EP0042044B1 - Compresseur axial dont la limite de pompage est déplacée - Google Patents

Compresseur axial dont la limite de pompage est déplacée Download PDF

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Publication number
EP0042044B1
EP0042044B1 EP81102534A EP81102534A EP0042044B1 EP 0042044 B1 EP0042044 B1 EP 0042044B1 EP 81102534 A EP81102534 A EP 81102534A EP 81102534 A EP81102534 A EP 81102534A EP 0042044 B1 EP0042044 B1 EP 0042044B1
Authority
EP
European Patent Office
Prior art keywords
flow
housing
ledges
axial compressor
compressor according
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
EP81102534A
Other languages
German (de)
English (en)
Other versions
EP0042044A1 (fr
Inventor
Hartmut Dr.-Ing. Griepentrog
Hellmut Weinrich
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 Energy Solutions SE
Original Assignee
MAN Maschinenfabrik Augsburg Nuernberg 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 MAN Maschinenfabrik Augsburg Nuernberg AG filed Critical MAN Maschinenfabrik Augsburg Nuernberg AG
Publication of EP0042044A1 publication Critical patent/EP0042044A1/fr
Application granted granted 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
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D19/00—Axial-flow pumps
    • F04D19/02—Multi-stage pumps
    • F04D19/028—Layout of fluid flow through the stages
    • 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
    • F04D29/54—Fluid-guiding means, e.g. diffusers
    • F04D29/541—Specially adapted for elastic fluid pumps
    • F04D29/545—Ducts
    • F04D29/547—Ducts having a special shape in order to influence fluid flow

Definitions

  • the invention relates to a single-stage or multi-stage axial compressor with axially one behind the other, combined into stages guide vane and rotor blade rings, and with one or more from the inner surface of the housing surrounding the vane rings protruding in the circumferential direction around the axis, which according to Art are stair-stepped.
  • sleepers are arranged on the inner wall of the axial compressor, the penultimate sleeper lying directly at the level of a moving blade in the direction of flow.
  • DE-C No. 809842 also describes an axial compressor in which the changes in the internal diameter of the housing required in the direction of flow are carried out by stepwise narrowing.
  • the thresholds formed by the constriction are present both on the inside of the housing and on the outside of the rotor.
  • the threshold surfaces are each cylindrical or conical.
  • the flow guidance is to be improved by the thresholds in such a way that the risk of the flow becoming detached is reduced on the outside of the impeller and on the inside of the stator when the axial speed is shifted.
  • Such a shift in the axial speed is then - according to the cited patent specification - under certain circumstances to avoid difficulties with regard to the Mach number at high peripheral speeds. This indicates that the known device should make it possible to improve the flow, particularly when shifting to high speeds.
  • the primary aim is not to improve the design of the compressor, but to enlarge the work area. As experience shows, it is necessary to increase the flow in the axial direction at the blade tip, e.g. the peripheral speed is reduced.
  • each threshold should restrict the overall free cross-section of the housing only to a cross-sectional area between 80 to 99%, preferably between 95 to 99%, of the cross-sectional area existing before the threshold.
  • the outer contour of the rising surface of the sleepers be curved in the form of a convex curve, which is composed of circular and / or parabolic arcs. A similar rounding can also be found in DE-PS No. 809842.
  • the inner contour of the compressor housing can be assigned a certain average taper, which is related to the compression to be achieved. It is proposed, when using the sleepers according to the invention, to place the upstream base points of the sleepers approximately on a conical jacket describing the mean taper of the inner surface of the housing. This situation can also be deviated from, wind tunnel and standing tests can give the expert advice for improvement.
  • the fact that the axial velocity in the outer blade area is accelerated by the narrowing due to the sleepers is used.
  • the effect is intensified by reducing the flow cross-section.
  • the swirl of the flow is not changed by the constriction; the circumferential component remains constant.
  • the defined high point of the thresholds for example the average threshold height, be approximately on a conical jacket K z describing the average conicity of the inner surface 11 of the housing.
  • the exemplary embodiments of multi-stage axial compressors shown in FIGS. 1 and 2 have guide vane and rotor blade rings arranged one behind the other in conventional and known manner and combined into stages 1, 2, 3,.
  • the guide blades 4, 6 are connected downstream of the moving blades 5, 7.
  • the blades 4 to 7 are also partially pivotable and connected to corresponding adjustment devices.
  • sleepers 12, 13, 14 are provided on the opposite housing inner wall 11, which protrude inward from the inner surface of the housing surrounding the blade rings and in the circumferential direction about the axis.
  • the sleepers are stepped in the direction of flow in the manner of a staircase, constricting the free overall cross section of the housing from step to step by 1 to 5% of the cross-sectional area in front of the threshold.
  • Each threshold 12 to 14 is arranged immediately in front of a moving blade, in the present case designated with the numbers 15, 16, 17, the operation being in the area of the moving blade tips Streamlines are compressed.
  • the outer contour of the sleepers ie the rising surface 18, is rounded in a convex manner.
  • the curvature curve is composed of circular and / or parabolic arcs. The curvature is intended to prevent flow interruptions, turbulence and similar disturbances in the flow.
  • the narrowing of the overall cross section through the thresholds 12, 13, 14 is not so great that an excessive flow constriction occurs in normal operation, which is also undesirable.
  • FIG. 3 On the left side of FIG. 3, the flow conditions of an axial compressor without a threshold arrangement are shown, but with a conically narrowing flow channel.
  • the amount delivered is assumed to be 100% of the bucket height.
  • the speeds C ax are essentially the same over the blade height .
  • the flow velocity in the axial direction If, on the other hand, the quantity is reduced significantly, for example to 60% of the nominal delivery quantity, the speed decreases measured over the bucket height. This can result in tearing, particularly in the upper blade area.
  • the flow channel is equipped with thresholds B, there is an increase in the flow velocities in the upper region, recognizable by the nose, which results from the envelope of the velocity verifiers. It is therefore plausible that the surge limit can be shifted to smaller flow rates - calculated in relation to the nominal flow rate.
  • the installation of sleepers was initially dispensed with in the entrance area.
  • the entire housing with such thresholds, for example if the gases used have a high speed of sound, as is the case for helium, for example.
  • the upstream base points of the sleepers 12 to 14 lie approximately on a conical jacket K, which describes the mean taper of the inner surface 11 of the housing. This shape is relatively easy to produce and brings a defined compression performance.
  • the blades 15, 16, 17 within the housing are turned cylindrical or conical at their tips. This gives them exactly the same distance from the inner surface 11 of the housing, the gradation by the threshold permitting a defined flow gain which is the same for all individual blades.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Claims (7)

1. Compresseur axial à un ou plusieurs étages avec des couronnes d'aubes directrices et d'aubes mobiles (4, 6;15,16,17) réunies les unes derrière les autres pour former des étages (1,2,3), et un ou plusieurs seuils (12, 13, 14), en saillie vers l'intérieur par rapport à la surface intérieure (11) du carter entourant les couronnes d'aubes, entourant l'axe dans la direction périphérique et étant échelonnés à la manière d'un escalier, caractérisé en ce que les seuils (12, 13,14) sont prévus dans la direction d'écoulement directement en amont des aubes mobiles (15, 16, 17) sur la surface intérieure (11 ) du carter, de façon à comprimer les lignes d'écoulement au niveau des pointes des aubes mobiles.
2. Compresseur axial selon la revendication 1, caractérisé en ce que chaque seuil (12, 13, 14) réduit la section d'ensemble libre du carter à une surface de section comprise entre 80 et 99%, et de préférence entre 95 et 99%, de la surface de la section en amont du seuil.
3. Compresseur axial selon l'une des revendications 1 ou 2, caractérisé en ce que le contour extérieur de la surface de montée (18) des seuils (12,13,14) est courbé suivant une ligne convexe qui se compose d'arcs de cercle et/ou de paraboles.
4. Compresseur axial à étages multiples selon l'une des revendications 1 à 3, caractérisé en ce que les points des talons des seuils (12, 13, 14), situés chaque fois en amont, se trouvent pratiquement sur une surface-enveloppe (K,) correspondant à la conicité moyenne de la surface intérieure (11 ) du carter.
5. Compresseur axial à étages multiples selon l'une des revendications 1 à 3, caractérisé en ce que les points hauts fixes des seuils (12,.13, 14), par exemple la hauteur moyenne des seuils, se trouvent sur une surface-enveloppe (Kz) correspondant à la conicité moyenne de la surface intérieure (11 ) du carter.
6. Compresseur axial selon la revendication 1, caractérisé en ce que les aubes mobiles (15, 16, 17) ont des pointes tournées de façon cylindrique ou conique.
7. Compresseur axial selon la revendication 1, caractérisé en ce que les hauteurs des seuils (12, 13,14) augmentent pas à pas dans la direction de l'écoulement.
EP81102534A 1980-06-13 1981-04-03 Compresseur axial dont la limite de pompage est déplacée Expired EP0042044B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3022206 1980-06-13
DE3022206A DE3022206C2 (de) 1980-06-13 1980-06-13 Axialverdichter mit verschobener Pumpgrenze

Publications (2)

Publication Number Publication Date
EP0042044A1 EP0042044A1 (fr) 1981-12-23
EP0042044B1 true EP0042044B1 (fr) 1984-07-11

Family

ID=6104545

Family Applications (1)

Application Number Title Priority Date Filing Date
EP81102534A Expired EP0042044B1 (fr) 1980-06-13 1981-04-03 Compresseur axial dont la limite de pompage est déplacée

Country Status (4)

Country Link
EP (1) EP0042044B1 (fr)
JP (2) JPS5728900A (fr)
DE (2) DE3022206C2 (fr)
SU (1) SU1109065A3 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2908152B1 (fr) * 2006-11-08 2009-02-06 Snecma Sa Aube en fleche de turbomachine
DE102009032277A1 (de) 2009-07-08 2011-01-20 Rolls-Royce Deutschland Ltd & Co Kg Brennkammerkopf einer Gasturbine
DE102009033754A1 (de) 2009-07-17 2011-01-20 Rolls-Royce Deutschland Ltd & Co Kg Axialverdichter mit einem Strömungsimpulserzeuger
US10473118B2 (en) 2014-08-29 2019-11-12 Siemens Aktiengesellschaft Controlled convergence compressor flowpath for a gas turbine engine

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH216489A (de) * 1940-04-04 1941-08-31 Sulzer Ag Mehrstufiger Axialverdichter.
DE809842C (de) * 1948-10-19 1951-08-02 Hermann Oestrich Dr Ing Axialverdichter
US2846137A (en) * 1955-06-03 1958-08-05 Gen Electric Construction for axial-flow turbomachinery
GB866793A (en) * 1956-09-01 1961-05-03 Gio Batta Sommariva Improvements in or relating to axial flow compressors
US2990106A (en) * 1956-10-12 1961-06-27 English Electric Co Ltd Axial flow multi-stage compressors
US3775023A (en) * 1971-02-17 1973-11-27 Teledyne Ind Multistage axial flow compressor
DE2351308C3 (de) * 1973-10-12 1981-10-08 M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 4200 Oberhausen Einrichtung zur Erweiterung des Arbeitsbereichs von Axialströmungsmaschinen
JPS5314205A (en) * 1976-07-23 1978-02-08 Hitachi Ltd Step structure for axial-flow fluid machine

Also Published As

Publication number Publication date
SU1109065A3 (ru) 1984-08-15
DE3022206C2 (de) 1983-08-11
JPS5728900A (en) 1982-02-16
JPS6259800U (fr) 1987-04-14
DE3022206A1 (de) 1982-01-07
EP0042044A1 (fr) 1981-12-23
DE3164670D1 (en) 1984-08-16

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