EP0044564A1 - Turbokompressor mit einer Einrichtung zum Verhindern des Pumpens - Google Patents

Turbokompressor mit einer Einrichtung zum Verhindern des Pumpens Download PDF

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Publication number
EP0044564A1
EP0044564A1 EP81105752A EP81105752A EP0044564A1 EP 0044564 A1 EP0044564 A1 EP 0044564A1 EP 81105752 A EP81105752 A EP 81105752A EP 81105752 A EP81105752 A EP 81105752A EP 0044564 A1 EP0044564 A1 EP 0044564A1
Authority
EP
European Patent Office
Prior art keywords
vane
compressor
induction
compressor wheel
passage
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Withdrawn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
EP81105752A
Other languages
English (en)
French (fr)
Inventor
Keiichi Nakanishi
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.)
Nissan Motor Co Ltd
Original Assignee
Nissan Motor Co Ltd
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 Nissan Motor Co Ltd filed Critical Nissan Motor Co Ltd
Publication of EP0044564A1 publication Critical patent/EP0044564A1/de
Withdrawn legal-status Critical Current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
    • F04D29/40—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
    • F04D29/46—Fluid-guiding means, e.g. diffusers adjustable
    • F04D29/462—Fluid-guiding means, e.g. diffusers adjustable especially adapted for elastic fluid pumps
    • F04D29/464—Fluid-guiding means, e.g. diffusers adjustable especially adapted for elastic fluid pumps adjusting flow cross-section, otherwise than by using adjustable stator blades
    • 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
    • F04D27/0246—Surge control by varying geometry within the pumps, e.g. by adjusting vanes
    • 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
    • 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
    • F05D2250/00—Geometry
    • F05D2250/50—Inlet or outlet
    • F05D2250/51—Inlet

Definitions

  • the present invention relates generally to a compressor and more specifically to a turbo compressor for a gas turbine or the like equipped with a surge suppressing arrangement.
  • FIG. 1 A known arrangement utilized for controllably swirling the incomming flow of air upstream of the turbo compressor wheel 1 is shown in Figs. 1 and 2.
  • This arrangement takes the form of a series of equidistantly spaced vanes 2 disposed radially about the axis of rotation of the turbo compressor 1.
  • Each of the vanes 2 is pivotally mounted on a shaft 3 provided at one end with a connection link or lever 4.
  • a ring member 5 is operatively connected to each of the links 4 and so that upon rotation of same each of the vanes 2 undergoes the same degree of deflection from its home or neutral position.
  • this arrangement is applied to the type of gas turbine illustrated in Figs.
  • the swirl arrangement includes a plurality of radially disposed adjustable vanes each of which is connected to a control ring through a linkage, whereby the production, assembly and disposition of same in the extremely confined environment of the compressor housing, are time consuming and expensive.
  • the invention features an annular vane having a truncated hyperboloid configuration which is disposed in a portion of a turbo compressor induction passage having a similar curvature.
  • the vane defines inner and an outer sub-passages the cross sectional area of the inlets of which may be varied by moving the vane axially with respect to the compressor wheel while the cross sectional area of the outlets of the two passages remain substantially unchanged.
  • the vane is moved away from the compressor wheel to increase the flow passing through the outer sub-passage while reducing that which passes through the inner one.
  • the resulting increased flow velocity through the outer sub-passage reduces the angle of incidence of the air emitted therefrom impinging on the outer peripheral region of the compressor wheel blades, suppressing the surge tendency, while the lower velocity flow emitted from the inner sub-passage impinges on the root portion of the compressor blades.
  • each of the sub-passages smoothly reduces in the direction of flow which compresses and accelerates each of the flows to promote laminar flow and prevent any tendency to "peel off" the walls of their respective passages.
  • a turbo compressor wheel 10 is operatively disposed in a turbo compressor induction housing 12 of the type having an asymmetical induction port 14 (viz., a port having a mouth which lies on an essentially flat plane spaced from and non-intersecting with the axis of rotation of the compressor wheel 10).
  • the induction housing 12 is further formed with a bell or trumpet shaped member 16 for smoothing and promoting laminar fluid flow toward the blades of the compressor wheel.
  • a surge suppressing guide vane 20 is disposed within the induction passage 22 of the induction housing.
  • This vane has a truncated hyperboloid configuration which has a curvature approximately the same as the bell or trumpet shaped member 16 and is disposed coaxially about the axis of rotation of the compressor wheel.
  • Rods 24 or other suitable linkage members interconnect the surge supressing vane 20 to an actuator 26 adapted to move the vane axially with respect to the compressor wheel in response to the normal surge limit of the compressor being approached.
  • the vane 20 is moved axially away from the compressor wheel 10 as shown in Fig. 4 (above the compressor wheel axis). Due to the movement of the vane within the induction passage the cross sectional area of the inlet 32 of the inner sub-passage 28 decreases while the cross sectional area of the outlet 34 thereof, remains essentially the same and on the other hand the cross sectional area of the inlet 36 of the outer sub-passage 30 hand increases while the cross sectional area of the outlet 38 thereof also remains almost unchanged. This causes a restriction of the flow passing through the inner sub-passage 28 while allowing an increased flow through the outer sub-passage 30.
  • the flow velocity through the outer sub-passage 30 is accordingly increased as compared with the same induction volume with the vane in its "normal" position while the flow through the inner passage is accordingly decreased.
  • the flow velocity of the air impinging on the compressor wheel blades 18 at the outer peripheral portions thereof is increased which reduces the angle of incidence between the air flow and the blades and suppresses the tendency for the compressor to surge.
  • the flow of air emitted from the inner sub-passage 28 has a velocity lower than that emitted from sub-passage 30 but impinges on the root portion of the blades 18 at a location wherein the blades tend to curve both radially and outwardly and which, as such, is not apt to impair the operation of the compressor (viz., inducing a stall or the like).
  • the actuator 26 may be rendered responsive to a suitable control signal from a controller or the like depending on the control system employed to control the compressor and/or associated gas turbine be it hydraulic, electric or pneumatic.
  • the controller is pneumatic it may be responsive to a pressure signal originating on the discharge side of the compressor. This pressure signal may be directly fed to the actuator if desired in which case a damper may be combined with the actuator to offset any hunting tendency apt to occur.
  • Fig. 5 shows in vector form, the relationship between the flow velocity of the fluid in the induction passage, the peripheral velocity of the wheel and the relative velocity of the gases entering to the compressor wheel.
  • VPS denotes the peripheral velocity of the turbine wheel
  • IS the induction velocity in a region close to the outer periphery of the bladed compressor wheel
  • RIS the relative induction velocity of the air entering the peripheral region of the compressor wheel.
  • the broken lines indicate the surge limit of the compressor without the provision or use of the present invention while the solid line shows the extended limit via the use of the invention.
  • RIS increases while the angle of incidence on the blades 18 of the compressor wheel decreases. Accordingly surging is suppressed.
  • the present invention provides a very simple arrangement which neither tends to produce turbulent flow nor be usable with only given types of turbo compressor induction housings and which takes the form of a truncated hyperboloid guide vane movably disposed in the induction passage upstream of and coaxial with the bladed compressor wheel. Movement of the vane away from the compressor wheel accelerates the flow of air impinging on the outer peripheral region of the compressor blades while slowing that impinging on the root portion thereof.
EP81105752A 1980-07-22 1981-07-21 Turbokompressor mit einer Einrichtung zum Verhindern des Pumpens Withdrawn EP0044564A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP99351/80 1980-07-22
JP9935180A JPS5724496A (en) 1980-07-22 1980-07-22 Turbo-compressor

Publications (1)

Publication Number Publication Date
EP0044564A1 true EP0044564A1 (de) 1982-01-27

Family

ID=14245183

Family Applications (1)

Application Number Title Priority Date Filing Date
EP81105752A Withdrawn EP0044564A1 (de) 1980-07-22 1981-07-21 Turbokompressor mit einer Einrichtung zum Verhindern des Pumpens

Country Status (2)

Country Link
EP (1) EP0044564A1 (de)
JP (1) JPS5724496A (de)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2552498A1 (fr) * 1983-09-22 1985-03-29 Proizv Ob Nev Compresseur centrifuge
FR2552499A1 (fr) * 1983-09-22 1985-03-29 Proizv Ob Nev Compresseur centrifuge
GB2168432A (en) * 1984-12-12 1986-06-18 Nevsky Z Im V I Proizv Ob Adjustable guide vanes for centrifugal compressors
EP1662149A1 (de) * 2004-11-29 2006-05-31 M & I Heat Transfer Products Ltd. Einlasskanal für Axiallüfter mit Schalldämpfung
WO2009083292A1 (de) 2007-12-21 2009-07-09 Continental Automotive Gmbh Drallerzeugungsapparat und turbolader mit einem solchen drallerzeugungsapparat
DE102009012971A1 (de) * 2009-03-12 2010-09-16 Bosch Mahle Turbo Systems Gmbh & Co. Kg Ladeeinrichtung für Brennkraftmaschinen
SE2100114A1 (en) * 2021-07-12 2023-01-13 Hans Drangel Variable inlet trim system for a centrifugal compressor

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6071932A (ja) * 1983-09-28 1985-04-23 Toyoda Gosei Co Ltd ピストンカツプ検査機

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH120888A (de) * 1926-07-09 1927-08-01 Escher Wyss Maschf Ag Als Druck- oder Volumenregler für Kraft- und Arbeitsmaschinen verwendbare Regelungsvorrichtung.
DE526494C (de) * 1928-10-11 1931-06-09 Siemens Schuckertwerke Akt Ges Kreiselverdichter
US2169232A (en) * 1939-04-08 1939-08-15 Westinghouse Electric & Mfg Co Blower apparatus
US3918828A (en) * 1974-09-05 1975-11-11 Emerson L Kumm Flow control for compressors and pumps

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH120888A (de) * 1926-07-09 1927-08-01 Escher Wyss Maschf Ag Als Druck- oder Volumenregler für Kraft- und Arbeitsmaschinen verwendbare Regelungsvorrichtung.
DE526494C (de) * 1928-10-11 1931-06-09 Siemens Schuckertwerke Akt Ges Kreiselverdichter
US2169232A (en) * 1939-04-08 1939-08-15 Westinghouse Electric & Mfg Co Blower apparatus
US3918828A (en) * 1974-09-05 1975-11-11 Emerson L Kumm Flow control for compressors and pumps

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2552498A1 (fr) * 1983-09-22 1985-03-29 Proizv Ob Nev Compresseur centrifuge
FR2552499A1 (fr) * 1983-09-22 1985-03-29 Proizv Ob Nev Compresseur centrifuge
GB2168432A (en) * 1984-12-12 1986-06-18 Nevsky Z Im V I Proizv Ob Adjustable guide vanes for centrifugal compressors
EP1662149A1 (de) * 2004-11-29 2006-05-31 M & I Heat Transfer Products Ltd. Einlasskanal für Axiallüfter mit Schalldämpfung
WO2009083292A1 (de) 2007-12-21 2009-07-09 Continental Automotive Gmbh Drallerzeugungsapparat und turbolader mit einem solchen drallerzeugungsapparat
DE102009012971A1 (de) * 2009-03-12 2010-09-16 Bosch Mahle Turbo Systems Gmbh & Co. Kg Ladeeinrichtung für Brennkraftmaschinen
SE2100114A1 (en) * 2021-07-12 2023-01-13 Hans Drangel Variable inlet trim system for a centrifugal compressor

Also Published As

Publication number Publication date
JPS5724496A (en) 1982-02-09
JPH0325640B2 (de) 1991-04-08

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PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

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STAA Information on the status of an ep patent application or granted ep patent

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18D Application deemed to be withdrawn

Effective date: 19830102

RIN1 Information on inventor provided before grant (corrected)

Inventor name: NAKANISHI, KEIICHI