EP0699276B1 - Procede de pompage permettant d'actionner une pompe a broche helicoidale multiphase et pompe correspondante - Google Patents

Procede de pompage permettant d'actionner une pompe a broche helicoidale multiphase et pompe correspondante Download PDF

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Publication number
EP0699276B1
EP0699276B1 EP94913479A EP94913479A EP0699276B1 EP 0699276 B1 EP0699276 B1 EP 0699276B1 EP 94913479 A EP94913479 A EP 94913479A EP 94913479 A EP94913479 A EP 94913479A EP 0699276 B1 EP0699276 B1 EP 0699276B1
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EP
European Patent Office
Prior art keywords
liquid
phase
flow
delivery
screw pump
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP94913479A
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German (de)
English (en)
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EP0699276A1 (fr
Inventor
Gerhard Rohlfing
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ITT Bornemann GmbH
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Joh Heinr Bornemann GmbH
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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 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 a low-pulsation continuous flow moving parallel to the screw shaft and in the pressure port is continuously ejected, the respective liquid phase being separated from the gas phase on the pressure side by reducing the flow rate of the medium flow emerging from the delivery screw and / or specifically deflecting it in its flow direction.
  • 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 being connected to a suction space upstream of the feed screw and the pressure port being connected to a pressure space downstream of the feed screw stand, especially for exercise of a method according to one of the preceding claims, wherein the pressure chamber has devices for separating the respective liquid phase from the gas phase of the medium stream emerging from the screw and a lower section for receiving at least a partial amount of the separated liquid phase.
  • Multiphase is to be understood as 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 run around without 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.
  • the invention has for its object to improve the pumping method described above and the multi-phase screw pump described above so that neither extremely high gas content nor longer dry-running phases lead to an interruption in delivery or damage.
  • a liquid short-circuit line is connected to this lower pressure chamber section, in which the flow velocity approaches zero, which is connected to the suction chamber and together with the conveying elements, a closed circuit for a permanent Sealing forms the required amount of liquid.
  • the delivery flow emerging from the delivery screw on the delivery side is thus separated into its liquid phase and into its gas phase, the phase division present in the delivery flow remaining unchanged, i.e. the separation of the percentage of the phase in the total volume should not be changed.
  • it is further provided to branch off a certain partial quantity from the liquid phase separated on the pressure side and to keep it in a permanent circulation through the pump chamber by returning it to the suction area, in order to ensure sufficient gap sealing there even if the suctioned pumped medium is only a very slight or even at all has no liquid phase.
  • the degree of separation required to achieve the stated task 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 flow rate 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 guide 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 associated shaft seal and subsequently to the connection area of the liquid short-circuit line.
  • the screw spindle pump shown in FIG. 1 has, as conveying elements, two contactless, opposing pairs of conveying screws which mesh with one another without contact, each of which comprises a right-handed screw 1 and a left-handed screw 2.
  • the axial thrust is balanced by this two-flow arrangement.
  • the torque is transmitted from the drive shaft to the driven shaft 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 top 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 discharge ports 5, 6 have been Lich 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. Downstream of these feed screws 1, 2 is a pressure chamber 11, which is closed axially outwards by a shaft seal 12, which is used 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 from the suction chamber 10 into the pressure chamber 11 as a liquid circulation.
  • connection of the liquid short-circuit line 14 to the pressure chamber 11 should be arranged so deep that permanent liquid circulation (while avoiding gas entry) is ensured. This degree of separation can be determined from the housing and flow configuration. It has proven to be useful 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 1 below the shafts 7, 8.
  • 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. Because the liquid adhering to the tooth head of the lower feed screw is thrown into the tooth base of the upper feed screw and then migrates along its flanks to the tooth head due to the centrifugal force. As a result, the mesh and tooth head remain permanently wetted. This minimal wetting of the harmful gaps is 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.
  • 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.
  • the fluid is conveyed axially from the outside to the center of the pump into a pressure chamber 11, which is directly downstream of the delivery screws and 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.

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  • 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)

Claims (17)

  1. Procédé de pompage pour faire fonctionner une pompe à vis multiphase comprenant au moins une vis transporteuse entourée par un carter qui présente au moins un raccord d'aspiration et au moins un raccord de refoulement, dans laquelle le milieu aspiré est entraîné en un flux de transport continu faiblement pulsé parallèlement à l'arbre de vis et se trouve refoulé dans le raccord de refoulement, procédé dans lequel, du côté du refoulement, on sépare la phase liquide de la phase gazeuse par changement approprié de la direction d'écoulement et/ou réduction de la vitesse d'écoulement du flux du milieu sortant de la vis transporteuse, caractérisé en ce qu'on prélève dans la phase liquide ainsi séparée un flux volumique liquide partiel (recirculation de liquide), que l'on renvoie de manière dosée dans la zone d'aspiration et que l'on maintient ainsi en circulation, et en ce qu'on recombine avec la phase gazeuse précédemment séparée le flux volumique liquide excédentaire dans la zone du raccord de refoulement.
  2. Procédé de pompage selon la revendication 1, caractérisé en ce que le dosage de la recirculation de liquide a lieu en fonction de la pression différentielle de la pompe.
  3. Procédé de pompage selon la revendication 1 ou 2, caractérisé en ce qu'on maintient en recirculation de liquide environ 3% du flux de transport normal.
  4. Procédé de pompage selon la revendication 1, 2 ou 3, caractérisé en ce qu'on réduit la vitesse d'écoulement du milieu sortant de la vis transporteuse du côté du refoulement.
  5. Procédé de pompage pour faire fonctionner une pompe à vis multiphase comprenant des éléments transporteurs agencés en double flux avec paliers extérieurs, selon l'une des revendications précédentes, caractérisé en ce que les deux flux partiels sont transportés dans deux directions de transport opposées, s'écartant l'une de l'autre vers le côté du refoulement, puis de là dans la direction de l'étanchéité d'arbre associée.
  6. Pompe à vis multiphase comprenant au moins une vis de transporteuse (1, 2) entourée par un carter (3) qui présente au moins un raccord d'aspiration (5) et au moins un raccord de refoulement (6), le raccord d'aspiration (5) étant en liaison avec un espace d'aspiration (10) monté en amont de la vis transporteuse (1, 2), et le raccord de refoulement (6) avec un espace de refoulement (11) monté en aval de la vis transporteuse (1, 2), en particulier pour la mise en oeuvre d'un procédé selon l'une des revendications précédentes, l'espace de refoulement (11) présentant des moyens pour séparer la phase liquide de la phase gazeuse du flux de milieu sortant de la vis transporteuse (1, 2) ainsi qu'une partie inférieure pour collecter au moins une quantité partielle de la phase liquide séparée, caractérisée en ce qu'à cette partie inférieure de l'espace de refoulement, dans laquelle la vitesse d'écoulement tend vers zéro, est raccordée une conduite de court-circuit de liquide (14) qui est en liaison avec l'espace d'aspiration (10) et constitue avec les éléments transporteurs un circuit fermé pour une quantité de liquide nécessaire pour l'étanchéité permanente.
  7. Pompe à vis multiphase selon la revendication 6, caractérisée en ce que la conduite formant court-circuit de liquide (14) présente une section d'écoulement dimensionnée en fonction de la pression différentielle de la pompe.
  8. Pompe à vis multiphase selon la revendication 6, caractérisée en ce que dans la conduite formant court-circuit de liquide (14) est montée une pompe doseuse.
  9. Pompe à vis multiphase selon la revendication 6, caractérisée en ce que dans la conduite formant court-circuit de liquide (14) est montée une soupape commandée en fonction en de la température.
  10. Pompe à vis multiphase selon l'une des revendications 6 à 9, caractérisée en que le raccord de refoulement (6) est disposé du côté supérieur du carter (3).
  11. Pompe à vis multiphase selon l'une des revendications 6 à 10, caractérisée en ce que la conduite formant court-circuit de liquide (14) est raccordée au point le plus bas de l'espace de refoulement (11).
  12. Pompe à vis multiphase comprenant deux arbres (7, 8) disposés parallèlement l'un à l'autre, qui sont équipés chacun de deux vis transporteuses fonctionnant en opposition l'une par rapport à l'autre et présentent chacun un système de palier extérieur (13), dans laquelle le milieu (9) coulant vers la pompe à travers les raccord d'aspiration (5) est acheminé, dans le carter de pompe (3), en deux flux partiels aux deux espaces d'aspiration (10), selon l'une des revendications 6 à 11, caractérisée en ce que les espaces d'aspiration (10) s'étendent en position médiane et les espaces de refoulement (11) sont fermés axialement vers l'extérieur chacun par une étanchéité d'arbre (12).
  13. Pompe à vis multiphase selon l'une des revendications 6 à 12, caractérisée en ce que l'espace de refoulement (11) présente une section qui croît dans la direction d'écoulement du milieu (9).
  14. Pompe à vis multiphase selon l'une des revendications 6 à 13, caractérisée en ce que dans l'espace de refoulement (11) il est prévu des moyens de guidage d'écoulement (17) qui conduisent la phase liquide du milieu (9) sortant de la vis transporteuse (1, 2), jusque contre l'étanchéité d'arbre associée (12) puis à la zone de raccordement de la conduite formant court-circuit de liquide (14).
  15. Pompe à vis multiphase selon l'une des revendications 6 à 14, caractérisée en ce que dans l'espace de refoulement (11) il est prévu des moyens de guidage d'écoulement (17) pour favoriser la séparation.
  16. Pompe à vis multiphase selon l'une des revendications 6 à 15, caractérisée en ce que dans l'espace de refoulement (11) il est prévu des moyens de guidage d'écoulement (17) dans l'espace haute pression (11) pour la régulation du niveau de liquide.
  17. Pompe à vis multiphase selon l'une des revendications 6 à 16, caractérisée en ce que pour le dosage de la circulation de liquide dans la conduite formant court-circuit de liquide (14) est monté un obturateur partiel (18) dimensionné de manière correspondante.
EP94913479A 1993-05-19 1994-04-28 Procede de pompage permettant d'actionner une pompe a broche helicoidale multiphase et pompe correspondante Expired - Lifetime EP0699276B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4316735 1993-05-19
DE4316735A DE4316735C2 (de) 1993-05-19 1993-05-19 Pumpverfahren zum Betreiben einer Multiphasen-Schraubenspindelpumpe und Pumpe
PCT/DE1994/000477 WO1994027049A1 (fr) 1993-05-19 1994-04-28 Procede de pompage permettant d'actionner une pompe a broche helicoidale multiphase et pompe correspondante

Publications (2)

Publication Number Publication Date
EP0699276A1 EP0699276A1 (fr) 1996-03-06
EP0699276B1 true EP0699276B1 (fr) 1997-02-05

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EP94913479A Expired - Lifetime EP0699276B1 (fr) 1993-05-19 1994-04-28 Procede de pompage permettant d'actionner une pompe a broche helicoidale multiphase et pompe correspondante

Country Status (12)

Country Link
US (1) US5624249A (fr)
EP (1) EP0699276B1 (fr)
JP (1) JP3655306B2 (fr)
KR (1) KR100301419B1 (fr)
AT (1) ATE148772T1 (fr)
AU (1) AU6562994A (fr)
BR (1) BR9406532A (fr)
CA (1) CA2153385C (fr)
DE (2) DE4316735C2 (fr)
NO (1) NO306077B1 (fr)
RU (1) RU2101571C1 (fr)
WO (1) WO1994027049A1 (fr)

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DE10350226A1 (de) * 2003-10-27 2005-07-21 Joh. Heinr. Bornemann Gmbh Verfahren zur Förderung von Multiphasengemischen sowie Pumpenanlage
DE102005025816A1 (de) * 2005-06-02 2006-12-07 Joh. Heinrich Bornemann Gmbh & Co Kg Schraubenspindelpumpe
CN109578271A (zh) * 2018-09-18 2019-04-05 莱斯特里兹泵吸有限责任公司 螺杆泵

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DE102012015064B4 (de) 2012-07-31 2018-08-02 Joh. Heinr. Bornemann Gmbh Verfahren zum Betreiben einer Multiphasenpumpe und Vorrichtung dazu
KR101579676B1 (ko) * 2014-03-18 2015-12-23 한국기계연구원 다상유동 펌프 시험장치
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KR102583846B1 (ko) * 2019-03-14 2023-09-27 아뜰리에 부쉬 에스.아. 기체용 건식 펌프 및 다수의 기체용 건식 펌프들의 세트
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DD290241A5 (de) * 1989-11-15 1991-05-23 Veb Kombinat Pumpen Und Verdichter,De Schraubenpumpe
US5348453A (en) * 1990-12-24 1994-09-20 James River Corporation Of Virginia Positive displacement screw pump having pressure feedback control

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10350226A1 (de) * 2003-10-27 2005-07-21 Joh. Heinr. Bornemann Gmbh Verfahren zur Förderung von Multiphasengemischen sowie Pumpenanlage
DE10350226B4 (de) * 2003-10-27 2005-11-24 Joh. Heinr. Bornemann Gmbh Verfahren zur Förderung von Multiphasengemischen sowie Pumpenanlage
CN1867753B (zh) * 2003-10-27 2010-09-22 约翰·海因里希·波内曼有限公司 用于输送多相混合物的方法和泵装置
DE102005025816A1 (de) * 2005-06-02 2006-12-07 Joh. Heinrich Bornemann Gmbh & Co Kg Schraubenspindelpumpe
DE102005025816B4 (de) * 2005-06-02 2010-06-02 Joh. Heinr. Bornemann Gmbh Schraubenspindelpumpe
CN109578271A (zh) * 2018-09-18 2019-04-05 莱斯特里兹泵吸有限责任公司 螺杆泵

Also Published As

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JP3655306B2 (ja) 2005-06-02
NO953234D0 (no) 1995-08-17
US5624249A (en) 1997-04-29
NO953234L (no) 1995-08-17
DE4316735A1 (de) 1994-11-24
RU2101571C1 (ru) 1998-01-10
KR100301419B1 (ko) 2001-11-22
BR9406532A (pt) 1996-01-02
ATE148772T1 (de) 1997-02-15
CA2153385A1 (fr) 1994-11-24
KR960701303A (ko) 1996-02-24
DE59401773D1 (de) 1997-03-20
NO306077B1 (no) 1999-09-13
JPH09500701A (ja) 1997-01-21
DE4316735C2 (de) 1996-01-18
EP0699276A1 (fr) 1996-03-06
CA2153385C (fr) 2001-05-22
AU6562994A (en) 1994-12-12
WO1994027049A1 (fr) 1994-11-24

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