection with intermediate cooling in accordance with the present invention
  • FIG. 7 is a representation of exhaustion (extraction) behind the rotor (side view/view from top),
  • FIG. 8 shows exhaustion (extraction) above the rotor (side view/view from top),
  • FIG. 9 shows throttling in the return line in accordance with the present invention.
  • FIG. 10 shows injection before the rotor (side view/view from top) in accordance with the present invention.
  • FIG. 11 shows an injection geometry for smooth and stepped casing wall in accordance with the present invention.
  • FIGS. 1 and 2 show a schematic sketch of a centrifugal compressor ( FIG. 1 ) and a centrifugal compressor rotor ( FIG. 2 ) in accordance with the state of the art.
  • a rotor 2 which has a rotor tip/rotor leading edge 3 and is approached by an axial flow 4 , is rotatably borne in a casing 1 .
  • a diffuser 10 which is adjacent to a rotor trailing edge 12 , is arranged downstream of the rotor 2 .
  • the rotor has a rotor gap 11 .
  • FIGS. 3 to 11 show variants according to the present invention.
  • FIG. 3 shows a centrifugal compressor rotor with exhaustion (extraction), with possible extraction positions/ports (exhaustion positions) being indicated by reference numeral 13 .
  • FIG. 4 shows a centrifugal compressor rotor with injection at possible injection positions/ports 14 .
  • FIG. 5 shows a coupling of exhaustion (extraction) and injection by a line 5 going from an extraction position/port 16 (tapping point) to an injection point/port 15 .
  • FIG. 6 shows a variant with coupling of exhaustion (extraction) and injection with intermediate cooling, with the line 5 being routed through a cold airflow 9 of a bypass duct 8 , thereby acting as a heat exchanger and being cooled.
  • FIG. 7 shows exhaustion (extraction) behind the rotor 2 with extraction position or tapping point 16 , respectively.
  • the right-hand side of FIG. 7 schematically shows exhaustion (extraction) by means of circumferential slots 6 or discrete holes (cutouts 7 ) which can be differently dimensioned and designed.
  • FIG. 8 shows exhaustion (extraction) above the rotor 2 , analogically to FIG. 7 , with extraction positions /tapping points 16 which can be provided in the rotor passage as discrete holes (cutouts 7 ) which, again, can be differently dimensioned, geometrized and disposed.
  • FIG. 9 shows an example with throttling in the return line 5 by a controllable shutoff element (valve) 19 .
  • valve controllable shutoff element
  • Introduction of the fluid flow is via a throat area (throttle 20 ).
  • FIG. 10 shows examples of injection before the rotor 2 in which, again, circumferential slots 6 or discrete injection cutouts/holes 7 can be provided which can be differently disposed, dimensioned and geometrized.
  • FIG. 11 shows an injection geometry for both a smooth and stepped casing wall.
  • the left-hand representation of FIG. 11 shows a smooth casing wall 17 with injection of the fluid flow, while the right-hand representation of FIG. 11 shows a stepped casing wall.
  • Tapping (extraction) and injection of the flow according to the present invention can, in detail, take the forms described in FIGS. 3 to 11 .
  • Tapping (extraction) of the flow is, in accordance with the present invention, accomplished on the rotor casing 1 at any axial position either above the rotor 2 or behind the rotor ( FIG. 3 ).
  • Tapping (extraction) can, in accordance with the present invention, be accomplished behind the rotor 2 either from a circumferential slot 6 of any size and form or from discrete holes 7 of any shape, number and size in the casing 1 ( FIG. 7 ).
  • Tapping (extraction) above the rotor 2 can, in accordance with the present invention, be accomplished from discrete holes (cutouts 7 ) of any number, shape, size and position ( FIG. 8 ).
  • the air can, in accordance with the present invention, be guided from the tapping points (extraction points) to the injection points at any angle to the casing wall using suitable lines, pipes and/or hoses 5 . While a valve 19 can here be used for flow control, the mass flow is also controllable by means of a throttle 20 of a defined throat area ( FIG. 9 ).
  • Injection of the flow can, in accordance with the present invention, be accomplished on the casing 1 before the rotor tip 3 .
  • the distance to the rotor tip 3 shall here be kept as small as possible.
  • Injection can, in accordance with the present invention, be accomplished through a circumferential slot 6 or through discrete circumferential slots or discrete nozzles of any shape, number and size ( FIG. 10 ).
  • the injection slots/nozzles shall be adapted such to the casing 1 that minimum segregation of the flow lines occurs and the injected flow hits the rotor gap 11 only. This is achievable either by adaptation of the geometry to the smooth casing wall 17 , in that the injection geometry is inclined at a shallow angle ( FIG. 11 ), or by a step in the casing wall 18 to which the injection geometry is connected at an, again shallow, exit angle ( FIG. 11 ).
  • the present invention is advantageous in that the efficiency and stability of the centrifugal compressor are increased to such an extent that they come close to those of an axial-flow compressor, making the centrifugal compressor according to the present invention particularly suitable for application in aircraft engines by trading upon its advantages of less cost and less complexity.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US12/320,113 2008-01-17 2009-01-16 Centrifugal compressor with air extraction and return at the casing Abandoned US20090238677A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008004834A DE102008004834A1 (de) 2008-01-17 2008-01-17 Radialverdichter mit Abnahme und Rückführung von Luft am Gehäuse
DEDE102008004834.8 2008-01-17

Publications (1)

Publication Number Publication Date
US20090238677A1 true US20090238677A1 (en) 2009-09-24

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Application Number Title Priority Date Filing Date
US12/320,113 Abandoned US20090238677A1 (en) 2008-01-17 2009-01-16 Centrifugal compressor with air extraction and return at the casing

Country Status (3)

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US (1) US20090238677A1 (de)
EP (1) EP2080908A3 (de)
DE (1) DE102008004834A1 (de)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20170114797A1 (en) * 2015-10-27 2017-04-27 Pratt & Whitney Canada Corp. Diffuser pipe with splitter vane
US20180135525A1 (en) * 2016-11-14 2018-05-17 Pratt & Whitney Canada Corp. Gas turbine engine tangential orifice bleed configuration
US10539073B2 (en) * 2017-03-20 2020-01-21 Chester L Richards, Jr. Centrifugal gas compressor
US10648403B2 (en) 2015-06-18 2020-05-12 Bayerische Motoren Werke Aktiengesellschaft Turbocharger for a motor vehicle
US20200332717A1 (en) * 2019-04-17 2020-10-22 General Electric Company Refreshing Heat Management Fluid in a Turbomachine

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2951440B1 (de) 2013-01-31 2019-07-31 Danfoss A/S Kreiselverdichter mit erweitertem arbeitsbereich
WO2017135949A1 (en) 2016-02-04 2017-08-10 Danfoss A/S Active surge control in centrifugal compressors using microjet injection

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3643675A (en) * 1970-01-02 1972-02-22 Lennart Wetterstad Method and device for providing a control of the velocity profile of the working medium in the inlet of flow medium
US20060104805A1 (en) * 2004-06-24 2006-05-18 Volker Gummer Turbomachine with means for the creation of a peripheral jet on the stator
US7364404B2 (en) * 2003-11-26 2008-04-29 Rolls-Royce Deutschland Ltd & Co Kg Turbomachine with fluid removal
US7387487B2 (en) * 2003-11-26 2008-06-17 Rolls-Royce Deutschland Ltd & Co Kg Turbomachine with fluid supply

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB635270A (en) * 1946-01-04 1950-04-05 Rateau Soc Improvements in or relating to centrifugal pumps and compressors
CH404069A (de) * 1962-06-29 1965-12-15 Licentia Gmbh Strömungskanal, insbesondere Arbeitsmittelströmungskanal eines Turbokompressors
US3901620A (en) * 1973-10-23 1975-08-26 Howell Instruments Method and apparatus for compressor surge control
JPH09310699A (ja) * 1996-05-21 1997-12-02 Ishikawajima Harima Heavy Ind Co Ltd 遠心圧縮機
DE19823274C1 (de) * 1998-05-26 1999-10-14 Daimler Chrysler Ag Abgasturbolader für eine Brennkraftmaschine
JP4100030B2 (ja) * 2002-04-18 2008-06-11 株式会社Ｉｈｉ 遠心圧縮機
US7025557B2 (en) * 2004-01-14 2006-04-11 Concepts Eti, Inc. Secondary flow control system
DE602004015337D1 (de) * 2004-06-07 2008-09-04 Honeywell Int Inc Verdichter mit rückführung und verfahren

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3643675A (en) * 1970-01-02 1972-02-22 Lennart Wetterstad Method and device for providing a control of the velocity profile of the working medium in the inlet of flow medium
US7364404B2 (en) * 2003-11-26 2008-04-29 Rolls-Royce Deutschland Ltd & Co Kg Turbomachine with fluid removal
US7387487B2 (en) * 2003-11-26 2008-06-17 Rolls-Royce Deutschland Ltd & Co Kg Turbomachine with fluid supply
US20060104805A1 (en) * 2004-06-24 2006-05-18 Volker Gummer Turbomachine with means for the creation of a peripheral jet on the stator

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10648403B2 (en) 2015-06-18 2020-05-12 Bayerische Motoren Werke Aktiengesellschaft Turbocharger for a motor vehicle
US20170114797A1 (en) * 2015-10-27 2017-04-27 Pratt & Whitney Canada Corp. Diffuser pipe with splitter vane
US10570925B2 (en) * 2015-10-27 2020-02-25 Pratt & Whitney Canada Corp. Diffuser pipe with splitter vane
US11215196B2 (en) 2015-10-27 2022-01-04 Pratt & Whitney Canada Corp. Diffuser pipe with splitter vane
US20180135525A1 (en) * 2016-11-14 2018-05-17 Pratt & Whitney Canada Corp. Gas turbine engine tangential orifice bleed configuration
US10539073B2 (en) * 2017-03-20 2020-01-21 Chester L Richards, Jr. Centrifugal gas compressor
US20200332717A1 (en) * 2019-04-17 2020-10-22 General Electric Company Refreshing Heat Management Fluid in a Turbomachine
US10927761B2 (en) * 2019-04-17 2021-02-23 General Electric Company Refreshing heat management fluid in a turbomachine
US11230972B2 (en) 2019-04-17 2022-01-25 General Electric Company Refreshing heat management fluid in a turbomachine

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Publication number Publication date
EP2080908A3 (de) 2011-07-13
EP2080908A2 (de) 2009-07-22
DE102008004834A1 (de) 2009-07-23

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Owner name: ROLLS-ROYCE DEUTSCHLAND LTD & CO KG, GERMANY

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:CLEMEN, CARSTEN;GUEMMER, VOLKER;REEL/FRAME:022540/0236;SIGNING DATES FROM 20090312 TO 20090313

STCB Information on status: application discontinuation

Free format text: EXPRESSLY ABANDONED -- DURING EXAMINATION