EP0046173B1 - Rotary machine, particularly radial-flow compressor - Google Patents
Rotary machine, particularly radial-flow compressor Download PDFInfo
- 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
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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
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- 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
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- 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
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- 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.
Abstract
Description
Die Erfindung betrifft eine Kreiselmaschine, insbesondere Radialverdichter mit einem unbeschaufelten Diffusor gemäss dem Oberbegriff des Anspruches.The invention relates to a centrifugal machine, in particular a radial compressor with an unbladed diffuser according to the preamble of the claim.
Aus der CH-A-409 223 ist ein Radialverdichter mit einem unbeschaufelten Diffusor bekannt, mit Grenzschichtabsaugung in einem Ueberleitkanal. Hierzu sollen nach dem Diffusor in dem Ueberleitkanal sich an den gegenüberliegenden Wandungen dieses Kanals ausbildende Grenzschichten durch in den Wandungen angeordnete Schlitze in ringförmige Hohlräume abgesaugt und hinter das Laufrad zurückgeführt werden. Durch diese Massnahmen sollen Druckverluste im Ueberleitkanal reduziert werden.From CH-A-409 223 a radial compressor with a non-bladed diffuser is known, with boundary layer suction in a transfer duct. For this purpose, after the diffuser in the 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. These measures are intended to reduce pressure losses in the transfer channel.
Aus der US-A-4 131 389 ist ein Radialverdichter mit einem beschaufelten Diffusor bekannt, wobei der Diffusor von Sammelräumen umgeben ist, welche durch Schlitze mit dem Diffusoreintritt verbunden sein sollen. Diese Einrichtung hat den Zweck, eine Ablösung der Grenzschichten an den Diffusorschaufeln zu vermindern und hierdurch eine Reduktion der Pumpzone herbeizuführen.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.
Demgegenüber hat sich die Erfindung die Lösung eines völlig anderen Problems zum Ziel gesetzt.In contrast, the invention aims to solve a completely different problem.
Bekanntlich treten bei Maschinen, wie sie die Erfindung betrifft, beim Erreichen gewisser Betriebszustände während des Teillastbetriebes Druckpulsationen im strömenden Arbeitsmittel auf.As is known, in machines as the invention relates, pressure pulsations occur in the flowing working medium when certain operating states are reached during part-load operation.
Im Kennfeld einer Kreiselmaschine trennt die Stabilitätsgrenze das pulsationsfreie vom pulsationsbelasteten Arbeitsgebiet.In the map of a gyroscope, the stability limit separates the pulsation-free from the pulsation-loaded work area.
Der Erfindung liegt die Aufgabe zugrunde, die Stabilitätsgrenze zu kleineren Durchflusswerten, d. h. zu kleineren Ansaugvolumen zu verschieben, um ein möglichst grosses Gebiet für pulsationsfreien Betrieb zu schaffen.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.
Aus der DE-PS 1 503 658 ist beispielsweise ein Radialverdichter bekannt, dessen Leistungsregelung mittels im axialen Ansaugstutzen angeordneten, in eine Drossel- oder Schliessstellung verstellbaren Leitschaufeln vorgenommen wird. Die bei verminderter Förderleistung auftretenden Druckpulsationen sollen dadurch unterdrückt werden, dass der das Laufrad umschliessende schaufellose Diffusor eine in axialer Richtung verschiebbare Wand aufweist. Bei einem derartigen querschnittsveränderlichen Diffusor wird dessen Stellwand über ein Stellglied gekuppelt, wobei die Querschnittsverminderung des Diffusors erst beginnt, wenn die Leitschaufeln schon teilweise geschlossen sind. Das zum Verstellen der Leitschaufeln dienende Stellglied soll hierbei vorzugsweise aus einem im Verdichtergehäuse axial verschiebbaren, hydraulisch betätigten Ringkolben bestehen, der gegen Ende seiner zum Schliessen der Leitschaufeln dienenden Bewegung gegen die Stellwand des Diffusors stösst und sie in die den Diffusorquerschnitt verengende Stellung drängt.From DE-PS 1 503 658, for example, 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. In the case of 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.
Zur Beseitigung der bei verminderter Förderleistung auftretenden Druckpulsationen, welche pulsierende Stösse im Laufrad hervorrufen, die Vibrationen und störende Geräusche verursachen, ist es weiterhin bekannt, in einem Radialverdichter einen Drosselring anzuordnen, der in Abhängigkeit von der Einstellung der Leitschaufeln, ebenfalls den Diffusorquerschnitt entsprechend verengt. Auch hierbei sind Stellglieder erforderlich, die pneumatisch betätigt werden.In order to eliminate the pressure pulsations which occur with reduced delivery capacity and which cause pulsating shocks in the impeller, which cause vibrations and disturbing noises, it is also known to arrange a throttle ring in a radial compressor which, depending on the setting of the guide vanes, also narrows the diffuser cross section accordingly. Actuators that are pneumatically operated are also required here.
Die bekannten Vorrichtungen benötigen bewegliche Teile und sind konstruktiv aufwendig. Sie bedürfen einer ständigen Wartung.The known devices require moving parts and are structurally complex. They require constant maintenance.
Der Erfindung liegt die Aufgabe zugrunde, ohne einen derartigen konstruktiven Aufwand mit einfachen Mitteln, das eingangs beschriebene Ziel zu erreichen.The object of the invention is to achieve the objective described at the outset with simple means without such a design effort.
Diese Aufgabe wird durch die im Kennzeichen des Anspruchs 1 angegebenen Massnahmen gelöst, wie experimentell bestätigt werden kann.This object is achieved by the measures specified in the characterizing part of
Erfindungsgemäss wird die Querschnittsfläche der Druckausgleichskammer derart gewählt, dass die Querschnittsfläche der Druckausgleichskammer so bemessen ist, dass die Heimholtz-Resonanzfrequenz mindestens dreimal höher als die höchste Pulsationsfrequenz ist, und dass die Durchtrittsbreite höchstens 1 % des Laufraddurchmessers der Kreiselmaschine beträgt.According to the invention, 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.
Die Helmholtz-Resonanzfrequenz F wird nach der Formel
Hierbei ist
- c die Schallgeschwindigkeit des kompressiblen Arbeitsmittels,
- A die Querschnittsfläche der Druckausgleichskammer,
- B die Breite des Durchtritts und
- 1 die Länge des Durchtritts.
Here is
- c the speed of sound of the compressible work equipment,
- A the cross-sectional area of the pressure compensation chamber,
- B the width of the passage and
- 1 the length of the passage.
Bei der vorstehend beschriebenen Anwendung der Bemessungsvorschrift kann ein praktisch verzögerungsfreier Druckausgleich bewirkt werden.With the application of the design specification described above, a practically instantaneous pressure equalization can be brought about.
Es sei noch darauf hingewiesen, dass die Dimensionsgrössen A, B, und 1 vorteilhaft so bestimmt werden, dass die Länge 1 des Durchtritts möglichst klein ist zugunsten einer grösseren Querschnittsfläche A, die für die Ausgleichsströmung zur Verfügung steht. Die Breite B des Durchtritts wird vorteilhaft möglichst klein gewählt, um die Strömungsverluste im Diffusor gering zu halten.It should also be pointed out that the dimension sizes A, B, and 1 are advantageously determined in such a way that the
Die Erfindung wird im folgenden anhand eines in der Zeichnung dargestellten Ausführungsbeispieles erläutert.
Figur 1 zeigt einen Längsschnitt durch einen einstufigen Radialverdichter undFigur 2 ein Detail in vergrössertem Massstab in schematischer Darstellungsweise.Figur 3 zeigt ein Diagram, in dem das Druckverhältnis eines einstufigen Radialverdichters über dem Durchsatz aufgetragen ist und zwar einmal mit und einmal ohne die erfindungsgemässen Massnahmen und mit verschiedenen Vordrallstellungen der Vordrallschaufeln.
- Figure 1 shows a longitudinal section through a single-stage radial compressor and
- Figure 2 shows a detail on an enlarged scale in a schematic representation.
- Figure 3 shows a diagram in which the pressure ratio of a single-stage radial compressor is plotted over the throughput, once with and once without the measures according to the invention and with different pre-twist positions of the pre-twist blades.
Das fliegend gelagerte Laufrad 4 des Verdichters wird gemäss Fig. 1 über die Rotorwelle 3 von einem nicht dargestellten Motor angetrieben. Im Ansaugrohr 1 sind Vordrallschaufeln 2 angeordnet, die entsprechend der Förderleistung in nicht dargestellter, an sich bekannter Weise eingestellt werden.The overhung impeller 4 of the compressor is driven according to FIG. 1 via the
Aus dem Ansaugrohr 1 wird das zu verdichtende Medium, z. B. das Kältemittel einer Kälteanlage, von dem Laufrad 4 in Achsrichtung angesaugt und durch die Laufschaufeln 5 radial nach aussen gefördert.From the
Vom Laufradaustritt aus gelangt das Medium in den unbeschaufelten Diffusor 7 und strömt zwischen dessen Wänden 7a und 7b der Austrittsspirale 8 zu.From the impeller outlet, the medium arrives in the
Der Laufraddurchmesser ist mit D bezeichnet.The impeller diameter is labeled D.
Hinter der Diffusorwand 7a und dem Diffusorgehäuse 6 sind zwei Druckausgleichskammern 9 angeordnet, die jeweils über als Ringspalte 10 ausgebildete Durchtritte mit dem Diffusorkanal in Verbindung stehen.Behind the
In Fig. 2 ist ein vergrösserter Ausschnitt der Fig. 1 dargestellt, und zwar eine im Diffusorgehäuse 6 hinter der Wand 7a des Diffusorkanals 7 angeordnete Druckausgleichskammer 9 mit einem Querschnitt A und einem als Ringspalt ausgebildeten Durchtritt 10 mit der Breite B und Länge 1.FIG. 2 shows an enlarged section of FIG. 1, namely a
Es sei darauf hingewiesen, dass die Erfindung auch solche Fälle umfasst, bei denen eine Druckausgleichskammer über mehrere, als Bohrungen ausgeführte Durchtritte, die über den Umfang verteilt sind, mit dem Diffusorkanal verbunden ist. Weiterhin ist es möglich, nur eine oder mehr als zwei Druckausgleichskammern Vorzusehen, wobei diese Druckausgleichskammern sowohl hinter einer der beiden Diffusorwände als auch gegebenenfalls hinter beiden Diffusorwänden angeordnet sein können.It should be pointed out that 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.
Die Pulsationsfrequenz wird experimentell bestimmt und danach die Bemessung der Druckausgleichskammern und Druckdurchtritte bezüglich Breite und Länge vorgenommen.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.
Hierbei wird der Bemessung die vorstehend beschriebene Vorschrift zugrundegelegt, d. h. derart, dass die Helmholtz-Resonanzfrequenz mindestens das dreifache der höchstens Pulsationsfrequenz ist.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 zeigt ein Diagramm, wie es aus Versuchen ermittelt wurde, und zwar Kennlinien eines einstufigen Radialverdichters für die Winkel (11-(16 der Vordrallschaufeln. Die Kennlinien, welche die Druckverhältnisse in Abhängigkeit vom Durchsatz des Verdichters zeigen, sind für die bekannte Ausführung ohne Druckausgleichskammern mit I-VI und für die erfindungsgemässe Ausführung mit I'-VI' bezeichnet.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 '.
Die Pumpgrenze ist als strichpunktierte Kurve P und die Stabilitätsgrenzen S bzw. S' sind als gestrichelte Kurven dargestellt.The surge limit is shown as a dash-dotted curve P and the stability limits S and S 'are shown as dashed curves.
Aus dem Diagramm geht klar hervor, dass bei Anwendung der erfindungsgemässen Massnahmen die Stabilitätsgrenze in das Gebiet kleinerer Durchsätze bzw. Ansaugvolumen verschoben wird. Somit wird ein wesentlich grösseres Gebiet für einen pulsationsfreien Betrieb für eine Kreiselmaschine erreicht.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.
Claims (1)
- A centrifugal machine, more particularly a radial compressor having an unbiaded diffuser, the unbladed diffuser duct (7) containing, at least in one wall (7a, 7b), a continuous passage (10) or passages distributed over the periphery, the same connecting the diffuser duct (7) to at least one annular chamber disposed behind the diffuser wall (7a, 7b), characterised in that the chamber is in the form of a pressure equalization chamber (9) and its cross-sectional area (A) is so dimensioned that the Helmholtz resonance frequency is at least three times greater than the maximum pulsation frequency, and the passage width (B) is not more than 1 % of the diameter (D) of the centrifugal machine impeller.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CH628180A CH646757A5 (en) | 1980-08-20 | 1980-08-20 | RADIAL COMPRESSORS. |
| CH6281/80 | 1980-08-20 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP0046173A1 EP0046173A1 (en) | 1982-02-24 |
| EP0046173B1 true EP0046173B1 (en) | 1984-04-11 |
Family
ID=4307080
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP81104713A Expired EP0046173B1 (en) | 1980-08-20 | 1981-06-19 | Rotary machine, particularly radial-flow compressor |
Country Status (6)
| Country | Link |
|---|---|
| EP (1) | EP0046173B1 (en) |
| CH (1) | CH646757A5 (en) |
| DE (2) | DE3031848A1 (en) |
| DK (1) | DK151495C (en) |
| ES (1) | ES268526Y (en) |
| NO (1) | NO152381C (en) |
Cited By (1)
| 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)
| 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 (en) | 2008-02-15 | 2009-08-20 | Rolls-Royce Deutschland Ltd & Co Kg | Housing structuring for stabilizing flow in a fluid power machine |
| JP5925192B2 (en) | 2010-06-04 | 2016-05-25 | ボーグワーナー インコーポレーテッド | Exhaust gas turbocharger compressor |
| CN103016363B (en) * | 2011-09-26 | 2016-01-20 | 珠海格力电器股份有限公司 | A kind of centrifugal compressor and controlling method thereof |
| DE102012202707B3 (en) | 2012-02-22 | 2013-03-07 | Siemens Aktiengesellschaft | Impeller side chambers with resonators in radial flow machines |
| CN106065877B (en) * | 2016-08-02 | 2019-01-25 | 合肥通用机械研究院有限公司 | A kind of steady system of centrifugal compressor vaneless diffuser expansion |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR999797A (en) * | 1946-01-04 | 1952-02-05 | Rateau Soc | Further training in centrifugal pumps and compressors |
| US2656096A (en) * | 1946-01-04 | 1953-10-20 | Rateau Soc | Centrifugal pump and compressor |
| DE1096536B (en) * | 1953-08-17 | 1961-01-05 | Rheinische Maschinen Und App G | Centrifugal compressor, from the impeller of which the conveying medium enters a guide device concentrically surrounding the impeller at supersonic speed |
| DE1403519A1 (en) * | 1961-06-24 | 1969-12-11 | Gutehoffnungshuette Sterkrade | Device for boundary layer suction in turbo machines, in particular radial compressors |
| US4131389A (en) * | 1975-11-28 | 1978-12-26 | The Garrett Corporation | Centrifugal compressor with improved range |
-
1980
- 1980-08-20 CH CH628180A patent/CH646757A5/en not_active IP Right Cessation
- 1980-08-23 DE DE19803031848 patent/DE3031848A1/en not_active Withdrawn
-
1981
- 1981-06-19 EP EP81104713A patent/EP0046173B1/en not_active Expired
- 1981-06-19 DE DE8181104713T patent/DE3163065D1/en not_active Expired
- 1981-07-27 ES ES1981268526U patent/ES268526Y/en not_active Expired
- 1981-08-03 DK DK344681A patent/DK151495C/en not_active IP Right Cessation
- 1981-08-19 NO NO81812804A patent/NO152381C/en unknown
Cited By (1)
| 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 |
|---|---|
| NO152381B (en) | 1985-06-10 |
| DK344681A (en) | 1982-02-21 |
| EP0046173A1 (en) | 1982-02-24 |
| DE3163065D1 (en) | 1984-05-17 |
| DE3031848A1 (en) | 1982-03-04 |
| ES268526Y (en) | 1983-12-01 |
| NO812804L (en) | 1982-02-22 |
| DK151495C (en) | 1988-05-24 |
| CH646757A5 (en) | 1984-12-14 |
| DK151495B (en) | 1987-12-07 |
| ES268526U (en) | 1983-05-16 |
| NO152381C (en) | 1985-09-18 |
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