EP0699276B1 - Pumpverfahren zum betreiben einer multiphasen-schraubenspindelpumpe und pumpe - Google Patents

Pumpverfahren zum betreiben einer multiphasen-schraubenspindelpumpe und pumpe 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
Authority
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)
French (fr)
Other versions
EP0699276A1 (de
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
Priority date (The priority date 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 date listed.)
Filing date
Publication date
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First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=6488452&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0699276(B1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Joh Heinr Bornemann GmbH filed Critical Joh Heinr Bornemann GmbH
Publication of EP0699276A1 publication Critical patent/EP0699276A1/de
Application granted granted Critical
Publication of EP0699276B1 publication Critical patent/EP0699276B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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.

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)
EP94913479A 1993-05-19 1994-04-28 Pumpverfahren zum betreiben einer multiphasen-schraubenspindelpumpe und pumpe Expired - Lifetime EP0699276B1 (de)

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 (de) 1993-05-19 1994-04-28 Pumpverfahren zum betreiben einer multiphasen-schraubenspindelpumpe und pumpe

Publications (2)

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

Family

ID=6488452

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94913479A Expired - Lifetime EP0699276B1 (de) 1993-05-19 1994-04-28 Pumpverfahren zum betreiben einer multiphasen-schraubenspindelpumpe und pumpe

Country Status (12)

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

Cited By (3)

* 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
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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DE19519247C2 (de) * 1995-05-25 2000-08-31 Guenter Kirsten Schraubenverdichter
US5871340A (en) * 1995-06-05 1999-02-16 Hatton; Gregory John Apparatus for cooling high-pressure boost high gas-fraction twin-screw pumps
US6039059A (en) * 1996-09-30 2000-03-21 Verteq, Inc. Wafer cleaning system
ATE230070T1 (de) * 1998-04-11 2003-01-15 Bornemann J H Gmbh Spaltringdichtung
EP1026399A1 (de) 1999-02-08 2000-08-09 Ateliers Busch S.A. Zwillings-Förderschrauben
US6457950B1 (en) 2000-05-04 2002-10-01 Flowserve Management Company Sealless multiphase screw-pump-and-motor package
WO2002033262A1 (en) 2000-10-18 2002-04-25 Leybold Vakuum Gmbh Multi-stage helical screw rotor
MXPA03005600A (es) * 2000-12-21 2003-10-06 Procter & Gamble Copolimeros de polhidroxialcanoato biodegradables que tienen propiedades de cristalizacion mejoradas.
JP4122405B2 (ja) * 2000-12-21 2008-07-23 メリディアン インコーポレイテッド 改善された結晶化特性を有する生分解性ポリヒドロキシアルカノエートコポリマーの製造方法
US7963832B2 (en) * 2006-02-22 2011-06-21 Cummins Inc. Engine intake air temperature management system
US7569097B2 (en) * 2006-05-26 2009-08-04 Curtiss-Wright Electro-Mechanical Corporation Subsea multiphase pumping systems
US20090098003A1 (en) * 2007-10-11 2009-04-16 General Electric Company Multiphase screw pump
US7708059B2 (en) * 2007-11-13 2010-05-04 Baker Hughes Incorporated Subsea well having a submersible pump assembly with a gas separator located at the pump discharge
JP4365443B1 (ja) * 2008-07-29 2009-11-18 株式会社神戸製鋼所 無給油式スクリュ圧縮機
US8419398B2 (en) * 2009-04-30 2013-04-16 General Electric Company Method and apparatus for managing fluid flow within a screw pump system
US20100278671A1 (en) * 2009-04-30 2010-11-04 General Electric Company Method and apparatus for reducing particles in a screw pump lubricant
US20110103987A1 (en) * 2009-11-04 2011-05-05 General Electric Company Pump system
US20110158841A1 (en) * 2009-12-28 2011-06-30 Sunny King Machinery Co., Ltd. Screw Pump with Anti-Turbulent Structure
CN101793251A (zh) * 2010-03-15 2010-08-04 西安交通大学 一种对称串联式三转子螺杆压缩机
DE102011011404B4 (de) 2011-02-16 2012-08-30 Joh. Heinr. Bornemann Gmbh Zweiflutige Schraubspindelmaschine
RU2456477C1 (ru) * 2011-03-30 2012-07-20 Юрий Рэмович Залыгин Многофазный роторно-лопастной насос и способ его эксплуатации
EP2574790A1 (en) 2011-09-30 2013-04-03 Vetco Gray Scandinavia AS A priming liquid supply system for a sub-sea pump or compressor
DE202012003018U1 (de) 2012-01-31 2012-04-19 Jung & Co. Gerätebau GmbH Zweispindelige Schraubenspindelpumpe in zweiflutiger Bauweise
DE102012005949B4 (de) 2012-01-31 2013-09-12 Jung & Co. Gerätebau GmbH Zweispindelige Schraubenspindelpumpe in zweiflutiger Bauweise
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
CN110177918B (zh) * 2017-01-11 2022-04-01 开利公司 具有螺旋叶转子的流体机械
PL3938657T3 (pl) * 2019-03-14 2023-10-16 Ateliers Busch S.A. Pompa sucha do gazu oraz zestaw kilku pomp suchych do gazu
DE102020122460A1 (de) 2020-08-27 2022-03-03 Leistritz Pumpen Gmbh Verfahren und Schraubenspindelpumpe zur Förderung eines Gas-Flüssigkeitsgemischs
CN112780558A (zh) * 2021-02-26 2021-05-11 珠海格力电器股份有限公司 转子组件、压缩机及空调
KR102694989B1 (ko) * 2022-04-27 2024-08-13 배형탁 연속가변 스크류 로터가 구비된 건식 진공펌프

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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

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

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