EP0046173B1 - Kreiselmaschine, insbesondere Radialverdichter - Google Patents

Kreiselmaschine, insbesondere Radialverdichter Download PDF

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Publication number
EP0046173B1
EP0046173B1 EP81104713A EP81104713A EP0046173B1 EP 0046173 B1 EP0046173 B1 EP 0046173B1 EP 81104713 A EP81104713 A EP 81104713A EP 81104713 A EP81104713 A EP 81104713A EP 0046173 B1 EP0046173 B1 EP 0046173B1
Authority
EP
European Patent Office
Prior art keywords
diffuser
wall
chamber
centrifugal machine
cross
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
Application number
EP81104713A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0046173A1 (de
Inventor
Ulrich Dr. Bolleter
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.)
Sulzer AG
Original Assignee
Gebrueder Sulzer AG
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 Gebrueder Sulzer AG filed Critical Gebrueder Sulzer AG
Publication of EP0046173A1 publication Critical patent/EP0046173A1/de
Application granted granted Critical
Publication of EP0046173B1 publication Critical patent/EP0046173B1/de
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D17/00—Regulating or controlling by varying flow
    • F01D17/10—Final actuators
    • F01D17/12—Final actuators arranged in stator parts
    • F01D17/14—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits
    • F01D17/141—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of shiftable members or valves obturating part of the flow path
    • F01D17/143—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of shiftable members or valves obturating part of the flow path the shiftable member being a wall, or part thereof of a radial diffuser
    • 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
    • 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
    • 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
    • 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
    • F05D2250/52—Outlet

Definitions

  • the invention relates to a centrifugal machine, in particular a radial compressor with an unbladed diffuser according to the preamble of the claim.
  • a radial compressor with a non-bladed diffuser is known, with boundary layer suction in a transfer duct.
  • boundary layers forming on the opposite walls of this duct are to be sucked off into annular cavities through slots arranged in the walls and returned behind the impeller.
  • a radial compressor with a bladed diffuser is known from US Pat. No. 4,131,389, the diffuser being surrounded by collecting spaces which are to be connected to the diffuser inlet by slots.
  • the purpose of this device is to reduce the detachment of the boundary layers on the diffuser blades and thereby bring about a reduction in the pumping zone.
  • the invention aims to solve a completely different problem.
  • pressure pulsations occur in the flowing working medium when certain operating states are reached during part-load operation.
  • the stability limit separates the pulsation-free from the pulsation-loaded work area.
  • the object of the invention is to reduce the stability limit to smaller flow values, i. H. to smaller intake volumes to create the largest possible area for pulsation-free operation.
  • a radial compressor is known, the power regulation of which is carried out by means of guide vanes which are arranged in the axial intake port and can be adjusted into a throttle or closed position.
  • the pressure pulsations that occur when the delivery rate is reduced are to be suppressed in that the blade-free diffuser surrounding the impeller has a wall that can be displaced in the axial direction.
  • a diffuser of this type which is variable in cross section, its partition is coupled via an actuator, the cross section of the diffuser only beginning when the guide vanes are already partially closed.
  • the actuator used to adjust the guide vanes should preferably consist of a hydraulically actuated annular piston which is axially displaceable in the compressor housing and which, at the end of its movement serving to close the guide vanes, pushes against the partition of the diffuser and urges it into the position which narrows the diffuser cross section.
  • the known devices require moving parts and are structurally complex. They require constant maintenance.
  • the object of the invention is to achieve the objective described at the outset with simple means without such a design effort.
  • the cross-sectional area of the pressure compensation chamber is selected such that the cross-sectional area of the pressure compensation chamber is dimensioned such that the Heimholtz resonance frequency is at least three times higher than the highest pulsation frequency, and that the passage width is at most 1% of the impeller diameter of the gyroscope.
  • the dimension sizes A, B, and 1 are advantageously determined in such a way that the length 1 of the passage is as small as possible in favor of a larger cross-sectional area A, which is available for the compensating flow.
  • the width B of the passage is advantageously chosen to be as small as possible in order to keep the flow losses in the diffuser low.
  • the overhung impeller 4 of the compressor is driven according to FIG. 1 via the rotor shaft 3 by a motor, not shown.
  • Pre-swirl vanes 2 are arranged in the intake pipe 1 and are adjusted in a manner known per se in accordance with the delivery rate in a manner not shown.
  • the medium to be compressed for. B. the refrigerant of a refrigeration system, sucked in by the impeller 4 in the axial direction and conveyed radially outward by the blades 5.
  • the medium arrives in the non-bladed diffuser 7 and flows between the walls 7a and 7b of the outlet spiral 8.
  • the impeller diameter is labeled D.
  • two pressure compensation chambers 9 are arranged, each of which is connected to the diffuser channel via passages designed as annular gaps 10.
  • FIG. 2 shows an enlarged section of FIG. 1, namely a pressure compensation chamber 9 arranged in the diffuser housing 6 behind the wall 7a of the diffuser channel 7 with a cross section A and a passage 10 with the width B and length 1 designed as an annular gap.
  • the invention also includes cases in which a pressure compensation chamber is connected to the diffuser channel via a plurality of passages designed as bores and distributed over the circumference. Furthermore, it is possible to provide only one or more than two pressure compensation chambers, it being possible for these pressure compensation chambers to be arranged both behind one of the two diffuser walls and, if appropriate, behind both diffuser walls.
  • the pulsation frequency is determined experimentally and then the dimensioning of the pressure compensation chambers and pressure passages is carried out with respect to width and length.
  • the design is based on the rule described above, i. H. such that the Helmholtz resonance frequency is at least three times the maximum pulsation frequency.
  • FIG. 3 shows a diagram as it was determined from tests, namely the characteristic curves of a single-stage radial compressor for the angles (11- (16 of the pre-twist blades.
  • the characteristic curves which show the pressure conditions as a function of the throughput of the compressor are for the known embodiment without pressure compensation chambers with I-VI and for the embodiment according to the invention with I'-VI '.
  • the surge limit is shown as a dash-dotted curve P and the stability limits S and S 'are shown as dashed curves.
  • the diagram clearly shows that when the measures according to the invention are used, the stability limit is shifted to the area of smaller throughputs or intake volumes. A much larger area for pulsation-free operation for a rotary machine is thus achieved.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP81104713A 1980-08-20 1981-06-19 Kreiselmaschine, insbesondere Radialverdichter Expired EP0046173B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH6281/80 1980-08-20
CH628180A CH646757A5 (de) 1980-08-20 1980-08-20 Radialverdichter.

Publications (2)

Publication Number Publication Date
EP0046173A1 EP0046173A1 (de) 1982-02-24
EP0046173B1 true EP0046173B1 (de) 1984-04-11

Family

ID=4307080

Family Applications (1)

Application Number Title Priority Date Filing Date
EP81104713A Expired EP0046173B1 (de) 1980-08-20 1981-06-19 Kreiselmaschine, insbesondere Radialverdichter

Country Status (6)

Country Link
EP (1) EP0046173B1 (es)
CH (1) CH646757A5 (es)
DE (2) DE3031848A1 (es)
DK (1) DK151495C (es)
ES (1) ES268526Y (es)
NO (1) NO152381C (es)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4125487C1 (en) * 1991-08-01 1992-06-17 Mtu Friedrichshafen Gmbh Flow casing for radial-flow compressor - has side duct in restricted peripheral section in narrow region of spiral cross=section

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4579509A (en) * 1983-09-22 1986-04-01 Dresser Industries, Inc. Diffuser construction for a centrifugal compressor
GB0004140D0 (en) 2000-02-23 2000-04-12 Holset Engineering Co Compressor
DE102008009604A1 (de) * 2008-02-15 2009-08-20 Rolls-Royce Deutschland Ltd & Co Kg Gehäusestrukturierung zum Stabilisieren der Strömung in einer Strömungsarbeitsmaschine
KR101741618B1 (ko) 2010-06-04 2017-05-30 보르그워너 인코퍼레이티드 배기가스 터보차저의 압축기
CN103016363B (zh) * 2011-09-26 2016-01-20 珠海格力电器股份有限公司 一种离心压缩机及其控制方法
DE102012202707B3 (de) * 2012-02-22 2013-03-07 Siemens Aktiengesellschaft Laufradseitenräume mit Resonatoren bei radialen Strömungsmaschinen
CN106065877B (zh) * 2016-08-02 2019-01-25 合肥通用机械研究院有限公司 一种离心压缩机无叶扩压器扩稳系统

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2656096A (en) * 1946-01-04 1953-10-20 Rateau Soc Centrifugal pump and compressor
FR999797A (fr) * 1946-01-04 1952-02-05 Rateau Soc Perfectionnement aux pompes et compresseurs centrifuges
DE1096536B (de) * 1953-08-17 1961-01-05 Rheinische Maschinen Und App G Zentrifugalverdichter, aus dessen Laufrad das Foerdermittel mit UEberschallgeschwindigkeit in eine das Laufrad konzentrisch umschliessende Leitvorrichtung eintritt
DE1403519A1 (de) * 1961-06-24 1969-12-11 Gutehoffnungshuette Sterkrade Einrichtung zur Grenzschichtabsaugung bei Turbomaschinen,insbesondere Radialverdichtern
US4131389A (en) * 1975-11-28 1978-12-26 The Garrett Corporation Centrifugal compressor with improved range

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4125487C1 (en) * 1991-08-01 1992-06-17 Mtu Friedrichshafen Gmbh Flow casing for radial-flow compressor - has side duct in restricted peripheral section in narrow region of spiral cross=section

Also Published As

Publication number Publication date
DK151495B (da) 1987-12-07
DE3163065D1 (en) 1984-05-17
CH646757A5 (de) 1984-12-14
DK151495C (da) 1988-05-24
NO152381B (no) 1985-06-10
DK344681A (da) 1982-02-21
DE3031848A1 (de) 1982-03-04
NO812804L (no) 1982-02-22
NO152381C (no) 1985-09-18
ES268526Y (es) 1983-12-01
EP0046173A1 (de) 1982-02-24
ES268526U (es) 1983-05-16

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