EP2080908A2 - Compresseur radial doté d'une diminution et d'une récupération d'air sur le boîtier - Google Patents

Compresseur radial doté d'une diminution et d'une récupération d'air sur le boîtier Download PDF

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Publication number
EP2080908A2
EP2080908A2 EP09000446A EP09000446A EP2080908A2 EP 2080908 A2 EP2080908 A2 EP 2080908A2 EP 09000446 A EP09000446 A EP 09000446A EP 09000446 A EP09000446 A EP 09000446A EP 2080908 A2 EP2080908 A2 EP 2080908A2
Authority
EP
European Patent Office
Prior art keywords
rotor
radial compressor
housing
compressor according
injection
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Withdrawn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
EP09000446A
Other languages
German (de)
English (en)
Other versions
EP2080908A3 (fr
Inventor
Carsten Clemen
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 EP2080908A2 publication Critical patent/EP2080908A2/fr
Publication of EP2080908A3 publication Critical patent/EP2080908A3/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Withdrawn legal-status Critical Current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
    • F04D29/66—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 invention relates to a centrifugal compressor with a rotatably mounted in a housing rotor.
  • radial compressors are able to deliver very high pressure ratios, they have the disadvantage that they have a lower efficiency than an axial compressor with the same pressure ratio. This is due to the fact that the rotor gap between rotor and housing ( Fig. 2 ), based on the blade height, is very large, since it must compensate, inter alia, the axial movement of the rotor in order to exclude contact between the rotor and the housing. The larger the rotor gap, the larger the gap losses and the lower the efficiency. In addition, the rotor gap limits the surge limit of the compressor and its maximum achievable pressure ratio and the lossy gap flow lead to a blockage near the housing, an inhomogeneous flow into the diffuser and increased diffuser losses.
  • the invention has for its object to provide a centrifugal compressor of the type mentioned, which avoids the disadvantages of the prior art with a simple structure and simple, cost-effective manufacturability and has a high efficiency.
  • Fig. 1 and 2 show in accordance with the prior art a schematic diagram of a radial compressor ( Fig. 1 ) and a radial compressor rotor ( Fig. 2 ).
  • a rotor 2 is rotatably mounted in a housing 1, which has a rotor tip / rotor leading edge 3 and is flown by an axial flow 4.
  • a diffuser 10 is provided, which adjoins a rotor trailing edge 12.
  • the rotor has a rotor gap 11.
  • the Fig. 3-11 show inventive design variants. It shows the Fig. 3 a radial compressor rotor with suction (discharge), wherein possible discharge positions (suction positions) are provided with the reference numeral 13. In Fig. 4 a centrifugal compressor rotor with injection at possible injection positions 14 is shown. The Fig. 5 shows a coupling of the suction (discharge) and injection by means of a line 5, which leads from a discharge position 16 (tapping point) to a Einblasstelle 15.
  • the Fig. 6 shows an embodiment variant with a coupling of the suction (discharge) and the injection with intermediate cooling, wherein the conduit 5 is passed through a cold air flow 9 of a bypass channel 8 and thereby cooled.
  • the Fig. 7 shows a suction (discharge) behind the rotor 2 with discharge position or tapping point 16.
  • the right side of the Fig. 7 shows in a schematic representation of the suction (derivative) by means of circumferential slots 6 or discrete holes (Recesses 7), which can be differently dimensioned and configured.
  • the Fig. 8 shows the suction (derivative) on the rotor 2, analog Fig. 7 , with discharge positions / taps 16, which may be in the form of discrete holes in the rotor passage (recesses 7), which may also be of different dimensions, geometrically designed and arranged.
  • the Fig. 9 shows an embodiment with a restriction in the return line 5 by means of a controllable shut-off valve.
  • throttle 20 The introduction of the fluid flow takes place over a narrowest cross section (throttle 20).
  • Fig. 10 shows embodiments of the injection in front of the rotor 2, wherein here also circumferential slots 6 or discrete Einblasaus Principle / holes 7 may be provided, which may be arranged differently, dimensioned and geometrically designed.
  • the Fig. 11 shows a Einblasegeometrie with smooth and stepped housing wall.
  • the left illustration of the Fig. 11 shows a smooth housing wall 17 with insufflation of the fluid flow, while the right-hand illustration of Fig. 11 a stepped housing wall 18 represents.
  • the flow decrease (derivative) is carried out according to the invention on the rotor housing 1 at any axial position either above the rotor 2 or behind the rotor ( Fig. 3 ).
  • the decrease (derivative) can according to the invention behind the rotor 2 either from a circumferential slot 6 of any size and shape or from discrete holes 7 in the housing 1 of any shape, number and size ( Fig. 7 ).
  • the decrease (derivative) over the rotor 2 can according to the invention consist of discrete holes (recesses 7) of any number, shape, size and position ( Fig. 8 ).
  • the guidance of the air from the delivery points (discharge points) to the injection points can be realized according to the invention at any angle to the housing wall with suitable lines, pipes and / or hoses 5.
  • a valve 19 can be used to regulate the flow, but the mass flow can also be effected by throttling 20 with the aid of a defined, narrowest flow cross-section ( Fig. 9 ).
  • the blowing of the flow can take place on the housing 1 in front of the rotor tip 3.
  • the distance to the rotor tip 3 is preferably to be chosen as small as possible.
  • the injection can be effected by a peripheral slot 6 or by discrete circumferential slots or discrete nozzles whose shape, number and size can be arbitrary ( Fig. 10 ).
  • the injection slots / nozzles are to be adapted to the housing 1 so that the smallest possible fanning of the streamlines arises and the injected flow only hits the rotor gap 11.
  • This can be achieved either by adaptation of the geometry to the smooth housing wall 17, in which the Einblasegeometrie is inclined at a shallow angle ( Fig. 11 ), or through a step in the housing wall 18, to which the Einblasegeometrie is also connected with a flat exit angle ( Fig. 11 ).
  • the invention has the advantage that the radial compressor efficiency and the stability are increased so that they approach that of an axial compressor and thus the radial compressor according to the invention is particularly suitable for use in aircraft engines, since it has its advantages in terms of low cost and low complexity over the Axial compressor can deploy.

Landscapes

  • 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)
EP09000446A 2008-01-17 2009-01-14 Compresseur radial doté d'une diminution et d'une récupération d'air sur le boîtier Withdrawn EP2080908A3 (fr)

Applications Claiming Priority (1)

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

Publications (2)

Publication Number Publication Date
EP2080908A2 true EP2080908A2 (fr) 2009-07-22
EP2080908A3 EP2080908A3 (fr) 2011-07-13

Family

ID=40445875

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09000446A Withdrawn EP2080908A3 (fr) 2008-01-17 2009-01-14 Compresseur radial doté d'une diminution et d'une récupération d'air sur le boîtier

Country Status (3)

Country Link
US (1) US20090238677A1 (fr)
EP (1) EP2080908A3 (fr)
DE (1) DE102008004834A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9157446B2 (en) 2013-01-31 2015-10-13 Danfoss A/S Centrifugal compressor with extended operating range
US10962016B2 (en) 2016-02-04 2021-03-30 Danfoss A/S Active surge control in centrifugal compressors using microjet injection

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015211270A1 (de) * 2015-06-18 2016-12-22 Bayerische Motoren Werke Aktiengesellschaft Turbolader für ein Kraftfahrzeug
US10570925B2 (en) 2015-10-27 2020-02-25 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
US10927761B2 (en) * 2019-04-17 2021-02-23 General Electric Company Refreshing heat management fluid in a turbomachine

Citations (3)

* 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
DE10355241A1 (de) 2003-11-26 2005-06-30 Rolls-Royce Deutschland Ltd & Co Kg Strömungsarbeitsmaschine mit Fluidzufuhr
DE10355240A1 (de) 2003-11-26 2005-07-07 Rolls-Royce Deutschland Ltd & Co Kg Strömungsarbeitsmaschine mit Fluidentnahme

Family Cites Families (9)

* 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
US8021104B2 (en) * 2004-06-07 2011-09-20 Honeywell International Inc. Compressor apparatus with recirculation and method therefore
DE102004030597A1 (de) * 2004-06-24 2006-01-26 Rolls-Royce Deutschland Ltd & Co Kg Strömungsarbeitsmaschine mit Aussenradstrahlerzeugung am Stator

Patent Citations (3)

* 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
DE10355241A1 (de) 2003-11-26 2005-06-30 Rolls-Royce Deutschland Ltd & Co Kg Strömungsarbeitsmaschine mit Fluidzufuhr
DE10355240A1 (de) 2003-11-26 2005-07-07 Rolls-Royce Deutschland Ltd & Co Kg Strömungsarbeitsmaschine mit Fluidentnahme

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9157446B2 (en) 2013-01-31 2015-10-13 Danfoss A/S Centrifugal compressor with extended operating range
US10184481B2 (en) 2013-01-31 2019-01-22 Danfoss A/S Centrifugal compressor with extended operating range
US10962016B2 (en) 2016-02-04 2021-03-30 Danfoss A/S Active surge control in centrifugal compressors using microjet injection

Also Published As

Publication number Publication date
DE102008004834A1 (de) 2009-07-23
EP2080908A3 (fr) 2011-07-13
US20090238677A1 (en) 2009-09-24

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