EP0196363B1 - Compresseur axial à un ou plusieurs étages - Google Patents

Compresseur axial à un ou plusieurs étages Download PDF

Info

Publication number
EP0196363B1
EP0196363B1 EP85113808A EP85113808A EP0196363B1 EP 0196363 B1 EP0196363 B1 EP 0196363B1 EP 85113808 A EP85113808 A EP 85113808A EP 85113808 A EP85113808 A EP 85113808A EP 0196363 B1 EP0196363 B1 EP 0196363B1
Authority
EP
European Patent Office
Prior art keywords
resonator
axial compressor
absorption
compressor
clearance spaces
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
EP85113808A
Other languages
German (de)
English (en)
Other versions
EP0196363A1 (fr
Inventor
Manfred Förster
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.)
MAN Gutehoffnungshutte GmbH
Original Assignee
MAN Gutehoffnungshutte GmbH
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 MAN Gutehoffnungshutte GmbH filed Critical MAN Gutehoffnungshutte GmbH
Priority to AT85113808T priority Critical patent/ATE49459T1/de
Publication of EP0196363A1 publication Critical patent/EP0196363A1/fr
Application granted granted Critical
Publication of EP0196363B1 publication Critical patent/EP0196363B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/663—Sound attenuation
    • F04D29/665—Sound attenuation by means of resonance chambers or interference
    • 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
    • F04D29/52—Casings; Connections of working fluid for axial pumps
    • F04D29/522—Casings; Connections of working fluid for axial pumps especially adapted for elastic fluid pumps
    • 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
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/663—Sound attenuation
    • F04D29/664—Sound attenuation by means of sound absorbing material

Definitions

  • the invention relates to a single-stage or multi-stage axial compressor with dead volumes within the compressor housing.
  • pressure pulsations which occur in a single-stage radial compressor with reduced delivery capacity and which cause pulsating impacts in the impeller, which cause vibrations and disturbing noises, are to be prevented in that a single passage or over at least in one wall in the unspanned diffuser channel the circumference of distributed passages are arranged which connect the diffuser channel to at least one annular pressure compensation chamber arranged behind the diffuser wall.
  • GB-A-2 090 334 relates to a tubular resonator for axial machines for reducing vibrations of the impeller blades of the first row of a gas turbine of an aircraft engine.
  • a plurality of tube resonators are embedded in the wall of the flow channel directly opposite the tip of the rotating impeller blade, tuned to 1/4 of the wavelength of the flutter frequency of the impeller blades.
  • absorption resonators form practically perforated walls, each with an inlet bore and a small volume arranged behind it.
  • Absorption resonators of this type are also known in silencers.
  • the object of the invention is to reduce the amplitude of an existing pulsation spectrum in single-stage or multi-stage axial compressors, in order to enlarge the usable working range in the characteristic map of the compressor.
  • an axial compressor is equipped with one or more absorption resonators, so-called Helmholtz resonators.
  • the absorption resonators are arranged between several stages in a stage group.
  • the specialty of the axial compressor and here in the case of speed-controllable machines, is that the pumping point of interest is reached at a constant final pressure, which corresponds to the design pressure, at a speed at which all stages reach their pump limit at the pumping point of the entire compressor. At lower speeds, the first stages pump first. At higher speeds, however, the last stages pump first.
  • the coupling of the absorption resonators is of course not limited to the area of the middle compressor stages. You can also e.g. be coupled to the compressor discharge chamber.
  • the absorption resonators can be used in both compressor sections.
  • the dead volumes known in the case of axial compressors within the compressor housing are suitable as resonator chambers. These are coupled to the gas flow via a circumferential slot, which is arranged before or after an impeller. Such a design creates a Helmholtz resonator, the circumferential slot forming the mouth of the resonator.
  • the axial compressor does not have sufficient dead volumes in the housing, additional dead volumes, which serve as resonator chambers, can be coupled from the outside according to the invention.
  • the walls of the resonator chambers can be at least partially equipped with a damping material of a certain sound resistance.
  • a damping material of a certain sound resistance can e.g. be an insulating material based on mineral fiber.
  • a damping of the neck of the Helmholtz resonator, represented by the circumferential slot, is not possible because of the narrow shape.
  • the frequency of the pulsation spectrum to be damped depends on the type, number of stages and some dynamic factors of the respective axial compressor and is therefore determined experimentally once for each type.
  • the design according to the invention is also suitable for damping pump pulses in the event of a complete stall (deep surge). Although the frequency of this pump is lower, the absorption resonator has a dampening effect.
  • the invention does not take into account the relatively high frequencies resulting from speed and number of blades, nor the relatively low frequency in the event of a complete stall, the "pumping" of the compressor.
  • the existing broadband pulsation spectrum superimposed on the gas flow in the range from 200 to 800 Hz is considered under "steady-state conditions".
  • the amplitude of these pulsations increases when the delivery capacity is reduced before the circulating stall flow (rotating stall) and ultimately the complete stall.
  • the housing space (dead volume) which can be seen between the inflow part 5 and the outflow part 6 is used as the resonator chamber 7.
  • the compressor has a circumferential slot 8, which serves as a coupling slot for the absorption resonator (resonator chamber) 7 and can also be referred to as the neck of a Helmholtz resonator.
  • the walls of the resonator chamber 7, as indicated in FIG. 2, are coated with an acoustic insulation layer D, for example mineral wool.
  • the absorption resonator as shown in the schematic diagram (FIG. 2), represents a mass-spring resonance system.
  • the volume V gives the spring.
  • the resonator neck (slot 8) with its surface S and the length L gives the mass.
  • the resonance frequency is according to the formula certainly.
  • the expression (1 + 2 A I) denotes the muzzle correction necessary for the resonator neck length for this application.
  • an experimentally determined correction for the resonance frequency to higher frequencies is used, since the oscillating gas mass is carried away at the slot outlet by the high gas flow.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Claims (4)

1. Un compresseur axial à un ou plusieurs étages ayant un volume mort à l'intérieur du carter du compresseur, caractérisé en ce que le volume mort existant dans le compresseur axial constitue des chambres de résonateurs et le compresseur axial est équipé d'au moins d'un résonateur par absorption (7) à bande large, formant l'absorbeur des pulsations, et pour coupler le résonateur d'absorption sur la veine de gaz, des fentes périphériques (8) formant l'embouchure du résonateur par absorption sont prévues en amont et en aval d'un rotor (3) et en ce que les parois du résonateur par absorption (7) sont revêtus d'un matériau amortissant D.
2. Compresseur axial à un ou plusieurs étages selon la revendication 1 caractérisé en ce que les fentes (8) sont interrompues par des entretoises.
3. Compresseur axial à un ou plusieurs étages selon la/l'une des revendications 1 et 2 caractérisé en ce que des volumes morts complémentaires sont couplés de l'extérieur sur les chambres de résonateurs.
4. Compresseur axial à un ou plusieurs étages selon les revendications 1 à 3 caractérisé en ce que la fréquence de résonance du résonateur par absorption (7) est accordé sur la plage des pulsations dont l'amplitude maximale est comprise entre 200 et 800 Hz ainsi que sur la première harmonique de cette fréquence.
EP85113808A 1985-03-30 1985-10-30 Compresseur axial à un ou plusieurs étages Expired - Lifetime EP0196363B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT85113808T ATE49459T1 (de) 1985-03-30 1985-10-30 Ein- und mehrstufiger axialkompressor.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19853511769 DE3511769A1 (de) 1985-03-30 1985-03-30 Ein- und mehrstufiger axialkompressor
DE3511769 1985-03-30

Publications (2)

Publication Number Publication Date
EP0196363A1 EP0196363A1 (fr) 1986-10-08
EP0196363B1 true EP0196363B1 (fr) 1990-01-10

Family

ID=6266914

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85113808A Expired - Lifetime EP0196363B1 (fr) 1985-03-30 1985-10-30 Compresseur axial à un ou plusieurs étages

Country Status (3)

Country Link
EP (1) EP0196363B1 (fr)
AT (1) ATE49459T1 (fr)
DE (2) DE3511769A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3927791A1 (de) * 1989-08-23 1991-02-28 Gebhardt Ventilatoren Axialventilator
FR2911923B1 (fr) * 2007-01-25 2011-07-08 Snecma Redresseur acoustique pour carter de soufflante de turboreacteur
US20130263823A1 (en) * 2010-10-25 2013-10-10 Umfotec Umformtechnik Gmbh Disc damper for charge air lines of an internal combustion engine having a turbocharger

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2252256A (en) * 1939-01-11 1941-08-12 Harris Eliot Huntington Sound attenuator for air impellers
NL67569C (fr) * 1948-01-26
DE1403519A1 (de) * 1961-06-24 1969-12-11 Gutehoffnungshuette Sterkrade Einrichtung zur Grenzschichtabsaugung bei Turbomaschinen,insbesondere Radialverdichtern
DE2036085A1 (de) * 1970-07-20 1972-01-27 Kresic M Achsensymmetrisch-Zentrifugalventilator
DE7616393U1 (de) * 1976-05-21 1976-10-28 Bernstein, Hans Friedrich, 8000 Muenchen Radialgebläse
GB2090334B (en) * 1980-12-29 1983-11-16 Rolls Royce Damping flutter of ducted fans

Also Published As

Publication number Publication date
DE3511769A1 (de) 1986-10-02
EP0196363A1 (fr) 1986-10-08
DE3575332D1 (de) 1990-02-15
ATE49459T1 (de) 1990-01-15

Similar Documents

Publication Publication Date Title
DE60105531T2 (de) Gasturbinenbrennkammer, Gasturbine und Düsentriebwerk
EP1738061B1 (fr) Procede de conception d'une turbine d'un moteur d'aeronef
EP1244870B1 (fr) Silencieux pour le compresseur d'un turbocompresseur a gaz d'echappement
DE19640980B4 (de) Vorrichtung zur Dämpfung von thermoakustischen Schwingungen in einer Brennkammer
EP2140119B1 (fr) Compresseur pour turbocompresseur à gaz d'échappement
EP1483536B1 (fr) Turbine a gaz
DE19818873C2 (de) Hubkolbenbrennkraftmaschine
WO2005119031A1 (fr) Silencieux absorbeur pour compresseurs
DE4316475A1 (de) Gasturbinen-Brennkammer
DE112014006922T5 (de) Akustische Behandlungsanordnung für ein Turbinensystem
CH714432A2 (de) Radialverdichter.
WO2007022648A1 (fr) Compresseur centrifuge
EP0196363B1 (fr) Compresseur axial à un ou plusieurs étages
DE102009024568A1 (de) Verdichterlaufrad
DE19818874C2 (de) Hubkolbenmaschine
EP1158590B1 (fr) Système de pile à combustible
DE102012202707B3 (de) Laufradseitenräume mit Resonatoren bei radialen Strömungsmaschinen
EP1153219B1 (fr) Diffuseur sans pulsations de l'interface d'impact, et procede pour empecher les pulsations de l'interface d'impact de diffuseurs
DE10220507B4 (de) Verbrennungsmotor
WO2018178385A1 (fr) Compresseur d'un turbocompresseur de gaz d'échappement
DE102016015296A1 (de) Turbine für einen Abgasturbolader
DE102020113433A1 (de) Radialverdichter für eine Antriebseinrichtung eines Kraftfahrzeugs sowie Verfahren zum Betreiben eines Radialverdichters
DE102020113434A1 (de) Radialverdichter für eine Antriebseinrichtung eines Kraftfahrzeugs sowie Verfahren zum Betreiben eines Radialverdichters
EP4187058A1 (fr) Système de compression pour turbine à gaz, compresseur haute pression, système de compression comprenant un compresseur basse pression haute pression, système de compression comprenant un compresseur basse pression et turbine à gaz
EP3737850A1 (fr) Amortisseur de son de filtre pour un turbocompresseur à gaz d'échappement d'un moteur à combustion interne

Legal Events

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

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE CH DE FR GB IT LI LU NL SE

17P Request for examination filed

Effective date: 19870214

17Q First examination report despatched

Effective date: 19880714

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: MAN GUTEHOFFNUNGSHUETTE AKTIENGESELLSCHAFT

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE CH DE FR GB IT LI LU NL SE

REF Corresponds to:

Ref document number: 49459

Country of ref document: AT

Date of ref document: 19900115

Kind code of ref document: T

REF Corresponds to:

Ref document number: 3575332

Country of ref document: DE

Date of ref document: 19900215

ET Fr: translation filed
ITF It: translation for a ep patent filed

Owner name: BARZANO' E ZANARDO MILANO S.P.A.

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

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

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
ITTA It: last paid annual fee
EPTA Lu: last paid annual fee
EAL Se: european patent in force in sweden

Ref document number: 85113808.1

REG Reference to a national code

Ref country code: CH

Ref legal event code: PUE

Owner name: MAN GUTEHOFFNUNGSHUETTE AKTIENGESELLSCHAFT -DANN A

NLS Nl: assignments of ep-patents

Owner name: GHH BORSIG TURBOMASCHINEN GMBH

REG Reference to a national code

Ref country code: FR

Ref legal event code: TP

REG Reference to a national code

Ref country code: GB

Ref legal event code: 732E

REG Reference to a national code

Ref country code: FR

Ref legal event code: CJ

Ref country code: FR

Ref legal event code: CD

Ref country code: FR

Ref legal event code: CA

REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20030929

Year of fee payment: 19

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: NL

Payment date: 20030930

Year of fee payment: 19

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 20031001

Year of fee payment: 19

Ref country code: LU

Payment date: 20031001

Year of fee payment: 19

Ref country code: CH

Payment date: 20031001

Year of fee payment: 19

Ref country code: AT

Payment date: 20031001

Year of fee payment: 19

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20031009

Year of fee payment: 19

Ref country code: BE

Payment date: 20031009

Year of fee payment: 19

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20031010

Year of fee payment: 19

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20041030

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20041030

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20041030

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20041031

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20041031

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20041031

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20041031

BERE Be: lapsed

Owner name: *GHH BORSIG TURBOMASCHINEN G.M.B.H.

Effective date: 20041031

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20050501

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20050503

EUG Se: european patent has lapsed
REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20041030

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20050630

NLV4 Nl: lapsed or anulled due to non-payment of the annual fee

Effective date: 20050501

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

BERE Be: lapsed

Owner name: *GHH BORSIG TURBOMASCHINEN G.M.B.H.

Effective date: 20041031