EP0413130A1 - Pressure wave machine - Google Patents

Pressure wave machine Download PDF

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Publication number
EP0413130A1
EP0413130A1 EP90113155A EP90113155A EP0413130A1 EP 0413130 A1 EP0413130 A1 EP 0413130A1 EP 90113155 A EP90113155 A EP 90113155A EP 90113155 A EP90113155 A EP 90113155A EP 0413130 A1 EP0413130 A1 EP 0413130A1
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Prior art keywords
cell
rotor
pressure wave
wave machine
curvature
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Granted
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EP90113155A
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German (de)
French (fr)
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EP0413130B1 (en
Inventor
Rolf Dr. Althaus
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ABB Asea Brown Boveri Ltd
ABB AB
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ABB Asea Brown Boveri Ltd
Asea Brown Boveri AB
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Priority to AT90113155T priority Critical patent/ATE87712T1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B7/00—Engines characterised by the fuel-air charge being ignited by compression ignition of an additional fuel
    • F02B7/02—Engines characterised by the fuel-air charge being ignited by compression ignition of an additional fuel the fuel in the charge being liquid
    • F02B7/04—Methods of operating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F13/00—Pressure exchangers

Definitions

  • the present invention relates to a pressure wave machine according to the preamble of claim 1.
  • housings with channels for the supply and / or discharge of the two media involved in the pressure wave process are located on the two end faces of the rotor.
  • a pressure wave runs into the cell and compresses the air.
  • the pressure wave reaches the end of the cell as soon as it passes through the high pressure air outlet.
  • the air is pushed out there and the cell is then completely filled with gas.
  • expansion waves ensure that the gas leaves the cell and that fresh air is sucked in, whereupon the compression process is repeated.
  • the rotating rotor creates a radial pressure gradient in the cells due to the rotary movement of the rotor. In the vicinity of the cell end and connection housing, the various a radial flow gradient.
  • the invention seeks to remedy this.
  • the invention has for its object to design the geometry of the inlet and outlet housings in a pressure wave machine of the type mentioned in such a way that the same radial pressure gradient is impressed on the fluid in the flow channels of these housings as in the rotor cells themselves.
  • the main advantage of the invention is to be seen in that, by bending the connection housing in the axial direction in the channel, an acceleration field is generated which prevents the above-mentioned compensation processes in the cells in the rotor end / housing area. This counteracts the risk of detachment and backflow.
  • the following explanations apply to a pressure wave machine with a countercurrent pressure wave process in which the air enters and exits on the two opposite sides of the rotor 1, but also applies in an analogous manner to the process in which the air enters and exits same side of the rotor.
  • the counterflow process mentioned is mainly used in high pressure compressors for gas turbines.
  • the rotor 1 is only partially and schematically shown in the figure. This illustration also shows a single cell 2 and the housings 3 and 4 which follow it. The sheath, which surrounds the rotor 1 and connects the housings, is not shown.
  • the rotor axis 5 is rotationally asymmetrical. Due to the rotary movement of the rotor 1, a radial and outwardly increasing pressure gradient is established in the cells. In the case of a straight inlet housing, the flow at the inlet 3a into the cell 2 is accelerated on the inside of the cell 2 because of the pressure gradients there, and is slowed down on the outside of the cell. This means that a harmful secondary flow arises with such a configuration.
  • Another harmful secondary flow from the cell 2 arises when an outlet housing has a straight outflow geometry: in the area of the outlet 4a from the cell 2, a separation occurs in the flow, which leads to a backflow from the outlet housing back into the interior of the cell 2, the backflow leading from the location of a higher pressure gradient to the location of a lower pressure gradient.
  • the housing is designed according to the figure, the same centrifugal force on the flow is generated in the curvatures as it then forms in cell 2:
  • the fluid in the curved inlet housing 3 points into the inlet 3a
  • Cell 2 has the same pressure gradients as it finds there, ie radial pressure gradients increasing outwards, as a result of which no secondary flow can arise.
  • the same effects are generated in the curved outlet housing 4.
  • the optimal radius of curvature R is characterized by 3 variables: - The flow velocity V of the fluid; - From the mean diameter D of the rotor 1; - The angular velocity ⁇ of the rotor 1.
  • the radius of curvature R at which the centrifugal force generated there corresponds to that in cell 2, is determined according to the following function:
  • the length of the curvature of the housings 3, 4 is preferably three hydraulic cell diameters from the inlet opening 3a upstream and from the outlet opening 4a downstream. This area ensures that at most further up or emerging secondary currents resp. Compensating processes no longer the flow in the area of the entrance 3a into the cell 2 or. condition the outlet 4a from the cell 2.
  • this length of curvature must take into account the geometrical conditions of the connection housing.
  • downstream of the outlet opening 4a The length of the curvature is a diffuser for a smooth transition of the flow into the subsequent guide. If no curvature is possible at the outlet 4a for constructional reasons, a diffuser can be used to help.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Supercharger (AREA)
  • Other Liquid Machine Or Engine Such As Wave Power Use (AREA)
  • Emergency Protection Circuit Devices (AREA)
  • Motor Or Generator Frames (AREA)
  • Electrical Discharge Machining, Electrochemical Machining, And Combined Machining (AREA)
  • Manufacturing Of Printed Wiring (AREA)
  • Ignition Installations For Internal Combustion Engines (AREA)

Abstract

In a pressure wave machine, the ducts of the connecting casings (3, 4) to and from the cells (2) are provided with a curvature running in the axial direction to the opening of the cells (2) and concave in the direction of the axis (5) of the rotor (1). By this means, the same radial pressure gradients as are found in the cells (2) due to the rotation of the rotor (1) are produced in the connecting casings (3, 4). Secondary flows and reverse flows respectively from the cells (2) into the connecting casings (3, 4) or out of them are therefore prevented.

Description

Die vorliegende Erfindung betrifft eine Druckwellenmaschine gemäss Oberbegriff des Anspruchs 1.The present invention relates to a pressure wave machine according to the preamble of claim 1.

Technisches Gebiet und Stand der TechnikTechnical field and state of the art

In Druckwellenmaschinen wird bei ihrer Verwendung als Hoch­druckverdichterstufe einer Gasturbine vorverdichtete Luft zur Erzeugung von Treibgas für den Hochdruckturbinenteil weiter verdichtet. Die weitere Kompression der Luft findet dabei in einem Rotor statt, dessen Umfang in der Regel achsparallel verlaufende Zellen aufweist, in denen die Luft mit aus der Turbinenkammer abgezweigten Treibgas ohne festes Trennelement direkt in Berührung kommt. Zur Steuerung der Ein- und Auslässe von Luft und Gas in die bzw. aus den Zellen befinden sich an den beiden Stirnseiten des Rotors Gehäuse mit Kanälen für die Zu- und/oder Abfuhr der beiden am Druckwellenprozess beteilig­ten Medien.In pressure wave machines, when used as a high-pressure compressor stage of a gas turbine, compressed air is further compressed to generate propellant gas for the high-pressure turbine part. The further compression of the air takes place in a rotor, the circumference of which generally has axially parallel cells in which the air comes into direct contact with propellant gas branched off from the turbine chamber without a fixed separating element. To control the inlets and outlets of air and gas into and out of the cells, housings with channels for the supply and / or discharge of the two media involved in the pressure wave process are located on the two end faces of the rotor.

Kommt eine mit zu verdichtetender Luft gefüllte Zelle vor einem Hochdruckgaseinlass, so läuft eine Druckwelle in die Zelle und verdichtet die Luft. Die Druckwelle erreicht das Ende der Zelle, sobald diese den Hochdruckluftauslass pas­siert. Die Luft wird dort ausgeschoben und die Zelle ist dann ganz mit Gas gefüllt. Beim Weiterdrehen sorgen Expansionswel­len dafür, dass das Gas die Zelle wieder verlässt und dass frische Luft angesaugt wird, worauf sich der Kompressionsvor­gang wiederholt. Im bewegten Rotor stellt sich, im Gegensatz zu den ruhenden Gehäusen, aufgrund der Drehbewegung des Rotors ein radialer Druckgradient in den Zellen ein. In der Umgebung von Zellenende und Anschlussgehäuse setzt durch die verschie­ denen radialen Druckgradienten eine Ausgleichsströmung ein. Das heisst, beim Ausströmen aus dem Rotor wird das Fluid an der Rotoraussenseite beschleunigt, an der Rotorinnenseite wird es abgebremst, oder es tritt sogar Ablösung und Rückströmung auf. Beim Eintritt in die Zelle wird die Strömung an der In­nenseite des Rotors beschleunigt und an der Innenseite abge­bremst. Es ist allgemein bekannt, dass stark verzogene Ge­schwindigkeitsprofile direkt in den Wirkungsgrad eingehen und ihn somit verschlechtern. Weiter wird durch die Versperrung an den Ein- bzw. Austritten die Leistungsdichte einer Druckwel­lenmaschine stark herabgesetzt.If a cell filled with air to be compressed comes in front of a high-pressure gas inlet, a pressure wave runs into the cell and compresses the air. The pressure wave reaches the end of the cell as soon as it passes through the high pressure air outlet. The air is pushed out there and the cell is then completely filled with gas. When turning further, expansion waves ensure that the gas leaves the cell and that fresh air is sucked in, whereupon the compression process is repeated. In contrast to the stationary housings, the rotating rotor creates a radial pressure gradient in the cells due to the rotary movement of the rotor. In the vicinity of the cell end and connection housing, the various a radial flow gradient. This means that when it flows out of the rotor, the fluid on the outside of the rotor is accelerated, on the inside of the rotor it is braked, or even detachment and backflow occur. When entering the cell, the flow on the inside of the rotor is accelerated and slowed down on the inside. It is generally known that severely warped speed profiles directly affect the efficiency and thus worsen it. Furthermore, the blockage at the inlets and outlets greatly reduces the power density of a pressure wave machine.

Aufgabe der ErfindungObject of the invention

Hier will die Erfindung Abhilfe schaffen. Der Erfindung liegt die Aufgabe zugrunde, bei einer Druckwellenmaschine der ein­gangs genannten Art die Geometrie der Ein- und Austrittsge­häuse so zu gestalten, dass dem Fluid in den Strömungskanälen dieser Gehäuse der gleiche radiale Druckgradient aufgeprägt wird wie in den Rotorzellen selber.The invention seeks to remedy this. The invention has for its object to design the geometry of the inlet and outlet housings in a pressure wave machine of the type mentioned in such a way that the same radial pressure gradient is impressed on the fluid in the flow channels of these housings as in the rotor cells themselves.

Diese Aufgabe wird gelöst durch die Merkmale des kennzeichnen­den Teils des Anspruchs 1.
Der wesentliche Vorteil der Erfindung ist darin zu sehen, dass durch Krümmen der Anschlussgehäuse in Achsrichtung im Kanal ein Beschleunigungsfeld erzeugt wird, das die obenerwähnten Ausgleichsvorgänge in den Zellen im Gebiet Rotorende/Gehäuse verhindert. Damit wird dort der Gefahr von Ablösungen und Rückströmungen entgegengewirkt.This object is achieved by the features of the characterizing part of claim 1.
The main advantage of the invention is to be seen in that, by bending the connection housing in the axial direction in the channel, an acceleration field is generated which prevents the above-mentioned compensation processes in the cells in the rotor end / housing area. This counteracts the risk of detachment and backflow.

Im folgenden wird anhand der einzigen Figur ein Ausführungs­beispiel der Erfindung schematisch dargestellt. Alle für das unmittelbare Verständnis der Erfindung nicht erforderlichen Elemente sind fortgelassen.An exemplary embodiment of the invention is shown schematically below with reference to the single figure. All elements not necessary for the immediate understanding of the invention have been omitted.

Beschreibung des AusführungsbeispielsDescription of the embodiment

Die nachfolgenden Ausführungen gelten für eine Druckwellenma­schine mit einem Gegenstromdruckwellenprozess, bei dem Ein- und Austritt der Luft auf der zwei entgegengesetzten Seiten des Rotors 1 erfolgen, gelten aber in analoger Weise auch für den Prozess, bei dem Ein- und Austritt der Luft auf ein und derselben Seite des Rotors erfolgen. Der erwähnte Gegenstrom­prozess ist der vorwiegend bei Hochdruckverdichtern für Gasturbinen verwendete.The following explanations apply to a pressure wave machine with a countercurrent pressure wave process in which the air enters and exits on the two opposite sides of the rotor 1, but also applies in an analogous manner to the process in which the air enters and exits same side of the rotor. The counterflow process mentioned is mainly used in high pressure compressors for gas turbines.

Der Rotor 1 ist in der Figur der besseren Übersichtlichkeit halber nur ausschnittsweise und schematisch dargestellt. In dieser Darstellung ist auch eine einzige Zelle 2 und die sich ihr anschliessenden Gehäuse 3 und 4, ersichtlich. Nicht darge­stellt ist der Mantel, der den Rotor 1 umschliesst und die Ge­häuse verbindet. Die Rotorachse 5 ist rotationsasymmetrisch. In den Zellen stellt sich aufgrund der Drehbewegung des Rotors 1 ein radialer und nach aussen zunehmender Druckgradient ein. Bei einem geraden Eintrittsgehäuse wird die Strömung beim Ein­tritt 3a in die Zelle 2, wegen der dort vorhandenen Druckgra­dienten, an der Innenseite der Zelle 2 beschleunigt und an der Aussenseite der Zelle abgebremst. Das heisst, bei einer solchen Konfiguration entsteht eine schädliche sekundäre Strö­mung. Eine weitere schädliche sekundäre Strömung aus der Zelle 2 entsteht, wenn ein Austrittsgehäuse eine gerade Ausströ­mungsgeometrie aufweist: Im Bereich des Austritts 4a aus der Zelle 2 entsteht in der Strömung eine Ablösung, welche zu einer Rückströmung aus dem Autrittsgehäuse zurück ins Innere der Zelle 2 führt, wobei die Rückströmung von der Stelle eines höheren Druckgradienten zu der Stelle eines tieferen Druckgra­dienten führt.For the sake of clarity, the rotor 1 is only partially and schematically shown in the figure. This illustration also shows a single cell 2 and the housings 3 and 4 which follow it. The sheath, which surrounds the rotor 1 and connects the housings, is not shown. The rotor axis 5 is rotationally asymmetrical. Due to the rotary movement of the rotor 1, a radial and outwardly increasing pressure gradient is established in the cells. In the case of a straight inlet housing, the flow at the inlet 3a into the cell 2 is accelerated on the inside of the cell 2 because of the pressure gradients there, and is slowed down on the outside of the cell. This means that a harmful secondary flow arises with such a configuration. Another harmful secondary flow from the cell 2 arises when an outlet housing has a straight outflow geometry: in the area of the outlet 4a from the cell 2, a separation occurs in the flow, which leads to a backflow from the outlet housing back into the interior of the cell 2, the backflow leading from the location of a higher pressure gradient to the location of a lower pressure gradient.

Werden die Gehäuse beispielsweise gemäss der Figur ausgeführt, so wird in den Krümmungen dieselbe Fliehkraft auf die Strömung erzeugt, wie sie sich in der Zelle 2 dann bildet: Das Fluid im gekrümmten Eintrittsgehäuse 3 weist am Eintritt 3a in die Zelle 2 dieselben Druckgradienten auf, wie es sie dort vorfin­det, d.h. radiale nach aussen zunehmende Druckgradienten, wo­durch keine sekundäre Strömung mehr entstehen kann. Dieselben Effekte werden im gekrümmten Austrittsgehäuse 4 erzeugt. Somit lässt sich sagen, dass durch Krümmen der Anschlussge­häuse (Eintrittsgehäuse 3, Austrittsgehäuse 4) in Achsrichtung im jeweiligen Kanal der Anschlussgehäuse ein Beschleunigungs­feld erzeugt wird, das die erwähnten Ausgleichsvorgänge im Be­reich des Eintritts 3a und Austritts 4a in die resp. aus der Zelle 2 verhindert.If, for example, the housing is designed according to the figure, the same centrifugal force on the flow is generated in the curvatures as it then forms in cell 2: The fluid in the curved inlet housing 3 points into the inlet 3a Cell 2 has the same pressure gradients as it finds there, ie radial pressure gradients increasing outwards, as a result of which no secondary flow can arise. The same effects are generated in the curved outlet housing 4. Thus, it can be said that by bending the connection housing (inlet housing 3, outlet housing 4) in the axial direction in the respective channel of the connection housing, an acceleration field is generated which compensates for the above-mentioned compensation processes in the area of the inlet 3a and outlet 4a in the resp. prevented from cell 2.

Somit wird erreicht, dass die Zelle 2 fortlaufend sauber mit Fluid gefüllt wird und sich entleeren kann, was sich insbeson­dere positiv auf die Leistungsdichte der Druckwellenmaschine auswirkt.This ensures that the cell 2 is continuously cleanly filled with fluid and can empty, which has a particularly positive effect on the power density of the pressure wave machine.

Der optimale Krümmungsradius R wird von 3 Variablen geprägt:
- Von der Strömungsgeschwindigkeit V des Fluids;
- Vom mittleren Durchmesser D des Rotors 1;
- Von der Winkelgeschwindigkeit ω des Rotors 1.The optimal radius of curvature R is characterized by 3 variables:
- The flow velocity V of the fluid;
- From the mean diameter D of the rotor 1;
- The angular velocity ω of the rotor 1.

Der Krümmungsradius R, bei welchem die dort entstehende Flieh­kraft derjenigen in der Zelle 2 entspricht, wird nach folgen­der Funktion ermittelt:

Figure imgb0001
Die Länge der Krümmung der Gehäuse 3, 4 beträgt vorzugsweise ab Eintrittsöffnung 3a stromaufwärts und ab Austrittsöffnung 4a stromabwärts drei hydraulische Zellen-Durchmesser. Mit diesem Bereich ist gewährleistet, dass allenfalls weiter oben resp. unten entstehende sekundäre Strömungen resp. Ausgleichs­vorgänge nicht mehr die Strömung im Bereich des Eintritts 3a in die Zelle 2 resp. des Austritts 4a aus der Zelle 2 kondi­tionieren. Selbstverständlich muss diese Krümmungslänge die geometrischen Gegebenheiten der Anschlussgehäuse berücksichti­gen. Stromabwärts der Austrittsöffnung 4a erfolgt nach besag­ ter Länge der Krümmung ein Diffusor zum sanften Übergang der Strömung in die nachfolgende Führung. Wenn am Austritt 4a aus konstruktiven Gründen keine Krümmung möglich ist, kann man sich durch Einsetzen eines Diffusors behelfen.The radius of curvature R, at which the centrifugal force generated there corresponds to that in cell 2, is determined according to the following function:
Figure imgb0001
 The length of the curvature of the housings 3, 4 is preferably three hydraulic cell diameters from the inlet opening 3a upstream and from the outlet opening 4a downstream. This area ensures that at most further up or emerging secondary currents resp. Compensating processes no longer the flow in the area of the entrance 3a into the cell 2 or. condition the outlet 4a from the cell 2. Of course, this length of curvature must take into account the geometrical conditions of the connection housing. According to said, downstream of the outlet opening 4a The length of the curvature is a diffuser for a smooth transition of the flow into the subsequent guide. If no curvature is possible at the outlet 4a for constructional reasons, a diffuser can be used to help.

Claims (3)

1. Druckwellenmaschine, im wesentlichen bestehend aus einem Rotor (1), mit an seinem Umfang gleichmässig verteilt an­geordneten, parallel zur Rotorachse (5) gerichteten Zel­len (2), welche dazu bestimmt sind, im Betrieb zwei gas­förmige Medien aufzunehmen zwecks Verdichtung des ersten durch Druckwellen des zweiten Mediums, und aus festste­henden Anschlussgehäusen (3, 4) zur Führung der Medien, dadurch gekennzeichnet, dass die Kanäle der Anschlussge­häuse (3, 4) stromaufwärts der Eintrittsöffnung (3a) der Zelle (2) und stromabwärts der Austrittsöffnung (4a) der Zelle (2) eine in Achsrichtung zur Öffnung der Zelle (2) verlaufende, gegenüber der Rotorachse (5) konkave Krüm­mung beschreiben, deren Radius der Funktion
Figure imgb0002
 folgt, worin V die Strömungsgeschwindigkeit des Mediums, D der mittlere Rotordrehmesser, ω die Winkelgeschwindig­keit des Rotors (1) bedeuten.1. pressure wave machine, consisting essentially of a rotor (1), with uniformly distributed on its circumference, parallel to the rotor axis (5) directed cells (2), which are intended to hold two gaseous media during operation for the purpose of compressing the first Pressure waves of the second medium, and from fixed connection housings (3, 4) for guiding the media, characterized in that the channels of the connection housings (3, 4) upstream of the inlet opening (3a) of the cell (2) and downstream of the outlet opening (4a) the cell (2) describe a curvature running in the axial direction to the opening of the cell (2), concave with respect to the rotor axis (5), the radius of the function
Figure imgb0002
 follows, where V is the flow velocity of the medium, D is the mean rotor rotation meter, ω is the angular velocity of the rotor (1). 2. Druckwellenmaschine nach Anspruch 1, dadurch gekennzeich­net, dass die Länge der Krümmung der Anschlussgehäuse (3, 4) ab Eintrittsöffnung (3a) stromaufwärts resp. ab Aus­trittsöffnung (4a) stromabwärts drei mal den hydrauli­schen Durchmesser der Zelle (2) beträgt.2. Pressure wave machine according to claim 1, characterized in that the length of the curvature of the connection housing (3, 4) from the inlet opening (3a) upstream, respectively. from the outlet opening (4a) downstream three times the hydraulic diameter of the cell (2). 3. Druckwellenmaschine nach Anspruch 2, dadurch gekennzeich­net, dass der Krümmung der Austrittsöffnung (4a) ein Dif­fusor nachgeschaltet ist.3. Pressure wave machine according to claim 2, characterized in that the curvature of the outlet opening (4a) is followed by a diffuser.
EP90113155A 1989-08-17 1990-07-10 Pressure wave machine Expired - Lifetime EP0413130B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT90113155T ATE87712T1 (en) 1989-08-17 1990-07-10 PRESSURE WAVE MACHINE.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH300589 1989-08-17
CH3005/89 1989-08-17

Publications (2)

Publication Number Publication Date
EP0413130A1 true EP0413130A1 (en) 1991-02-20
EP0413130B1 EP0413130B1 (en) 1993-03-31

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EP90113155A Expired - Lifetime EP0413130B1 (en) 1989-08-17 1990-07-10 Pressure wave machine

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US (1) US5052895A (en)
EP (1) EP0413130B1 (en)
JP (1) JP2974736B2 (en)
KR (1) KR910004923A (en)
AT (1) ATE87712T1 (en)
CA (1) CA2021728A1 (en)
DE (1) DE59001110D1 (en)
ES (1) ES2044333T3 (en)
PL (1) PL286270A1 (en)
RU (1) RU1828519C (en)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2893086B1 (en) * 2005-11-09 2008-01-25 Onera (Off Nat Aerospatiale) HIGH PERFORMANCE THERMAL MACHINE

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB641167A (en) * 1946-07-29 1950-08-09 Bbc Brown Boveri & Cie Pressure exchangers

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2399394A (en) * 1940-12-07 1946-04-30 Bbc Brown Boveri & Cie Pressure exchanger
GB993288A (en) * 1962-11-15 1965-05-26 Dudley Brian Spalding Improvements in and relating to pressure exchangers
CH550937A (en) * 1972-10-25 1974-06-28 Bbc Brown Boveri & Cie AERODYNAMIC PRESSURE SHAFT MACHINE.
CH610986A5 (en) * 1975-10-10 1979-05-15 Bbc Brown Boveri & Cie
CH592809A5 (en) * 1976-10-15 1977-11-15 Bbc Brown Boveri & Cie

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB641167A (en) * 1946-07-29 1950-08-09 Bbc Brown Boveri & Cie Pressure exchangers

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JP2974736B2 (en) 1999-11-10
KR910004923A (en) 1991-03-29
JPH0396627A (en) 1991-04-22
ATE87712T1 (en) 1993-04-15
PL286270A1 (en) 1991-12-02
EP0413130B1 (en) 1993-03-31
DE59001110D1 (en) 1993-05-06
CA2021728A1 (en) 1991-02-18
US5052895A (en) 1991-10-01
ES2044333T3 (en) 1994-01-01
RU1828519C (en) 1993-07-15

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