EP0224764B1 - Axial thrust compensation device for fluid pumps - Google Patents

Axial thrust compensation device for fluid pumps Download PDF

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Publication number
EP0224764B1
EP0224764B1 EP86115684A EP86115684A EP0224764B1 EP 0224764 B1 EP0224764 B1 EP 0224764B1 EP 86115684 A EP86115684 A EP 86115684A EP 86115684 A EP86115684 A EP 86115684A EP 0224764 B1 EP0224764 B1 EP 0224764B1
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EP
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Prior art keywords
sleeve
bores
gap
equalizer
equalizer according
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Expired
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EP86115684A
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German (de)
French (fr)
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EP0224764A1 (en
Inventor
Johann Guelich
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Sulzer AG
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Gebrueder Sulzer AG
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    • 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
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/04—Antivibration arrangements
    • 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
    • F01D3/00—Machines or engines with axial-thrust balancing effected by working-fluid
    • F01D3/04—Machines or engines with axial-thrust balancing effected by working-fluid axial thrust being compensated by thrust-balancing dummy piston or the like
    • 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
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/041—Axial thrust balancing
    • F04D29/0416—Axial thrust balancing balancing pistons

Definitions

  • the invention relates to an axial thrust compensation device for a liquid pump, which essentially consists of a fixed sleeve and a relief piston rotating in this sleeve and firmly connected to the impeller shaft, and to the use of such an axial thrust compensation device.
  • Such devices are used in liquid pumps, in particular in multi-stage high-performance radial pumps, and have the purpose and the task of neutralizing or reducing large axial thrust forces.
  • the patent specification DE-C 611 232 describes a device for axle thrust relief, in which the working fluid flowing through the gap between the relief piston and the bushing is discharged via drain openings in the bushing and relief holes.
  • the published patent application DE-A 1 940 555 describes an encapsulated centrifugal pump in which an intermediate wall is arranged on both sides of the rotor in the rotor space of the housing.
  • the partition wall and the housing wall form a second channel for the working fluid.
  • the rotor each has a groove which, when the rotor is displaced in the axial direction, changes the flow in the rotor space in such a way that the centering forces acting on the rotor are increased.
  • the construction is self-centering.
  • French patent FR-A 1 276 208 describes a centrifugal pump in which the actual pump wheel lies between unevenly sized pressure surfaces of the axial thrust compensation device.
  • An axial thrust compensation device consists of a rotating pressure compensation or relief piston which is firmly connected to the pump impeller and which runs in a fixed sleeve without contact.
  • the sleeve can be designed as a separate part that is firmly connected to the housing.
  • the relief piston itself can be designed as part of the pump rotor shaft or can be rigidly connected to the rotor shaft as a separate part.
  • the axial thrust compensation device is arranged downstream of the last stage in the direction of the following pump stages.
  • the pressure conditions in the area of the axial thrust compensating device in the liquid are such that, in the operating state, working liquid constantly flows from the impeller side space to and through the gap between the bushing and the relief piston.
  • This liquid is set in rotation in the impeller side space, the intensity of which increases with the flow rate through the gap.
  • the working medium therefore enters the gap with a peripheral component. This rotation of the working fluid can interfere with the maximum performance of the pump by increasing the tendency of the rotor to natural vibrations.
  • the object of the invention is to completely prevent the penetration of liquid on the pump wheel side with pre-rotation into the gap and to supply liquid without pre-rotation to the gap without complex additional devices.
  • the invention as characterized in the claims, solves this problem with the aid of the flowing partial flow from the gap into the impeller side space. Since only pre-rotation-free liquid is fed into the gap via the channels, the rotational movement of the liquid through the gap into the gap space facing away from the pump wheel is reduced, which in turn reduces the tendency of the pump rotor to natural vibrations in the limit load range and thus permits higher pump outputs with the same dimensions of the pump rotor shaft .
  • a device according to the invention has particular advantages for multi-stage, high-speed high-pressure radial pumps such as Boiler feed pumps.
  • the figure shows schematically in section a part of the last two stages of a radial pump with an axial thrust compensation device.
  • the schematic section through the housing and rotor of the last two stages of a radial pump shows the one-part or multi-part, fixed pump housing 1 and the two pump wheels 2, 3, which are rigidly connected to the pump wheel shaft 4.
  • the direction of flow of the liquid in the channels 22, 23 of the pump wheels 2, 3, in the pump wheel adjoining rooms 12, 21, 31 and in the main flow channels 11 is indicated by arrows.
  • the axial thrust compensation device consists of the bush 5, which is fixedly connected to the housing, and the relief piston 6, which is rigidly connected to the rotor shaft 4 and rotates in the bush 5.
  • the sleeve 5 has bores 51, only one of which is shown, which open into an internal groove 52, which in turn opens into the gap 56 between the sleeve 5 and the relief piston 6.
  • the bores in the recess 15 are connected to the wheel side space 31 on the outside of the bush 5.
  • the outer and inner diameter (D 2 , Di) of the sleeve 5 and the outer diameter (Ds) of the relief piston 6 are the flows conditions in this area as shown by the arrows.
  • the embodiment of the invention suitable for a particular type of pump can be determined by a pump specialist without any problems.
  • the groove 52 has the task of uniformly supplying the working fluid to the gap 56 over the circumference of the compensating piston 6 and thus, seen over the circumference, to create pressure conditions which are as balanced as possible. However, it is also conceivable that the groove 52 is completely absent and the bores 51 open directly into the gap 56.
  • the working fluid is supplied to the bores 51 via the recess 15.
  • the recess 15 is missing and the bores 51 are connected directly to the pump wheel side space 31 through lateral bores in the bushing 5 (not shown here) or inclined bores in the housing 1.
  • the rotation of the pump wheel 3 generates a rotating flow of the working fluid in the wheel side space 31 and thus an outward radial pressure gradient.
  • the ratios must now be selected so that in the operating state the radial pressure difference in the side space 31 between the sleeve outer and inner diameter (D 2 , D 1 ) is greater than the pressure loss in the bores 51 and groove 52 with a flow rate (Qi) alone, ie that part of the flow (Q) which flows in the gap 56 towards the end of the gap 56 facing the pump wheel. If this condition is met, a ram flow (Q 2 ) flows from the mouth to the end of the pump impeller end into the impeller side space 31, which at the same time completely prevents the penetration of working fluid with pre-rotation into the gap 56.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Control Of Non-Positive-Displacement Pumps (AREA)
  • Rotary Pumps (AREA)

Abstract

1. An axial-thrust equalizer (5, 6) for a liquid pump, the equalizer mainly comprising a stationary sleeve (5) and, rotating therein, a dummy piston (6) rigidly secured to the pump rotor shaft, characterized in that the sleeve (5) is formed with ducts (51, 52) for guiding out of the rotor side chamber (31) contiguous with the equalizer a flow (Q) of working liquid moving towards the dummy piston (6), the flow (Q) dividing, at the place (53) where the ducts (51, 52) join the gap (56) between the sleeve (5) and the dummy piston (6), into two flows (Q1 , Q2 ) moving towards the two gap ends.

Description

Die Erfindung bezieht sich auf eine Axialschub-Ausgleichsvorrichtung für eine Flüssigkeitspumpe, welche im wesentlichen aus einer feststehenden Büchse und einem in dieser Büchse drehenden, mit der Pumpenradwelle fest verbundenen Entlastungskolben besteht, sowie auf die Verwendung einer derartigen Axialschub-Ausgleichsvorrichtung.The invention relates to an axial thrust compensation device for a liquid pump, which essentially consists of a fixed sleeve and a relief piston rotating in this sleeve and firmly connected to the impeller shaft, and to the use of such an axial thrust compensation device.

Derartige Vorrichtungen werden in Flüssigkeitspumpen, insbesondere in mehrstufigen Hochleistungs-Radialpumpen, eingesetzt und haben den Zweck und die Aufgabe, grosse axiale Schubkräfte zu neutralisieren oder zu mindern.Such devices are used in liquid pumps, in particular in multi-stage high-performance radial pumps, and have the purpose and the task of neutralizing or reducing large axial thrust forces.

Die Patentschrift DE-C 611 232 beschreibt eine Einrichtung zur Achsschubentlastung, bei welcher die durch den Spalt zwischen Entlastungskolben und Büchse fliessende Arbeitsflüssigkeit über Abflussöffnungen in der Büchse und Entlastungsbohrungen abgeführt werden.The patent specification DE-C 611 232 describes a device for axle thrust relief, in which the working fluid flowing through the gap between the relief piston and the bushing is discharged via drain openings in the bushing and relief holes.

Die Offenlegungsschrift DE-A 1 940 555 beschreibt eine gekapselte Zentrifugalpumpe, bei der auf beiden Seiten des Rotors im Rotorraum des Gehäuses eine Zwischenwand angeordnet ist. Zwischenwand und Gehäusewand bilden einen zweiten Kanal für die Arbeitsflüssigkeit. Der Rotor weist je eine Rille auf, die beim Verschieben des Rotors in axialer Richtung, die Strömung im Rotorraum derart verändert, dass die auf den Rotor wirkenden Zentrierkräfte erhöht werden. Die Konstruktion ist selbstzentrierend.The published patent application DE-A 1 940 555 describes an encapsulated centrifugal pump in which an intermediate wall is arranged on both sides of the rotor in the rotor space of the housing. The partition wall and the housing wall form a second channel for the working fluid. The rotor each has a groove which, when the rotor is displaced in the axial direction, changes the flow in the rotor space in such a way that the centering forces acting on the rotor are increased. The construction is self-centering.

Die französische Patentschrift FR-A 1 276 208 beschreibt eine Kreiselpumpe, bei welcher das eigentliche Pumpenrad zwischen ungleichgrossen Druckflächen der Axialschub-Ausgleichsvorrichtung liegen. Um auf die Druckflächen einen möglichst gleichbleibenden Druck auszuüben und damit ein axiales Oszillieren des Pumpenrotors zu vermeiden, wird u.a. vorgeschlagen, in den Lagerbüchsen der ausserhalb der Schubausgleichs-Vorrichtung liegenden Lager radiale Bohrungen anzubringen.French patent FR-A 1 276 208 describes a centrifugal pump in which the actual pump wheel lies between unevenly sized pressure surfaces of the axial thrust compensation device. In order to exert as constant a pressure as possible on the pressure surfaces and thus to avoid axial oscillation of the pump rotor, proposed to make radial bores in the bearing bushes of the bearings located outside the thrust compensation device.

Jede dieser Erfindungen löst andere spezifische Aufgaben, aber keine ist dazu geeignet, das Eindringen vorrotierender Arbeitsflüssigkeit in den Spalt zwischen dem Entlastungskolben und der Büchse zu verhindern.Each of these inventions accomplishes other specific tasks, but none is capable of preventing the pre-rotating working fluid from entering the gap between the relief piston and the sleeve.

Eine Axialschub-Ausgleichsvorrichtung nach dem Oberbegriff des Patentes besteht aus einem mit dem Pumpenlaufrad fest verbundenen, mitdrehenden Druckausgleichs- oder Entlastungskolben, der in einer feststehenden Büchse berührungsfrei läuft. Die Büchse kann als eigener, fest mit dem Gehäuse verbundenen Teil ausgebildet sein. Der Entlastungskolben selbst kann als Teil der Pumpenrotorwelle ausgebildet oder als separater Teil mit der Rotorwelle starr verbunden sein. Die Axialschub-Ausgleichsvorrichtung ist in Richtung der sich folgenden Pumpenstufen der letzten Stufe nachgeordnet.An axial thrust compensation device according to the preamble of the patent consists of a rotating pressure compensation or relief piston which is firmly connected to the pump impeller and which runs in a fixed sleeve without contact. The sleeve can be designed as a separate part that is firmly connected to the housing. The relief piston itself can be designed as part of the pump rotor shaft or can be rigidly connected to the rotor shaft as a separate part. The axial thrust compensation device is arranged downstream of the last stage in the direction of the following pump stages.

Die Druckverhältnisse im Bereich der Axialschub-Ausgleichsvorrichtung sind in der Flüssigkeit derart, dass im Betriebszustand ständig Arbeitsflüssigkeit vom Pumpenrad-Seitenraum zum und durch den Spalt zwischen Büchse und Entlastungskolben fliesst. Diese Flüssigkeit wird im Pumpenrad-Seitenraum in Rotation versetzt, deren Intensität mit der Durchflussmenge durch den Spalt steigt. Das Arbeitsmedium tritt demnach mit einer Umfangskomponente in den Spalt ein. Diese Rotation des Arbeitsmittels kann die maximale Leistung der Pumpe störend beeinflussen, indem die Neigung des Rotors zu Eigenschwingungen zunimmt.The pressure conditions in the area of the axial thrust compensating device in the liquid are such that, in the operating state, working liquid constantly flows from the impeller side space to and through the gap between the bushing and the relief piston. This liquid is set in rotation in the impeller side space, the intensity of which increases with the flow rate through the gap. The working medium therefore enters the gap with a peripheral component. This rotation of the working fluid can interfere with the maximum performance of the pump by increasing the tendency of the rotor to natural vibrations.

Bisher bekannte Lösungen versuchen die Rotationsbewegung des Arbeitsmittels im Pumpenrad-Seitenraum durch Schikanen wie Rippen, Nuten und ähnliches zu vermindern. Die pumpenradseitig in den Spalt eindringende Flüssigkeit hat aber immer eine, wenn auch verminderte Rotationskomponente, eine sogenannte Vorrotation.Previously known solutions attempt to reduce the rotational movement of the working medium in the pump wheel side space by means of chicanes such as ribs, grooves and the like. However, the liquid penetrating into the gap on the pump wheel side always has what is known as a pre-rotation, albeit a reduced component of rotation.

Aufgabe der Erfindung ist es, das pumpenradseitige Eindringen von Flüssigkeit mit Vorrotation in den Spalt vollständig zu unterbinden und dem Spalt vorrotationsfreie Flüssigkeit ohne aufwendige Zusatzeinrichtungen zuzuführen. Die Erfindung, wie sie in den Ansprüchen gekennzeichnet ist, löst diese Aufgabe mit Hilfe des fliessenden Teilstromes aus dem Spalt in den Pumpenrad-Seitenraum. Da dem Spalt über die Kanäle nur noch vorrotationsfreie Flüssigkeit zugeführt wird, ist die Rotationsbewegung der Flüssigkeit durch den Spalt in den vom Pumpenrad abgewendete Spaltraum herabgesetzt, was wiederum die Neigung des Pumpenrotors zu Eigenschwingungen im Grenzlastbereich verringert und damit bei gleichen Dimensionen der Pumpenrotorwelle höhere Pumpenleistungen zulässt.The object of the invention is to completely prevent the penetration of liquid on the pump wheel side with pre-rotation into the gap and to supply liquid without pre-rotation to the gap without complex additional devices. The invention, as characterized in the claims, solves this problem with the aid of the flowing partial flow from the gap into the impeller side space. Since only pre-rotation-free liquid is fed into the gap via the channels, the rotational movement of the liquid through the gap into the gap space facing away from the pump wheel is reduced, which in turn reduces the tendency of the pump rotor to natural vibrations in the limit load range and thus permits higher pump outputs with the same dimensions of the pump rotor shaft .

Besondere Vorteile bringt eine Vorrichtung nach der Erfindung für mehrstufige, schnellaufende Hochdruck-Radialpumpen wie z.B. Kesselspeisepumpen.A device according to the invention has particular advantages for multi-stage, high-speed high-pressure radial pumps such as Boiler feed pumps.

Im folgenden wird die Erfindung anhand der Zeichnung eines Ausführungsbeispiels näher erläutert.The invention is explained in more detail below with reference to the drawing of an exemplary embodiment.

Die Figur zeigt schematisch im Schnitt einen Teil der letzten zwei Stufen einer Radialpumpe mit einer Axialschub-Ausgleichsvorrichtung.The figure shows schematically in section a part of the last two stages of a radial pump with an axial thrust compensation device.

Der schematische Schnitt durch Gehäuse und Rotor der letzten zwei Stufen einer Radialpumpe zeigt das ein- oder mehrteilige, feststehende Pumpengehäuse 1 sowie die beiden Pumpenräder 2, 3, welches starr mit der Pumpenradwelle 4 verbunden sind. Die Strömungsrichtung der Flüssigkeit in den Kanälen 22, 23 der Pumpenräder 2, 3, in den Pumpenrad-Nebenräumen 12, 21, 31 sowie in den Hauptstromkanälen 11 ist mit Pfeilen angezeigt. Die Axialschub-Ausgleichsvorrichtung besteht aus der fest mit dem Gehäuse verbundenen Büchse 5 und dem mit der Rotorwelle 4 starr verbundenen Entlastungskolben 6, der in der Büchse 5 dreht.The schematic section through the housing and rotor of the last two stages of a radial pump shows the one-part or multi-part, fixed pump housing 1 and the two pump wheels 2, 3, which are rigidly connected to the pump wheel shaft 4. The direction of flow of the liquid in the channels 22, 23 of the pump wheels 2, 3, in the pump wheel adjoining rooms 12, 21, 31 and in the main flow channels 11 is indicated by arrows. The axial thrust compensation device consists of the bush 5, which is fixedly connected to the housing, and the relief piston 6, which is rigidly connected to the rotor shaft 4 and rotates in the bush 5.

Die Büchse 5 weist Bohrungen 51 auf, von denen nur eine gezeigt ist, welche in eine Innennute 52 münden, die ihrerseits in den Spalt 56 zwischen Büchse 5 und Entlastungskolben 6 mündet. Auf der Aussenseite der Büchse 5 sind die Bohrungen in unserem Beispiel in der Ausnehmung 15 mit dem Radseitenraum 31 verbunden. Bei entsprechender Dimensionierung und Anordnung der Bohrungen 51 und Nute 52, der Aussen- und Innendurchmesser (D2, Di) der Büchse 5 sowie des Aussendurchmessers (Ds) des Entlastungskolbens 6 sind die Strömungsverhältnisse in diesem Bereich wie mit den Pfeilen eingezeichnet. Die für einen bestimmten Pumpentyp geeignete Ausführung der Erfindung kann von einem Pumpenfachmann problemlos bestimmt werden.The sleeve 5 has bores 51, only one of which is shown, which open into an internal groove 52, which in turn opens into the gap 56 between the sleeve 5 and the relief piston 6. In our example, the bores in the recess 15 are connected to the wheel side space 31 on the outside of the bush 5. With appropriate dimensioning and arrangement of the bores 51 and groove 52, the outer and inner diameter (D 2 , Di) of the sleeve 5 and the outer diameter (Ds) of the relief piston 6 are the flows conditions in this area as shown by the arrows. The embodiment of the invention suitable for a particular type of pump can be determined by a pump specialist without any problems.

Die Wirkungsweise der erfindungsgemässen Anordnung der Kanäle 51 und 52 in der Büchse 5 ist die folgende:

  • Im Betrieb fliesst die Arbeitsflüssigkeit in einem Nebenstrom vom Pumpenrad 32 in den Radseitenraum 31. Beim Fehlen der in unserem Beispiel gezeigten Ausnehmung 15, Kanäle 51 und Nute 52 fliesst die Arbeitsflüssigkeit im Pumpenrad-Seitenraum 31 radial zur pumpenradseitigen Öffnung des Spalts 56 zwischen Büchse 5 und Entlastungskolben 6 der Axialschub-Ausgleichsvorrichtung 5, 6. Die Arbeitsflüssigkeit erfährt dabei im Radseitenraum 31 eine Rotationsbewegung in Drehrichtung des Pumpenrads 3, eine sogenannte Vorrotation. Die Vorrotation wird um so kräftiger, je grösser die Flüssigkeitsmenge, die zum Spalt 56 fliesst, ist.
  • Im gezeigten Beispiel wird nun das Zufliessen von Arbeitsflüssigkeit mit Vorrotation zum pumpenradseitigen Ende des Spaltes 56 dadurch vollständig eliminiert, dass über die Radialbohrungen 51 und Nute 52 vorrotationsfreie Arbeitsflüssigkeit dem Spalt 56 zwischen den beiden Spaltenden zugeführt wird. Ein Teil der durch Bohrungen 51 und Nute 52 strömenden Flüssigkeit (Q2) fliesst über den Spalt 56 in den Pumpenrad-Seitenraum zurück und bewirkt damit eine vollständige Sperrwirkung, so dass keine Flüssigkeit mit Vorrotation in den Spalt 56 eindringen kann. Da es Ziel der Erfindung ist, die Rotation der Flüssigkeit im Spalt 56 zu reduzieren, ist es auch denkbar, dass die Bohrungen 51 nicht Radialbohrungen, sondern gegen die Drehrichtung der Pumpe gerichtet angeordnet sind, womit zusätzlich die im Spalt 56 erfolgende Rotation der Arbeitsflüssigkeit vermindert wird.
The mode of operation of the arrangement of the channels 51 and 52 in the bush 5 according to the invention is as follows:
  • In operation, the working fluid flows in a bypass flow from the pump wheel 32 into the wheel side space 31. In the absence of the recess 15, channels 51 and groove 52 shown in our example, the working fluid flows in the pump wheel side space 31 radially to the opening of the gap 56 between the bushing 5 and 5 on the pump wheel side Relief piston 6 of the axial thrust compensating device 5, 6. The working fluid in the wheel side space 31 experiences a rotational movement in the direction of rotation of the pump wheel 3, a so-called pre-rotation. The pre-rotation becomes stronger the greater the amount of liquid that flows to the gap 56.
  • In the example shown, the inflow of working fluid with pre-rotation to the end of the gap 56 on the pump wheel side is completely eliminated by the fact that pre-rotation-free working fluid is fed to the gap 56 between the two gap ends via the radial bores 51 and grooves 52. Part of the liquid (Q 2 ) flowing through bores 51 and grooves 52 flows back through the gap 56 into the impeller side space and thus brings about a complete blocking action, so that no liquid with pre-rotation can penetrate into the gap 56. Since the aim of the invention is to reduce the rotation of the liquid in the gap 56, it is also conceivable that the bores 51 are not arranged in the radial direction but in the direction opposite to the direction of rotation of the pump, which additionally reduces the rotation of the working fluid in the gap 56 becomes.

Die Nute 52 hat die Aufgabe, die Arbeitsflüssigkeit über den Umfang des Ausgleichskolbens 6 dem Spalt 56 gleichmässig zuzuführen und damit über den Umfang gesehen, möglichst ausgeglichene Druckverhältnisse zu schaffen. Es ist aber auch denkbar, dass die Nute 52 vollständig fehlt und die Bohrungen 51 direkt in den Spalt 56 münden.The groove 52 has the task of uniformly supplying the working fluid to the gap 56 over the circumference of the compensating piston 6 and thus, seen over the circumference, to create pressure conditions which are as balanced as possible. However, it is also conceivable that the groove 52 is completely absent and the bores 51 open directly into the gap 56.

Im Beispiel wird die Arbeitsflüssigkeit den Bohrungen 51 über die Ausnehmung 15 zugeführt. Es ist aber auch denkbar, dass die Ausnehmung 15 fehlt und die Bohrungen 51 direkt durch hier nicht gezeichnete seitliche Bohrung in der Büchse 5 oder Schrägbohrungen im Gehäuse 1 mit dem Pumpenrad-Seitenraum 31 verbunden sind.In the example, the working fluid is supplied to the bores 51 via the recess 15. However, it is also conceivable that the recess 15 is missing and the bores 51 are connected directly to the pump wheel side space 31 through lateral bores in the bushing 5 (not shown here) or inclined bores in the housing 1.

Die Strömung über Ausnehmung 15, Bohrungen 51 und Nute 52 zum Spalt 56 und teilweise wieder zurück zum pumpenradseitigen Spaltende in den Pumpenrad-Nebenraum 31 kommt wie folgt zustande:The flow through recess 15, bores 51 and groove 52 to the gap 56 and partly back to the end of the impeller on the impeller side space 31 occurs as follows:

Die Rotation des Pumpenrades 3 erzeugt im Radseitenraum 31 eine Rotationsströmung der Arbeitsflüssigkeit und damit einen nach aussen gerichteten radialen Druckgradienten. Die Verhältnisse müssen nun so gewählt werden, dass im Betriebszustand der radiale Druckunterschied im Seitenraum 31 zwischen Büchsenaussen- und Innendurchmesser (D2, D1) grösser ist, als der Druckverlust in den Bohrungen 51 und Nute 52 bei einer Durchflussmenge (Qi) allein, d.h. jenem Teil der Strömung (Q), der im Spalt 56 zu dem Pumpenrad abgekehrten Ende des Spalts 56 fliesst. Wenn diese Bedingung erfüllt ist, fliesst von der Mündung zum pumpenradseitigen Spaltende in den Radseitenraum 31 ein Staustrom (Q2), der gleichzeitig das Eindringen von Arbeitsflüssigkeit mit Vorrotation in den Spalt 56 vollständig verhindert.The rotation of the pump wheel 3 generates a rotating flow of the working fluid in the wheel side space 31 and thus an outward radial pressure gradient. The ratios must now be selected so that in the operating state the radial pressure difference in the side space 31 between the sleeve outer and inner diameter (D 2 , D 1 ) is greater than the pressure loss in the bores 51 and groove 52 with a flow rate (Qi) alone, ie that part of the flow (Q) which flows in the gap 56 towards the end of the gap 56 facing the pump wheel. If this condition is met, a ram flow (Q 2 ) flows from the mouth to the end of the pump impeller end into the impeller side space 31, which at the same time completely prevents the penetration of working fluid with pre-rotation into the gap 56.

Günstige Verhältnisse in einer schnellaufenden, mehrstufigen Hochdruckradialpumpe erreicht man beispielsweise, wenn das Verhältnis von Aussenzu Innendurchmesser der Büchse (D2/Di) grösser oder gleich 1,25 ist, und die Summe der Querschnitte der Radialbohrungen 51 mindestens dreimal grösser als der Querschnitt des Spaltes 56 ist, und wenn die Radialbohrungen 51 im Abstand von nur einigen Millimetem, nahe der Stirnfläche 50 angebracht sind.Favorable conditions in a high-speed, multi-stage high-pressure radial pump are achieved, for example, if the ratio of the outside diameter to the inside diameter of the sleeve (D 2 / Di) is greater than or equal to 1.25 and the sum of the cross sections of the radial bores 51 is at least three times larger than the cross section of the gap 56, and if the radial bores 51 are made at a distance of only a few millimeters, near the end face 50.

Claims (10)

1. An axial-thrust equalizer (5, 6) for a liquid pump, the equalizer mainly comprising a stationary sleeve (5) and, rotating therein, a dummy piston (6) rigidly secured to the pump rotor shaft, characterised in that the sleeve (5) is formed with ducts (51, 52) for guiding out of the rotor side chamber (31) contiguous with the equalizer a flow (Q) of working liquid moving towards the dummy piston (6), the flow (Q) dividing, at the place (53) where the ducts (51, 52) join the gap (56) between the sleeve (5) and the dummy piston (6), into two flows (Qi, Q2) moving towards the two gap ends.
2. An equalizer according to claim 1, characterised in that the ducts in the sleeve (5) are bores (51) in the sleeve outer periphery, such bores being distributed uniformly therearound.
3. An equalizer according to claim 1, characterised in that the ducts (51) in the sleeve are bores distributed uniformly around the sleeve outer periphery and a groove (52), the bores (51) extending into the groove (52), the same extending into the gap (56).
4. An equalizer according to claim 2 or 3, characterised in that the bores (51) in the sleeve outer periphery are radial bores.
5. An equalizer according to claim 1 or 2 or 3, characterised in that the bores (51) extend at an angle to the direction of rotation of the rotor shaft (4).
6. An equalizer according to any of claims 3 or 4 or 5, characterised in that the axes of symmetry of the bores (51) are disposed in a plane perpendicular to the axis of the rotor shaft (4) and the groove is a peripheral groove (52).
7. An equalizer according to any of claims 1-6, characterised in that the quotient of outside sleeve diameter and inside sleeve diameter (WD2) is greater than or equal to 1.25 and the ratio of the sum of the bore cross-sections to the gap cross-section is greater than or equal to 3.
8. An equalizer according to any of claims 1-7, characterised in that the sleeve (5) is formed with 24 radial bores (51) distributed uniformly at radial angular spacings of 15° from one another around the sleeve periphery.
9. An equalizer according to any of claims 1-8, characterised in that the ducts (51, 52) are disposed near the rotor-side end face (50) of the sleeve (5).
10. Use of an equalizer according to any of claims 1-9 in a multistage high-speed high-pressure radial- flow liquid pump.
EP86115684A 1985-11-27 1986-11-12 Axial thrust compensation device for fluid pumps Expired EP0224764B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH5066/85 1985-11-27
CH5066/85A CH669241A5 (en) 1985-11-27 1985-11-27 AXIAL PUSH COMPENSATING DEVICE FOR LIQUID PUMP.

Publications (2)

Publication Number Publication Date
EP0224764A1 EP0224764A1 (en) 1987-06-10
EP0224764B1 true EP0224764B1 (en) 1989-05-03

Family

ID=4287365

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86115684A Expired EP0224764B1 (en) 1985-11-27 1986-11-12 Axial thrust compensation device for fluid pumps

Country Status (5)

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US (1) US4892459A (en)
EP (1) EP0224764B1 (en)
CH (1) CH669241A5 (en)
DE (1) DE3663165D1 (en)
FI (1) FI93259C (en)

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Also Published As

Publication number Publication date
CH669241A5 (en) 1989-02-28
FI864381A7 (en) 1987-05-28
FI93259B (en) 1994-11-30
FI864381A0 (en) 1986-10-28
EP0224764A1 (en) 1987-06-10
DE3663165D1 (en) 1989-06-08
FI93259C (en) 1995-03-10
US4892459A (en) 1990-01-09

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