EP0699276A1 - Pumping process for operating a multi-phase screw pump and pump - Google Patents

Pumping process for operating a multi-phase screw pump and pump

Info

Publication number
EP0699276A1
EP0699276A1 EP94913479A EP94913479A EP0699276A1 EP 0699276 A1 EP0699276 A1 EP 0699276A1 EP 94913479 A EP94913479 A EP 94913479A EP 94913479 A EP94913479 A EP 94913479A EP 0699276 A1 EP0699276 A1 EP 0699276A1
Authority
EP
European Patent Office
Prior art keywords
liquid
phase
screw pump
pressure
flow
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.)
Granted
Application number
EP94913479A
Other languages
German (de)
French (fr)
Other versions
EP0699276B1 (en
Inventor
Gerhard Rohlfing
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.)
ITT Bornemann GmbH
Original Assignee
Joh Heinr Bornemann GmbH
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Filing date
Publication date
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C13/00—Adaptations of machines or pumps for special use, e.g. for extremely high pressures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C2/16—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2210/00—Fluid
    • F04C2210/24—Fluid mixed, e.g. two-phase fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/13—Kind or type mixed, e.g. two-phase fluid

Definitions

  • the invention relates to a pumping method for operating a multi-phase screw pump with at least one delivery screw, which is enclosed by a housing which has at least one suction port and at least one delivery port, the medium drawn in in a low-pulsation continuous flow parallel to the screw shaft is moved and continuously ejected in the pressure port.
  • the invention further relates to a multi-phase screw pump with at least one feed screw, which is enclosed by a housing which has at least one suction port and at least one pressure port, the suction port having a suction space upstream of the feed screw and the pressure port communicate with a pressure chamber downstream of the feed screw.
  • a “multi-phase” is a gas-liquid mixture.
  • the liquid In the case of multi-phase transport, in particular with high gas rates or dry running, the liquid is usually discharged completely.
  • the conveying elements then circulate without a gap-sealing liquid; the pump can no longer build up to full pressure, which causes the delivery to collapse.
  • the compression heat generated by the compression of the gas phase can no longer be sufficiently dissipated. This leads to overheating of the conveying elements and to their thermal expansion, which can result in the pump being destroyed by the start of the housing.
  • insufficient lubrication occurs at the shaft seals at high gas rates or when running dry, which can lead to overheating of the shaft seals and thus to their destruction.
  • the object of the invention is to improve the pumping method described at the outset and the multi-phase screw pump described at the outset in such a way that neither extremely high gas content nor longer dry-running phases lead to an interruption in delivery or damage.
  • this object is achieved in that a partial liquid volume flow (liquid circulation) on the pressure side is separated and metered back into the suction area and thus kept in circulation.
  • a liquid short-circuit line is connected to a lower section of the pressure chamber and is connected to the suction chamber.
  • the liquid remaining in the pump housing should permanently wet the shaft seals - possibly in the form of a mist.
  • the degree of separation required to achieve the stated object and the amount of liquid to be kept in circulation can be determined on the basis of the housing and flow configuration.
  • the liquid circulation can be metered as a function of the pump differential pressure. However, it is also possible to switch a metering pump or a temperature-controlled valve into the liquid short-circuit line. It is advantageous if about 3% of the normal conveying flow is kept in liquid circulation.
  • the flow velocity of the medium emerging from the delivery screw on the pressure side is reduced.
  • this can be done in that the pressure chamber has a cross section that increases in the flow direction of the medium.
  • flow guiding devices can be provided in the pressure chamber, which support the separation and / or feed the liquid phase of the medium emerging from the delivery screw against the assigned shaft seal and subsequently to the connection area of the liquid short-circuit line.
  • Figure 1 - a screw pump in longitudinal section
  • Figure 2 - a schematic representation of a cross section through a modified pump housing
  • the screw spindle pump shown in FIG. 1 has, as conveying elements, two contactless, counter-rotating pairs of conveying screws, each of which comprises a right-hand delivery screw 1 and a left-hand delivery screw 2.
  • the axial thrust is balanced by this two-flow arrangement.
  • the interlocking conveyor screws form, together with the housing 3 surrounding them, individually closed delivery chambers. When rotating via a drive shaft 7, these chambers move continuously and parallel to the shafts 7, 8 from the suction to the pressure side. The direction of rotation of the drive shaft 7 determines the locomotion of the conveyor chambers.
  • the torque transmission from the drive shaft to the driven shaft takes place by means of a gear transmission 4 arranged outside the pump housing 3, the setting of which ensures the contact-free running of the conveying elements.
  • the pump housing 3 has a suction nozzle 5 and a pressure nozzle 6.
  • the latter can preferably be provided on the upper side of the pump housing 3.
  • the drawing shows a vertical central section through the screw pump.
  • the representation can also be a horizontal section in which the suction and pressure ports 5, 6 have been lie opposite, while the two shafts 7, 8 are arranged side by side in a common horizontal plane.
  • the medium 9 flowing to the pump through the suction nozzle 5 is supplied in the pump housing 3 in two partial flows to the respective central suction chamber 10, which is connected upstream of the assigned feed screw 1 or 2.
  • These delivery screws 1, 2 are each followed by a pressure chamber 11, which is closed axially outwards by a shaft seal 12, which serves to seal the outer bearing 13.
  • the pressure chamber 11 has a cross section that increases in the flow direction of the medium 9.
  • a liquid short-circuit line 14 is connected to the lowest point of the pressure chamber 11 and is connected to the suction chamber 10.
  • the partial liquid volume flow separated from the conveyed liquid-gas mixture on the pressure side and metered back into the suction area is identified by the arrow 15 and is conveyed again as a liquid circulation from the suction chamber 10 into the pressure chamber 11.
  • This degree of separation can be determined based on the housing and flow configuration. It has proven expedient to keep about 3% of the normal flow in the liquid circulation.
  • the liquid level thereby ensured in the pump housing 3 or in the pressure chamber 11 can generally be below the waves 7, 8.
  • the wetting of the shaft seals 12 as a result of the direct inflow is generally sufficient for sufficient lubrication of the shaft seals 12. Permanent flushing of the shaft seals 12 is required only in the case of particularly sensitive sealing materials. In this case, a horizontal arrangement of the two shafts 7, 8 next to one another and a correspondingly higher liquid level in the pressure chamber 11 are recommended.
  • a circulation of the conveying elements with sufficient gap-sealing liquid is also ensured due to the liquid short-circuit line 14 according to the invention if the two shafts 7, 8 lie one above the other in a vertical plane. This is because the liquid adhering to the tooth head of the lower feed screw is flung into the tooth base of the upper feed screw and then migrates along the flanks of the top to the tooth head due to the centrifugal force. As a result, the mesh and tooth head remain permanently wetted. This mini wetting of the harmful column is already sufficient to maintain the funding.
  • a correspondingly dimensioned orifice 18 can be connected to the liquid short-circuit line 14 for metering the liquid circulation.
  • FIG. 3 shows a schematic representation of a cross section through a conventional pump housing, which is also intended for the installation of two opposing pairs of feed screws according to Figure 1.
  • the fluid is conveyed axially, seen from the outside towards the center of the pump, into a pressure chamber 11, which is directly downstream of the delivery screws and which merges into a pressure slot 16 arranged approximately centrally in the pump housing.
  • the flow velocity in the pressure chamber 11 and pressure slot 16 in the middle of the pump in such embodiments is approximately 3 to 8 m / s.
  • FIG. 2 shows that the pressure chamber 11 in the pump housing 3 also extends below the pairs of delivery screws or the delivery chambers formed by them together with the housing surrounding them.
  • the pressure chamber 11 is thus designed in such a way that in its lower part the flow velocity of the delivery flow emerging from the delivery screw on the pressure side goes to zero. This results in a separation of the liquid from the gas phase due to the density difference.
  • FIG. 2 The configuration shown in FIG. 2 is possible both with a central and lateral pressure space.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Electromagnetic Pumps, Or The Like (AREA)

Abstract

The invention relates to a pumping process for operating a multi-phase screw pump with at least one feed screw surrounded by a housing having at least one intake stub on one side and at least one discharge stub at its top, in which the intake medium is conveyed parallel to the screw shaft in a continuous low-pulsed stream and continuously discharged at the discharge stub. The invention also relates to a multi-phase screw pump. In order to prevent the drawbacks usually occurring in dry running phases, the invention proposes that a partial liquid volume flow (liquid circulation) be separated on the pressure side and returned in metered quantities into the intake region and thus kept in circulation.

Description

Pumpverfahren zum Betreiben einer Multiphasen-Schraubenspindel- pumpe und PumpePumping method for operating a multi-phase screw pump and pump
Die Erfindung betrifft ein Pumpverfahren zum Betreiben einer Multiphasen-Schraubenspindelpumpe mit zumindest einer Förder¬ schraube, die von einem Gehäuse umschlossen ist, das zumindest einen Saugstutzen und zumindest einen Druckstutzen aufweist, wobei das angesaugte Medium in einem pulsationsarmen kontinu¬ ierlichen Förderstrom parallel zu der Schraubenwelle fortbewegt und im Druckstutzen kontinuierlich ausgestoßen wird.The invention relates to a pumping method for operating a multi-phase screw pump with at least one delivery screw, which is enclosed by a housing which has at least one suction port and at least one delivery port, the medium drawn in in a low-pulsation continuous flow parallel to the screw shaft is moved and continuously ejected in the pressure port.
Die Erfindung betrifft ferner eine Multiphasen-Schraubenspin- delpumpe mit zumindest einer Förderschraube, die von einem Ge¬ häuse umschlossen ist, das zumindest einen Saugstutzen und zu¬ mindest einen Druckstutzen aufweist, wobei der Saugstutzen mit einem der Förderschraube vorgeschalteten Saugraum und der Druck¬ stutzen mit einem der Förderschraube nachgeordneten Druckraum in Verbindung stehen.The invention further relates to a multi-phase screw pump with at least one feed screw, which is enclosed by a housing which has at least one suction port and at least one pressure port, the suction port having a suction space upstream of the feed screw and the pressure port communicate with a pressure chamber downstream of the feed screw.
Unter "Multiphase" ist ein Gas-Flüssigkeits-Gemisch zu verste¬ hen. Beim Multiphasentransport, insbesondere mit hohen Gasraten oder Trockenlauf wird üblicherweise die Flüssigkeit vollständig ausgetragen. Die Förderelemente laufen dann ohne spaltabdich¬ tende Flüssigkeit um; die Pumpe kann nicht mehr den vollen Druck aufbauen, was zum Zusammenbruch der Förderung führt. Die durch die Verdichtung der Gasphase entstehende Kompressionswärme kann nicht mehr ausreichend abgeführt werden. Dies führt zu einer Überhitzung der Förderelemente und zu ihrer Wärmeausdehnung, was eine Zerstörung der Pumpe durch Gehäuseanlauf zur Folge haben kann. Ferner tritt bei hohen Gasraten oder Trockenlauf an den Wellen¬ dichtungen eine Mangelschmierung auf, die zu einer Überhitzung an den Wellenabdichtungen und damit zu deren Zerstörung führen kann. Denn wenn sich der einlaßseitige Restflüssigkeitsstand auf die Unterkante der Förderschrauben einstellt, liegen die Wellen¬ dichtungen trocken; das durch das Fördermedium gebildete Schmiermittel verdampft; die Reibwärme wird nicht mehr abgeführt und führt zur Zerstörung der Wellenabdichtung. Diesem Problem wird derzeit durch Permanentschmierung und -kühlung mit Hilfe eines externen Sperrölaggregates begegnet. Diese Aggregate sind jedoch kostenintensiv und störungsanfällig und beeinträchtigen daher die Wirtschaftlichkeit der in Rede stehenden Pumpen.A “multi-phase” is a gas-liquid mixture. In the case of multi-phase transport, in particular with high gas rates or dry running, the liquid is usually discharged completely. The conveying elements then circulate without a gap-sealing liquid; the pump can no longer build up to full pressure, which causes the delivery to collapse. The compression heat generated by the compression of the gas phase can no longer be sufficiently dissipated. This leads to overheating of the conveying elements and to their thermal expansion, which can result in the pump being destroyed by the start of the housing. In addition, insufficient lubrication occurs at the shaft seals at high gas rates or when running dry, which can lead to overheating of the shaft seals and thus to their destruction. This is because when the residual liquid level on the inlet side adjusts to the lower edge of the delivery screws, the shaft seals are dry; the lubricant formed by the pumped medium evaporates; the frictional heat is no longer dissipated and leads to the destruction of the shaft seal. This problem is currently being countered by permanent lubrication and cooling with the help of an external sealing oil unit. However, these units are cost-intensive and prone to failure and therefore impair the economy of the pumps in question.
Der Erfindung liegt die Aufgabe zugrunde, das eingangs be- schriebene Pumpverfahren sowie die eingangs beschriebene Mul- tiphasen-Schraubenspindelpumpe so zu verbessern, daß weder ex¬ trem hoher Gasgehalt noch längere Trockenlaufphasen zu einer Unterbrechung der Förderung oder zu Schäden führen.The object of the invention is to improve the pumping method described at the outset and the multi-phase screw pump described at the outset in such a way that neither extremely high gas content nor longer dry-running phases lead to an interruption in delivery or damage.
Diese Aufgabe wird hinsichtlich des Pumpfverfahrens erfin¬ dungsgemäß dadurch gelöst, daß druckseitig ein Teil-Flüssig¬ keitsvolumenstrom (Flüssigkeitsumlauf) separiert und dosiert in den Ansaugbereich zurückgeführt und so in Umlauf gehalten wird.With regard to the pumping method, this object is achieved in that a partial liquid volume flow (liquid circulation) on the pressure side is separated and metered back into the suction area and thus kept in circulation.
Hinsichtlich der Pumpe wird die genannte Aufgabe erfindungsgemäß dadurch gelöst, daß an einem unteren Abschnitt des Druckraumes eine Flüssigkeits-Kurzschlußleitung angeschlossen ist, die mit dem Saugraum in Verbindung steht.With regard to the pump, the stated object is achieved according to the invention in that a liquid short-circuit line is connected to a lower section of the pressure chamber and is connected to the suction chamber.
Gemäß dem wesentlichen Erfindungsgedanken soll also sicherge¬ stellt werden, daß in der Pumpe auch bei hohen Gasraten oder zeitlich begrenztem Trockenlauf ausreichend Flüssigkeit zur sicheren Funktionserfüllung in der Pumpe verbleibt und nicht ausgetragen wird. Dabei soll diese im Pumpengehäuse verbleibende Flüssigkeit die Wellenabdichtungen - ggf. in Nebelform - perman- tent ausreichend benetzen. Der zur Lösung der genannten Aufgabe erforderliche Separa¬ tionsgrad bzw. die im Umlauf zu haltende Flüssigkeitsmenge las¬ sen sich anhand der Gehäuse- und Strömungskonfiguration bestim¬ men. Dabei kann die Dosierung des Flüssigkeitsumlaufs in Abhän¬ gigkeit von dem Pumpendifferenzdruck erfolgen. Es ist jedoch auch möglich, in die Flüssigkeits-Kurzschlußleitung eine Dosier¬ pumpe oder aber ein temperaturgesteuertes Ventil zu schalten. Dabei ist es vorteilhaft, wenn etwa 3 % des normalen Förderstro¬ mes im Flüssigkeitsumlauf gehalten wird.According to the essential idea of the invention, it should therefore be ensured that sufficient liquid remains in the pump in the pump, even at high gas rates or for a time-limited dry running, for the safe fulfillment of the function and is not discharged. The liquid remaining in the pump housing should permanently wet the shaft seals - possibly in the form of a mist. The degree of separation required to achieve the stated object and the amount of liquid to be kept in circulation can be determined on the basis of the housing and flow configuration. The liquid circulation can be metered as a function of the pump differential pressure. However, it is also possible to switch a metering pump or a temperature-controlled valve into the liquid short-circuit line. It is advantageous if about 3% of the normal conveying flow is kept in liquid circulation.
Um im Druckraum eine Separierung der Flüssigkeitsphase von der Gasphase des geförderten Mediums zu erleichtern, ist es vorteil¬ haft, wenn die Strömungsgeschwindigkeit des druckseitig aus der Förderschraube austretenden Mediums reduziert wird. Dies kann vorrichtungsmäßig dadurch geschehen, daß der Druckraum einen sich in Durchströmrichtung des Mediums gesehen vergrößernden Querschnitt aufweist. Ferner können im Druckraum Strömungsleit- einrichtungen vorgesehen sein, die die Separation unterstützen und/oder die aus der Förderschraube austretende Flüssigkeits- phase des Mediums gegen die zugeordnete Wellendichtung und nachfolgend dem Anschlußbereich der Flüssigkeits-Kurzschlußlei¬ tung zuführen.In order to facilitate separation of the liquid phase from the gas phase of the conveyed medium in the pressure chamber, it is advantageous if the flow velocity of the medium emerging from the delivery screw on the pressure side is reduced. In terms of the device, this can be done in that the pressure chamber has a cross section that increases in the flow direction of the medium. Furthermore, flow guiding devices can be provided in the pressure chamber, which support the separation and / or feed the liquid phase of the medium emerging from the delivery screw against the assigned shaft seal and subsequently to the connection area of the liquid short-circuit line.
Weitere Merkmale der Erfindung ergeben sich aus den Unteran- Sprüchen und werden in Verbindung mit einem Ausführungsbeispiel näher erläutert. Further features of the invention result from the subclaims and are explained in more detail in connection with an embodiment.
In der Zeichnung sind zwei als Beispiele dienende Ausführungs¬ formen der Erfindung dargestellt. Es zeigen:Two exemplary embodiments of the invention are shown in the drawing. Show it:
Figur 1 - eine Schraubenspindelpumpe im Längsschnitt;Figure 1 - a screw pump in longitudinal section;
Figur 2 - in schematischer Darstellung einen Querschnitt durch ein Pumpengehäuse abgewandelter Bauart undFigure 2 - a schematic representation of a cross section through a modified pump housing and
Figur 3 - in einer Darstellung gemäß Figur 2 einen Quer- schnitt durch ein vorbekanntes PumpengehäuseFigure 3 - in a representation according to Figure 2, a cross section through a previously known pump housing
(Stand der Technik) .(State of the art) .
Die in Figur 1 abgebildete Schraubenspindelpumpe besitzt als Förderelemente zwei berührungslos ineinanderkämmende, gegenläu- fige Förderschraubenpaare, die jeweils eine rechtsgängige För¬ derschraube 1 sowie eine linksgängige Förderschraube 2 umfassen. Durch diese zweiströmige Anordnung ist der Axialschub ausge¬ glichen. Die ineinandergreifenden Förderschrauben bilden zusam¬ men mit dem sie umschließenden Gehäuse 3 einzeln abgeschlossene Förderkammern. Bei Drehung über eine Antriebswelle 7 bewegen sich diese Kammern kontinuierlich und parallel zu den Wellen 7,8 von der Saug- zur Druckseite. Dabei bestimmt die Drehrichtung der Antriebswelle 7 die Fortbewegungseinrichtung der Förderkam¬ mern.The screw spindle pump shown in FIG. 1 has, as conveying elements, two contactless, counter-rotating pairs of conveying screws, each of which comprises a right-hand delivery screw 1 and a left-hand delivery screw 2. The axial thrust is balanced by this two-flow arrangement. The interlocking conveyor screws form, together with the housing 3 surrounding them, individually closed delivery chambers. When rotating via a drive shaft 7, these chambers move continuously and parallel to the shafts 7, 8 from the suction to the pressure side. The direction of rotation of the drive shaft 7 determines the locomotion of the conveyor chambers.
Die Drehmomentübertragung von der Antriebs- auf die getriebene Welle erfolgt durch ein außerhalb des Pumpengehäuses 3 angeord¬ netes Zahnradgetriebe 4, dessen Einstellung den berührungsfreien Lauf der Förderelemente gewährleistet.The torque transmission from the drive shaft to the driven shaft takes place by means of a gear transmission 4 arranged outside the pump housing 3, the setting of which ensures the contact-free running of the conveying elements.
Das Pumpengehäuse 3 weist einen Saugstutzen 5 sowie einen Druckstutzen 6 auf.. Letzterer kann vorzugsweise auf der Ober¬ seite des Pumpengehäuses 3 vorgesehen sein. In diesem Fall zeigt die Zeichnung einen lotrechten Mittelschnitt durch die Schrau- benspindelpumpe. Die Darstellung kann jedoch auch ein Horizon¬ talschnitt sein, bei dem sich Saug- und Druckstutzen 5,6 seit lieh gegenüberliegen, während die beiden Wellen 7,8 in einer gemeinsamen Horizontalebene nebeneinander angeordnet sind.The pump housing 3 has a suction nozzle 5 and a pressure nozzle 6. The latter can preferably be provided on the upper side of the pump housing 3. In this case the drawing shows a vertical central section through the screw pump. However, the representation can also be a horizontal section in which the suction and pressure ports 5, 6 have been lie opposite, while the two shafts 7, 8 are arranged side by side in a common horizontal plane.
Das der Pumpe durch den Saugstutzen 5 zufließende Medium 9 wird im Pumpengehäuse 3 in zwei Teilströmen dem jeweils mittigen Saugraum 10 zugeführt, der der zugeordneten Förderschraube 1 bzw. 2 vorgeschaltet ist. Diesen Förderschrauben 1,2 nachge¬ schaltet ist jeweils ein Druckraum 11, der axial nach außen durch jeweils eine Wellendichtung 12 abgeschlossen ist, die zur Abdichtung der Außenlagerung 13 dient. Der Druckraum 11 weist einen sich in Durchströmrichtung des Mediums 9 gesehen ver¬ größernden Querschnitt auf.The medium 9 flowing to the pump through the suction nozzle 5 is supplied in the pump housing 3 in two partial flows to the respective central suction chamber 10, which is connected upstream of the assigned feed screw 1 or 2. These delivery screws 1, 2 are each followed by a pressure chamber 11, which is closed axially outwards by a shaft seal 12, which serves to seal the outer bearing 13. The pressure chamber 11 has a cross section that increases in the flow direction of the medium 9.
Geht man davon aus, daß die Zeichnung einen lotrechten Längs- mittelschnitt zeigt, dann ist am tiefsten Punkt des Druckraumes 11 eine Flüssigkeits-Kurzschlußleitung 14 angeschlossen, die mit dem Saugraum 10 in Verbindung steht. Der druckseitig aus dem geförderten Flüssigkeits-Gas-Geschmisch separierte und dosiert in den Ansaugbereich zurückgeführte Teil-Flüssigkeitsvolumen- ström ist mit dem Pfeil 15 gekennzeichnet und wird als Flüssig¬ keitsumlauf wieder vom Saugraum 10 in den Druckraum 11 geför¬ dert.If it is assumed that the drawing shows a vertical longitudinal central section, then a liquid short-circuit line 14 is connected to the lowest point of the pressure chamber 11 and is connected to the suction chamber 10. The partial liquid volume flow separated from the conveyed liquid-gas mixture on the pressure side and metered back into the suction area is identified by the arrow 15 and is conveyed again as a liquid circulation from the suction chamber 10 into the pressure chamber 11.
Aus der Zeichnung wird deutlich, daß die aus der Förderschraube 1,2 austretende Flüssigkeitsphase des Mediums 9 gegen die zu¬ geordnete Wellendichtung 12 geführt wird und dann aufgrund der Schwerkraft in den Anschlußbereich der Flüssigkeits-Kurzschlu߬ leitung 14 gelangt. Durch die Vergrößerung des Strömungsquer¬ schnitts des Druckraumes 11 wird die Strömungsgeschwindigkeit des austretenden Mediums verringert, wodurch die Separierung der Flüssigkeitsphase aus dem geförderten Gemisch begünstigt wird. Die Zuführung der Flüssigkeitsphase in den Anschlußbereich der Flüssigkeits-Kurzschlußleitung 14 kann durch in der Zeichnung nur schematisch dargestellte Strömungsleiteinrichtungen 17 be- günstigt werden, die auch zur Unterstützung der Separation sowie zur Regelung des Flüssigkeitsstandes im Druckraum 11 dienen können. Der Anschluß der Flüssigkeits-Kurzschlußleitung 14 am Druckraum 11 sollte so tief angeordnet sein, daß permanenter Flüssigkeits¬ umlauf (unter Vermeidung von Gaseintritt) gewährleistet ist. Dieser Separationsgrad läßt sich anhand der Gehäuse und Strö- mungskonfiguration bestimmen. Dabei hat es sich als zweckmäßig erwiesen, etwa 3 % des normalen Förderstromes im Flüssigkeits¬ umlauf zu halten. Der dadurch im Pumpengehäuse 3 bzw. im Druck¬ raum 11 sichergestellte Flüssigkeitspegel kann in der Regel unterhalb der Wellen 7,8 liegen. Die Benetzung der Wellendich- tungen 12 in Folge der direkten Anströmung reicht in der Regel für eine ausreichende Schmierung der Wellendichtungen 12 aus. Nur bei besonders empfindlichen Dichtungsmaterialien ist eine permanente Umspülung der Wellendichtungen 12 erforderlich. In diesem Fall empfiehlt sich eine horizontale Anordnung der beiden Wellen 7,8 nebeneinander und ein entsprechend höherer Flüssig¬ keitspegel im Druckraum 11.It is clear from the drawing that the liquid phase of the medium 9 emerging from the feed screw 1, 2 is guided against the associated shaft seal 12 and then reaches the connection area of the liquid short-circuit line 14 due to gravity. By increasing the flow cross-section of the pressure chamber 11, the flow velocity of the emerging medium is reduced, whereby the separation of the liquid phase from the conveyed mixture is favored. The supply of the liquid phase into the connection area of the liquid short-circuit line 14 can be favored by flow guide devices 17 which are only shown schematically in the drawing and which can also serve to support the separation and to regulate the liquid level in the pressure chamber 11. The connection of the liquid short-circuit line 14 to the pressure chamber 11 should be arranged so deep that permanent liquid circulation is ensured (while avoiding gas entry). This degree of separation can be determined based on the housing and flow configuration. It has proven expedient to keep about 3% of the normal flow in the liquid circulation. The liquid level thereby ensured in the pump housing 3 or in the pressure chamber 11 can generally be below the waves 7, 8. The wetting of the shaft seals 12 as a result of the direct inflow is generally sufficient for sufficient lubrication of the shaft seals 12. Permanent flushing of the shaft seals 12 is required only in the case of particularly sensitive sealing materials. In this case, a horizontal arrangement of the two shafts 7, 8 next to one another and a correspondingly higher liquid level in the pressure chamber 11 are recommended.
Ein Umlauf der Förderelemente mit ausreichend spaltabdichtender Flüssigkeit ist aufgrund der erfindungsgemäßen Flüssigkeits- Kurzschlußleitung 14 auch dann gewährleistet, wenn die beiden Wellen 7,8 in einer lotrechten Ebene übereinanderliegen. Denn die am Zahnkopf der unteren Förderschraube anhaftende Flüssig¬ keit wird in den Zahngrund der oberen Förderschraube geschleu¬ dert und wandert dann aufgrund der Fliehkraft an deren Flanken entlang zum Zahnkopf. Eingriff und Zahnkopf bleiben dadurch permanent benetzt. Diese Mini albenetzung der schädlichen Spalte reicht bereits zur Aufrechterhaltung der Förderung aus.A circulation of the conveying elements with sufficient gap-sealing liquid is also ensured due to the liquid short-circuit line 14 according to the invention if the two shafts 7, 8 lie one above the other in a vertical plane. This is because the liquid adhering to the tooth head of the lower feed screw is flung into the tooth base of the upper feed screw and then migrates along the flanks of the top to the tooth head due to the centrifugal force. As a result, the mesh and tooth head remain permanently wetted. This mini wetting of the harmful column is already sufficient to maintain the funding.
Zur Dosierung des Flüssigkeitsumlaufes kann in die Flüssigkeits- Kurzschlußleitung 14 eine entsprechend dimensionierte Blende 18 geschaltet sein.A correspondingly dimensioned orifice 18 can be connected to the liquid short-circuit line 14 for metering the liquid circulation.
Da der erfindungsgemäß vorgesehene Flüssigkeitsumlauf nur dann vorteilhaft ist, wenn die Flüssigkeitsphase des zu fördernden Mediums nicht ausreicht, kann dieser Flüssigkeitsumlauf ggf. bei Bedarf zuschaltbar sein, beispielsweise durch eine Temperatur¬ steuerung. Figur 3 zeigt in schematischer Darstellung einen Querschnitt durch ein konventionelles Pumpengehäuse, das ebenfalls zum Ein¬ bau von zwei gegenläufigen Förderschraubenpaaren gemäß Figur 1 bestimmt ist. Hier erfolgt die Flüssigkeitsförderung axial gese- hen jeweils von außen zur Pumpenmitte in einen den Förderschrau¬ ben jeweils unmittelbar nachgeschalteten Druckraum 11, der in einen etwa mittig im Pumpengehäuse angeordneten Druckschlitz 16 übergeht. Die Strömungsgeschwindigkeit im Druckraum 11 und Druckschlitz 16 in der Pumpenmitte liegt bei derartigen Ausfüh- rungsformen bei etwa 3 bis 8 m/s. Bei Gasförderung wird die Restflüssigkeit im Druckraum 11 durch Mitreißen im Gas und Ver¬ dampfung durch Kompressions- und Reibungswärme in kurzer Zeit ausgetragen.Since the liquid circulation provided according to the invention is only advantageous if the liquid phase of the medium to be conveyed is not sufficient, this liquid circulation can be switched on if necessary, for example by a temperature control. Figure 3 shows a schematic representation of a cross section through a conventional pump housing, which is also intended for the installation of two opposing pairs of feed screws according to Figure 1. Here, the fluid is conveyed axially, seen from the outside towards the center of the pump, into a pressure chamber 11, which is directly downstream of the delivery screws and which merges into a pressure slot 16 arranged approximately centrally in the pump housing. The flow velocity in the pressure chamber 11 and pressure slot 16 in the middle of the pump in such embodiments is approximately 3 to 8 m / s. When gas is pumped, the residual liquid in the pressure chamber 11 is discharged in a short time by being carried away in the gas and evaporated by the heat of compression and friction.
Demgegenüber zeigt die in Figur 2 dargestellte erfindungsgemäße Konstruktion, daß sich der Druckraum 11 im Pumpengehäuse 3 auch unterhalb der Förderschraubenpaare bzw. der von ihnen zusammen mit dem sie umschließenden Gehäuse gebildeten Förderkammern erstreckt. Der Druckraum 11 ist somit so gestaltet, daß in sei- nem unteren Teil die Strömungsgeschwindigkeit des druckseitig aus der Förderschraube austretenden Förderstroms gegen Null geht. Hierdurch erfolgt aufgrund der Dichtedifferenz eine Tren¬ nung der Flüssigkeits- von der Gasphase.In contrast, the construction according to the invention shown in FIG. 2 shows that the pressure chamber 11 in the pump housing 3 also extends below the pairs of delivery screws or the delivery chambers formed by them together with the housing surrounding them. The pressure chamber 11 is thus designed in such a way that in its lower part the flow velocity of the delivery flow emerging from the delivery screw on the pressure side goes to zero. This results in a separation of the liquid from the gas phase due to the density difference.
Die in Figur 2 dargestellte Konfiguration ist sowohl bei mit¬ tigem als auch seitlichem Druckraum möglich. The configuration shown in FIG. 2 is possible both with a central and lateral pressure space.

Claims

Ansprüche Expectations
1. Pumpverfahren zum Betreiben einer Multiphasen-Schrauben- spindelpumpe mit zumindest einer Förderschraube, die von einem Gehäuse umschlossen ist, das zumindest einen Saug¬ stutzen und zumindest einen Druckstutzen aufweist, wobei das angesaugte Medium in einem pulsationsarmen kontinuier¬ lichen Förderstrom parallel zu der Schraubenwelle fort- bewegt und im Druckstutzen kontinuierlich ausgestoßen wird, dadurch gekennzeichnet, daß druckseitig die jeweilige Flüs¬ sigkeitsphase von der Gasphase separiert wird, indem der aus der Förderschraube austretende Mediumstrom in seiner Strömungsgeschwindigkeit reduziert und/oder in seiner Strö- mungsrichtung gezielt umgelenkt wird, daß aus der so sepa¬ rierten Flüssigkeitsphase ein Teil-Flüssigkeitsvolumenstrom (Flüssigkeitsumlauf) entnommen, dosiert in den Ansaugbe¬ reich zurückgeführt und so in Umlauf gehalten wird, und daß der überschüssige Flüssigkeitsvolumenstrom im Be- reich des Druckstutzens wieder mit der zuvor separierten Gasphase zusammengeführt wird.1. Pumping method for operating a multi-phase screw pump with at least one feed screw which is enclosed by a housing which has at least one suction port and at least one pressure port, the medium drawn in in a low-pulsation continuous flow parallel to the screw shaft is moved and continuously ejected in the pressure port, characterized in that the respective liquid phase is separated from the gas phase on the pressure side by reducing the flow velocity of the medium flow emerging from the delivery screw and / or specifically deflecting it in its flow direction in such a way that a partial liquid volume flow (liquid circulation) is removed from the thus separated liquid phase, metered back into the suction area and kept in circulation, and that the excess liquid volume flow in the area of the pressure port is again separated with that previously ized gas phase is brought together.
2. Pumpverfahren nach Anspruch 1, dadurch gekennzeichnet, daß die Dosierung des Flüssigkeitsumlaufs in Abhängigkeit von dem Pumpendifferenzdruck erfolgt.2. Pumping method according to claim 1, characterized in that the metering of the liquid circulation takes place as a function of the pump differential pressure.
3. Pumpverfahren nach Anspruch 1 oder 2, dadurch gekenn¬ zeichnet, daß etwa 3 % des normalen Förderstromes im Flüssigkeitsumlauf gehalten wird. 3. Pumping method according to claim 1 or 2, characterized gekenn¬ characterized in that about 3% of the normal flow rate is kept in liquid circulation.
4. Pumpverfahren nach Anspruch 1,2 oder 3, dadurch gekenn¬ zeichnet, daß die Strömungsgeschwindigkeit des druckseitig aus der Förderschraube austretenden Mediums reduziert wird.4. Pumping method according to claim 1, 2 or 3, characterized in that the flow velocity of the medium escaping from the delivery screw on the pressure side is reduced.
5. Pumpverfahren zum Betreiben einer Multiphasen-Schrauben- spindelpumpe mit doppelflutig angeordneten Förderelementen mit Außenlagerung, nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die beiden Teilströme von der jeweiligen Saugseite in entgegengesetzten, voneinander weggerichteten Förderrichtungen zur Druckseite und von dort in Richtung der zugeordneten Wellendichtung gefördert wer¬ den.5. Pumping method for operating a multi-phase screw pump with double-flow conveying elements with external storage, according to one of the preceding claims, characterized in that the two partial flows from the respective suction side in opposite, away from each other conveying directions to the pressure side and from there in the direction of the associated Shaft seal are promoted.
6. Multiphasen-Schraubenspindelpumpe mit zumindest einer För¬ derschraube (1,2), die von einem Gehäuse (3) umschlossen ist, das zumindest einen Saugstutzen (5) und zumindest einen Druckstutzen (6) aufweist, wobei der Saugstutzen (5) mit einem der Förderschraube (1,2) vorgeschalteten Saugraum (10) und der Druckstutzen (6) mit einem der Förderschraube (1,2) nachgeordneten Druckraum (11) in Verbindung stehen, insbesondere zur Ausübung eines Verfahrens gemäß einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß der Druckraum (11) Einrichtungen zur Separierung der jeweiligen Flüssigkeitsphase von der Gasphase des aus der Förder¬ schraube (1,2) austretenden Mediumstromes sowie einen unte¬ ren Abschnitt zur Aufnahme von zumindest einer Teilmenge der separierten Flüssigkeitsphase aufweist, und daß an diesem unteren Druckraumabschnitt, in dem die Strömungsgeschwindigkeit gegen Null geht, eine Flüssig¬ keits-Kurzschlußleitung (14) angeschlossen ist, die mit dem Saugraum (10) in Verbindung steht und zusammen mit den Förderelementen einen geschlossenen Umlauf für eine zur permanenten Abdichtung erforderlichen Flüssigkeitsmenge bildet.6. Multi-phase screw pump with at least one feed screw (1, 2) which is enclosed by a housing (3) which has at least one suction nozzle (5) and at least one pressure nozzle (6), the suction nozzle (5) also one of the feed screw (1, 2) upstream suction chamber (10) and the pressure port (6) are connected to a feed screw (1, 2) downstream pressure chamber (11), in particular for carrying out a method according to one of the preceding claims, characterized that the pressure chamber (11) has devices for separating the respective liquid phase from the gas phase of the medium stream emerging from the delivery screw (1, 2) and a lower section for receiving at least a partial amount of the separated liquid phase, and that on this lower pressure chamber section, in which the flow velocity approaches zero, a liquid short-circuit line (14) is connected, which is connected to the suction Room (10) is connected and forms a closed circuit together with the conveyor elements for a quantity of liquid required for permanent sealing.
7. Multiphasen-Schraubenspindelpumpe nach Anspruch 6, dadurch gekennzeichnet, daß die Flüssigkeits-Kurzschlußleitung (14) einen in Abhängigkeit vom Pumpendifferenzdruck dimen¬ sionierten Strömungsquerschnitt aufweist.7. Multi-phase screw pump according to claim 6, characterized in that the liquid short-circuit line (14) has a flow cross section dimensioned as a function of the pump differential pressure.
8. Multiphasen-Schraubenspindelpumpe nach Anspruch 6, dadurch gekennzeichnet, daß in die Flüssigkeits-Kurzschlußleitung (14) eine Dosierpumpe geschaltet ist.8. Multi-phase screw pump according to claim 6, characterized in that in the liquid short-circuit line (14) a metering pump is connected.
9. Multiphasen-Schraubenspindelpumpe nach Anspruch 6, dadurch gekennzeichnet, daß in die Flüssigkeits-Kurzschlußleitung (14) ein temperaturgesteuertes Ventil geschaltet ist.9. Multi-phase screw pump according to claim 6, characterized in that a temperature-controlled valve is connected in the liquid short-circuit line (14).
10. Multiphasen-Schraubenspindelpumpe nach einem der Ansprüche 6 bis 9, dadurch gekennzeichnet, daß der Druckstutzen' (6) auf der Oberseite des Gehäuses (3) angeordnet ist.10. Multi-phase screw pump according to one of claims 6 to 9, characterized in that the pressure port '(6) is arranged on the top of the housing (3).
11. Multiphasen-Schraubenspindelpumpe nach einem der Ansprüche 6 bis 10, dadurch gekennzeichnet, daß die Flüssigkeits- Kurzschlußleitung (14) am tiefsten Punkt des Druckraumes (11) angeschlossen ist.11. Multi-phase screw pump according to one of claims 6 to 10, characterized in that the liquid short-circuit line (14) is connected to the lowest point of the pressure chamber (11).
12. Multiphasen-Schraubenspindelpumpe mit zwei parallel zuein¬ ander angeordneten Wellen (7,8), die mit je zwei einander gegenläufigen Förderschrauben (1,2) bestückt sind und je¬ weils eine Außenlagerung (13) aufweisen, wobei das der Pumpe durch den Saugstutzen (5) zufließende Medium (9) im Pumpengehäuse (3) in zwei Teilströmen den beiden Saugräumen (10) zugeführt wird, nach einem der Ansprüche 6 bis 11, dadurch gekennzeichnet, daß die Saugräume (10) mittig lie¬ gen und die Druckräume (11) axial nach außen durch jeweils eine Wellendichtung (12) abgeschlossen sind.12. Multi-phase screw pump with two shafts (7, 8) arranged in parallel to each other, which are each equipped with two counter-rotating feed screws (1, 2) and each have an external bearing (13), the pump being driven by the Medium (9) flowing into the suction nozzle (5) in the pump housing (3) is supplied to the two suction spaces (10) in two partial flows, according to one of claims 6 to 11, characterized in that the suction spaces (10) lie centrally and the pressure spaces (11) are axially closed to the outside by a shaft seal (12).
13. Multiphasen-Schraubenspindelpumpe nach einem der Ansprüche 6 bis 12, dadurch gekennzeichnet, daß der Druckraum (11) einen sich in Durchströmrichtung des Mediums (9) gesehen vergrößernden Querschnitt aufweist. 13. Multi-phase screw pump according to one of claims 6 to 12, characterized in that the pressure chamber (11) has an enlarged cross-section seen in the flow direction of the medium (9).
14. Multiphasen-Schraubenspindelpumpe nach einem der Ansprüche 6 bis 13, dadurch gekennzeichnet, daß im Druckraum (11) Strömungsleiteinrichtungen (17) vorgesehen sind, die die aus der Förderschraube (1,2) austretende Flüssigkeitsphase des Mediums (9) gegen die zugeordnete Wellendichtung (12) und nachfolgend dem Anschlußbereich der Flüssigkeits-Kurz¬ schlußleitung (14) zuführen.14. Multi-phase screw pump according to one of claims 6 to 13, characterized in that flow guide devices (17) are provided in the pressure chamber (11), the liquid phase emerging from the screw (1, 2) of the medium (9) against the associated shaft seal (12) and subsequently lead to the connection area of the liquid short-circuit line (14).
15. Multiphasen-Schraubenspindelpumpe nach einem der Ansprüche 6 bis 14, dadurch gekennzeichnet, daß zur Unterstützung der Separation im Druckraum (11) Strömungsleiteinrichtungen (17) vorgesehen sind.15. Multi-phase screw pump according to one of claims 6 to 14, characterized in that flow guide devices (17) are provided to support the separation in the pressure chamber (11).
16. Multiphasen-Schraubenspindelpumpe nach einem der Ansprüche 6 bis 15, dadurch gekennzeichnet, daß zur Regelung des Flüssigkeitsstandes im Druckraum (11) Strömungsleiteinrich¬ tungen (17) vorgesehen sind.16. Multi-phase screw pump according to one of claims 6 to 15, characterized in that for regulating the liquid level in the pressure chamber (11) flow guide devices (17) are provided.
17. Multiphasenschraubenspindelpumpe nach einem der Ansprüche17. Multi-phase screw pump according to one of the claims
6 bis 16, dadurch gekennzeichnet, daß zur Dosierung des6 to 16, characterized in that for metering the
Flüssigkeitsumlaufes in die Flüssigkeits-KurzschlußleitungLiquid circulation in the liquid short-circuit line
(14) eine entsprechend dimensionierte Blende (18) geschal- tet ist. (14) an appropriately dimensioned diaphragm (18) is switched.
EP94913479A 1993-05-19 1994-04-28 Pumping process for operating a multi-phase screw pump and pump Expired - Lifetime EP0699276B1 (en)

Applications Claiming Priority (3)

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DE4316735A DE4316735C2 (en) 1993-05-19 1993-05-19 Pumping method for operating a multi-phase screw pump and pump
DE4316735 1993-05-19
PCT/DE1994/000477 WO1994027049A1 (en) 1993-05-19 1994-04-28 Pumping process for operating a multi-phase screw pump and pump

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EP0699276A1 true EP0699276A1 (en) 1996-03-06
EP0699276B1 EP0699276B1 (en) 1997-02-05

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2005045189A1 (en) * 2003-10-27 2005-05-19 Joh. Heinr. Bornemann Gmbh Method for delivering a multi-phase mixture and pump installation
US7810572B2 (en) 2003-10-27 2010-10-12 Joh. Heinr. Bornemann Gmbh Method for delivering a multi phase mixture and pump installation
US7862315B2 (en) 2005-06-02 2011-01-04 Joh.Heinr.Bornemann Gmbh Screw displacement pump

Also Published As

Publication number Publication date
DE4316735A1 (en) 1994-11-24
NO953234L (en) 1995-08-17
WO1994027049A1 (en) 1994-11-24
JPH09500701A (en) 1997-01-21
DE4316735C2 (en) 1996-01-18
NO306077B1 (en) 1999-09-13
CA2153385C (en) 2001-05-22
DE59401773D1 (en) 1997-03-20
RU2101571C1 (en) 1998-01-10
BR9406532A (en) 1996-01-02
AU6562994A (en) 1994-12-12
NO953234D0 (en) 1995-08-17
JP3655306B2 (en) 2005-06-02
ATE148772T1 (en) 1997-02-15
KR960701303A (en) 1996-02-24
KR100301419B1 (en) 2001-11-22
US5624249A (en) 1997-04-29
CA2153385A1 (en) 1994-11-24
EP0699276B1 (en) 1997-02-05

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