EP2650543A2 - Radialverdichter mit einem Diffusor mit Mitteln zur passiven Kontrolle der Durchflussmenge - Google Patents

Radialverdichter mit einem Diffusor mit Mitteln zur passiven Kontrolle der Durchflussmenge Download PDF

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Publication number
EP2650543A2
EP2650543A2 EP13162922.2A EP13162922A EP2650543A2 EP 2650543 A2 EP2650543 A2 EP 2650543A2 EP 13162922 A EP13162922 A EP 13162922A EP 2650543 A2 EP2650543 A2 EP 2650543A2
Authority
EP
European Patent Office
Prior art keywords
diaphragm
gas
passages
compressor
diffuser
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.)
Granted
Application number
EP13162922.2A
Other languages
English (en)
French (fr)
Other versions
EP2650543B1 (de
EP2650543A3 (de
Inventor
Gilles Nawrocki
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.)
Thermodyn SAS
Original Assignee
Thermodyn SAS
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 Thermodyn SAS filed Critical Thermodyn SAS
Publication of EP2650543A2 publication Critical patent/EP2650543A2/de
Publication of EP2650543A3 publication Critical patent/EP2650543A3/de
Application granted granted Critical
Publication of EP2650543B1 publication Critical patent/EP2650543B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B45/00—Pumps or pumping installations having flexible working members and specially adapted for elastic fluids
    • F04B45/04—Pumps or pumping installations having flexible working members and specially adapted for elastic fluids having plate-like flexible members, e.g. diaphragms
    • 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
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • F04D17/12—Multi-stage pumps
    • F04D17/122—Multi-stage pumps the individual rotor discs being, one for each stage, on a common shaft and axially spaced, e.g. conventional centrifugal multi- stage 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
    • 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
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
    • F04D29/444—Bladed diffusers
    • 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

Definitions

  • the present invention relates to compressors and, in particular, centrifugal compressors. It relates more particularly to the control of the aerodynamic stability of the compressors, at low flow rate.
  • the compressors generally comprise an electric motor and a compressor unit, for example multi-stage, which comprises a set of paddle wheels carried by a shaft.
  • the motor rotates a rotor which is coupled to the compressor shaft.
  • the manipulated gas is admitted to the inlet of the compressor and is transmitted to the successive compression stages of the compressor unit to be discharged at the outlet of the compressor.
  • the characteristic curve of the compression provided by a compressor which represents the discharge pressure as a function of the flow rate, is a function of a series of parameters, such as the suction pressure, the speed of rotation of the rotor, the nature of the gas compressed, ...
  • Such devices require the use of instrumentation to measure the flow rate through the compressor, as well as the suction and discharge pressures, as well as control devices driving a gas recirculation control valve.
  • the object of the invention is therefore to overcome the drawbacks associated with the solutions according to the state of the art and to reduce the risks of occurrence of pumping phenomena and, in particular, the phenomena of instability of the gases flowing in the diffuser. of the compressor.
  • the invention therefore has, according to a first aspect, a diaphragm for a compression stage of a compressor, comprising an assembly of at least one through passage extending between two mutually opposite faces of the diaphragm, so as to create a diaphragm flow of gas between said faces according to the pressure difference prevailing on both sides of the diaphragm.
  • this diaphragm comprises a set of passages regularly arranged in the diaphragm and each extending on one of the faces of the diaphragm, between two fixed vanes provided on the diaphragm.
  • the subject of the invention is also, according to a second aspect, a compressor compression stage, comprising a diaphragm receiving a gas supplied at the inlet of said stage, a winding wheel providing a compression of the gas from the diaphragm and an outlet diffuser.
  • the diaphragm comprises an assembly of at least one through passage extending between a first face of the diaphragm facing gas suction in the compression stage and a second face facing the diffuser so as to create a flow of gas between the diffuser and the gas inlet zone in the diaphragm.
  • this compression stage comprises a set of passages regularly arranged in the diaphragm and each extending, on one of the faces of the diaphragm, between two fixed vanes provided on the diaphragm.
  • the invention also relates to a compressor, in particular a centrifugal compressor, comprising a diaphragm per compression stage as defined above.
  • FIG. 1 there is shown a sectional view of a compression stage of a multi-stage compressor according to the invention.
  • the compressor is a centrifugal compressor and is intended to ensure the compression of a gas taken upstream of the stage and returned downstream at a higher pressure.
  • the compression stage is an intermediate stage disposed between two compression stages. But of course, the invention also applies to the input and output stages.
  • the compression stage designated by the general numerical reference 1, comprises an impeller 2 driven in rotation by a rotor 3 itself coupled to a shaft (not shown) rotated by an electric motor.
  • the compression stage Upstream of the wheel 2, that is to say on the gas suction side, the compression stage comprises a diaphragm 4 intended to communicate the inlet of the compression stage 1 with the exit of a compression stage immediately placed upstream, and a diffuser 5 for slowing down the speed of the gases coming from the impeller 2 and thus increasing the pressure at the outlet of the stage 1.
  • the diaphragm 4 has a generally annular shape and is, with the diffuser 5, one of the stator parts of the compression stage.
  • the diaphragm 4 is provided with a set of through-passages, such as 9, extending between the two faces 6 and 7 of the diaphragm so as to ensure communication between the diffuser 5 and the suction zone. of the compression stage located immediately upstream of the wheel 2.
  • the number of passages 9 corresponds to that of the fixed vanes of the diaphragm 4, so that the passages each open, on the suction side, through an orifice 10 disposed between two fixed blades 8.
  • diaphragm 4 may comprise any number of such passages greater than one.
  • the passages are, however, preferably arranged in the thickness of the diaphragm 4 so as to extend in a radially external inclined manner between a zone converging towards the rotor 3, on the suction side, and a radial zone situated in the diffuser, downstream of wheel 2 ( figure 3 ).
  • the amount of recirculated gas, the discharge to the suction, through the passages 9, which depends on the differential pressure on either side of the diaphragm, is therefore greater for low flow rates. It is, on the contrary, less important for relatively higher flow rates for which the pumping phenomena are less likely to occur.
  • the number and the size of the gas passages are adapted to the flow coefficient of the centrifugal stage, to the number of rectifier blades of the diaphragm and to the quantity of gas necessary to maintain the operating stability.
  • the broadcaster just described has a number of additional advantages.
  • the operating principle of the diaphragm remains available for all conditions of higher pressure.

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)
EP13162922.2A 2012-04-11 2013-04-09 Radialverdichter mit einem diffusor mit mitteln zur passiven kontrolle der durchflussmenge Active EP2650543B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR1253314A FR2989434B1 (fr) 2012-04-11 2012-04-11 Diaphragme avec controle passif de debit pour etage de compression

Publications (3)

Publication Number Publication Date
EP2650543A2 true EP2650543A2 (de) 2013-10-16
EP2650543A3 EP2650543A3 (de) 2018-02-28
EP2650543B1 EP2650543B1 (de) 2021-02-24

Family

ID=48040115

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13162922.2A Active EP2650543B1 (de) 2012-04-11 2013-04-09 Radialverdichter mit einem diffusor mit mitteln zur passiven kontrolle der durchflussmenge

Country Status (4)

Country Link
US (1) US9447784B2 (de)
EP (1) EP2650543B1 (de)
BR (1) BR102013008608A2 (de)
FR (1) FR2989434B1 (de)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6133801B2 (ja) * 2014-02-05 2017-05-24 三菱重工業株式会社 ダイアフラム、および遠心回転機械
US11255338B2 (en) * 2019-10-07 2022-02-22 Elliott Company Methods and mechanisms for surge avoidance in multi-stage centrifugal compressors

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2305226A (en) * 1940-01-05 1942-12-15 Edward A Stalker Blower
DE1403519A1 (de) * 1961-06-24 1969-12-11 Gutehoffnungshuette Sterkrade Einrichtung zur Grenzschichtabsaugung bei Turbomaschinen,insbesondere Radialverdichtern
US3313105A (en) * 1965-08-30 1967-04-11 Gen Motors Corp Gas turbine engine having turbo-compressor thrust bearing means responsive to differential pressures
GB2365930B (en) * 2000-08-12 2004-12-08 Rolls Royce Plc A turbine blade support assembly and a turbine assembly
WO2002035072A2 (en) * 2000-09-05 2002-05-02 Sudarshan Paul Dev Nested core gas turbine engine
JP4675638B2 (ja) * 2005-02-08 2011-04-27 本田技研工業株式会社 ガスタービンエンジンの２次エア供給装置
US7685824B2 (en) * 2005-09-09 2010-03-30 The Regents Of The University Of Michigan Rotary ramjet turbo-generator
US7553122B2 (en) * 2005-12-22 2009-06-30 General Electric Company Self-aspirated flow control system for centrifugal compressors
US7758307B2 (en) * 2007-05-17 2010-07-20 Siemens Energy, Inc. Wear minimization system for a compressor diaphragm
JP5162332B2 (ja) * 2008-05-27 2013-03-13 日本電気株式会社 高周波モジュール及び無線装置

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None

Also Published As

Publication number Publication date
EP2650543B1 (de) 2021-02-24
EP2650543A3 (de) 2018-02-28
BR102013008608A2 (pt) 2016-03-29
US20130272909A1 (en) 2013-10-17
FR2989434B1 (fr) 2015-12-18
US9447784B2 (en) 2016-09-20
FR2989434A1 (fr) 2013-10-18

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