WO1991003647A1 - Ameliorations relatives aux pompes - Google Patents

Ameliorations relatives aux pompes Download PDF

Info

Publication number
WO1991003647A1
WO1991003647A1 PCT/GB1990/001398 GB9001398W WO9103647A1 WO 1991003647 A1 WO1991003647 A1 WO 1991003647A1 GB 9001398 W GB9001398 W GB 9001398W WO 9103647 A1 WO9103647 A1 WO 9103647A1
Authority
WO
WIPO (PCT)
Prior art keywords
pump
chamber
lubricant
sealing
pumping
Prior art date
Application number
PCT/GB1990/001398
Other languages
English (en)
Inventor
Raymond Anthony Leonard Goodridge
Timothy Neil Smith
Original Assignee
Multiphase Systems Plc
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
Application filed by Multiphase Systems Plc filed Critical Multiphase Systems Plc
Publication of WO1991003647A1 publication Critical patent/WO1991003647A1/fr

Links

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
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/008—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids for other than working fluid, i.e. the sealing arrangements are not between working chambers of the machine
    • F04C27/009—Shaft sealings specially adapted for pumps
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation

Definitions

  • the invention relates to pumps for fluids. More particularly, but not exclusively, the invention relates to pumps for handling multiphase flows, involving varying proportions o'f gas and liquid. Furthermore, the invention relates more particularly, but again not exclusively, to pumps for use sub-sea for assisting extraction of oil and gas from oil wells. Aspects of the invention, while advantageous in a sub-sea environment, are equally applicable to land and platform applications.
  • a pump comprising a pump body including connection means for external connection at the suction side and delivery side of the pump , and a pumping element and driver unit located within the body, the pumping element and driver unit, when assembled, being located as one unit within the pump body, sealing means sealing between the pumping element and driver unit and the pump body, the pumping element and driver unit being replaceable as a unit in the event of failure, without the need to disturb the pump body and external connections.
  • the pump element and driver unit is preferably located in the* pump body by vertical movement.
  • the pump element and driver unit may comprise a liner adapted to mate sealingly with the pump body with ports communicating with the connection means of the pump body, the liner containing pump element means and supporting driver means thereon.
  • the driver means may be supported on the liner by cover means .
  • the pump element means may comprise a pair of intermeshing screws.
  • the pump body preferably includes inlet means for allowing entry of lubricant and/or coolant fluid therethrough and into the pump element and driver unit.
  • the inlet means is preferably a single inlet, so that alignment of a single passage of the pump element and driver unit is required during assembly.
  • a pump including a body having material inlet and outlet means, and defining a pumping chamber, pumping means within the pumping chamber and means for providing drive to the pumping means, the pumping means being journalled for rotation, and at one end at least thereof, there being a sealing chamber for containing bearing lubricant and for sealing with the drive providing means, there being chamber inlet means for providing, in use, lubricant at a pressure above the pump suction pressure, means for allowing controlled lubricant passage to the sealing chamber, and open standpipe means communicating between the pump chamber and the sealing chamber adjacent the top thereof, in use, to provide a lubricant level in the sealing chamber not higher than the standpipe, sealing means for sealing between the drive providing means and the sealing chamber at a height below the top of the standpipe whereby the sealing means lies in lubricant, during operation of the pump.
  • the drive providing means is preferably a motor shaft, and may further include a coupling for providing a drive connection between the motor shaft and a pump element shaft.
  • the sealing means may seal between the coupling and the sealing chamber.
  • the sealing chamber may include an annulus surrounding the motor shaft or coupling, the sealing means acting betwen the motor shaft or coupling and the inner wall of the annulus.
  • a pump comprising a pump body defining a pump chamber, rotatable pump element means within the pump chamber, the pump element means being journalled in segmented bearings allowing liquid to flow through the bearings, chamber means enclosing the segmented bearings and means for providing lubricant to the chamber means, the pump including lubricant flow control means between the bearings and the pump chamber whereby lubricant flows from the chamber means to the pump chamber through the bearings at a desired rate.
  • the pump element means may comprise intermeshing screw elements journalled at each end thereof, the chamber means comprising two lubricant chambers.
  • Synchronisation of the screws may be achieved by gear means fixed for rotation with the screw elements, the gear means lying in lubricant in one of the lubricant chambers.
  • the lubricant flow control means may comprise labyrinth means for providing a tortuous flow path for liquid between the bearings and the pump chamber.
  • the labyrinth means may comprise overlapping annuli, one or more extending outwardly, preferably radially outwardly, from an associated shaft and one or more extending inwardly, preferably radially inwardly, from a wall surrounding the associated shaft.
  • the invention further provides a pump comprising a pump chamber, intermeshing screw pump elements within the pump chamber for pumping material between an inlet and an outlet, bearing means for rotatably supporting the screw pump elements, intermeshing gear means at at least one end of the screw pump elements for synchronising rotation of the screw pump elements, a gear lubricant chamber containing the gear means and means for supplying lubricant to the gear lubricant chamber, a flow of lubricant through the gear lubricant chamber being achieved by flow of lubricant from the gear lubricant chamber, past segmented screw pump element bearings lying between the gear lubricant chamber and the pump chamber, and into the pump chamber.
  • Flow control means such as labyrinth means referred to above, are preferably provided between the bearings and the pump chamber to control lubricant flow.
  • Figure 1 is a sectional view along the lines W-W in Figure 2;
  • Figure 2 is a sectional view along the lines X-X in Figure 1 ;
  • Figure 3 is a sectional view along the lines Y-Y in Figure 1 ;
  • Figure 4 is a part-sectional view along the lines Z-Z in Figure 2;
  • Figure 5 is a view on a larger scale of an upper part of the view of Figure 2;
  • Figure 6 is a detailed view of a seal arrangement
  • Figure 7 is a detailed view of a labyrinth arrangement
  • Figure 8 is a detailed view of a further seal arrangement.
  • FIG. 2 shows a sectional view of a sub-sea, twin screw, multiphase pump generally indicated at 10.
  • the pump 10 has a pump body 11 formed as a single metal casting, preferably stainless steel.
  • the pump is arranged in use in a vertical configuration, the pump body 11 including suction and discharge branches 12 and 13 respectively for the pumped product.
  • the pump body would remain fixed to the sub-sea well pipeline for the life of the pump.
  • the pump body 11 includes a series of concentric, stepped bores for location of a pumping element, the stepped bores being indicated at reference numerals 14, 15, 16 and 17.
  • the pumping element, indicated generally at 20 includes a liner 21 having a pair of binocular bores in which run a pair of intermeshing screw shafts 22, 23.
  • the liner 21 seats and seals against the concentric bores, 14, 15 and 16 of the pump body 11 and a top cover 25, bolted to the liner 21 with bolts 26 seats against the bore 17 of the pump body 11.
  • Figure 2 shows O-ring seals at the mating surfaces of the liner 21 and the top cover 25 with the pump body 11 but alternative sealing means may be preferable, such as a metal to metal seal and a clamping arrangement. Hydraulic tooling may be necessary to finally insert the pump timer motor assembly into the pump body. Similarly, hydraulic means may be use to form main positional and final connection to the clamping arrangement.
  • a pump driver 26 being -a motor such as a hydraulic motor or an electrical motor depending on which is more convenient.
  • the pumping element and the drive 26 form a single unit which constitutes a retrievable package containing all the moving parts ' and internal lubrication passageways.
  • the body 11 can remain in situe and the pump element 21 and driver 26 can be removed for replacement.
  • the vertical arrangement assists removal and replacement.
  • intermeshing screw elements are similar to those described in EP-A-0183380 but without screw pitch alteration, although compression shafts as described in EP-A-0183380 could be used.
  • the liner 21 is secured to the top cover 25, a top bearing housing being located in the top cover 25 and spigoted directly to the liner 21.
  • the top bearing housing 30 contain top journal bearings 31 and thrust bearings 32.
  • the journal bearing 31 is a radial bearing such as a hydrodynamic tilting pad bearing and the thrust bearings 32 are Michel bearings providing supportto axialthrust in either direction.
  • the bearings are preferably of silicon carbide and are segmented.
  • the screw shafts 22 and 23 are timed by a pair of timing gears 35, 36 ( Figure 3) located at the bottom end of the pump 10.
  • the gears 35 and 36 ensure that there is no metal to metal contact between the flights of the screw shafts 22 and 23.
  • a bottom cover 37 is bolted to the liner 21 by bolts 38, the bottom cover 37 providing a housing for a radial bearing 39 similar to the bearing 31 previously described.
  • a bearing plate 40 is bolted to the bottom cover 37 by bolts 41, the arrangement for each shaft being similar.
  • Lubrication for the bearings and timing gears is by treated sea water, or treated produced water or crude oil.
  • a single connection 45 to the top cover 25 provides all the lubrication, both to the top and bottom of the pump via internal passageways.
  • a bore 50 in the liner 21 conveys lubricant through the liner 21, the bore 50 being connected at top and bottom by tubes 51, 52 respectively sealed by O-rings to an upper lubricant chamber 55 and a lower lubricant chamber 56.
  • the lower lubricant chamber 56 also contains the timing gears 35, 36, lubricant in the lower lubricant chamber 56 also performing a cooling function for the gears 35, 36.
  • lubricant flows through the upper bearings, 31 and 32 and the lower bearings 39 into the pumping chamber to be pumped away with the product.
  • the segmented nature of the bearings is such that they allow lubricant to pass.
  • labyrinths 60, 61 and 62 are provided.
  • a typical labyrinth arrangement is shown in more detail in Figure 7 where three radially inwardly extending annular plates 65 lie adjacent three radially outwardly extending annular plates 66. This provides a tortuous flow path for lubricant and thereby controls flow through the labyrinth. It will be appreciatedthat different flow control means could be used.
  • the lubrication and sealing arrangements will now be desribed in more detail with reference to both Figures 2 and 5, Figure 5 showing an enlarged view of an upper section of the sectional view of Figure 2.
  • the upper lubricant chamber 55 includes a standpipe 70 extending from the suction side of the pump chamber into the chamber 55 whichis therefore at suction pressure.
  • Bearing flush arriving through the connection 45 and internal passageways reaches the upper bearing housing and exits between the bearings 31 and 32.
  • the bearing flush is provided at a pressure above suction pressure, for example one Bar above suction pressure, and flow of bearing flush lubricant passes both the bearings 31 and 32 of both shafts 22 and 23, thence via the labyrinths 60 and 61 into the upper chamber 55 or the pump chamber.
  • the upper chamber 55 is filled with lubricant to the level of the standpipe 70, bias of lubricant flow being alterable by altering the labyrinth configuration.
  • the liquid level is shown (Fig.5).Inner gas present is displaced by the liquid and leaves via the standpipe 70.
  • a motor shaft 71 coupled by a coupling 72 to screw shaft 23.
  • the screw shaft 22 is driven by the gear arrangement 35, 36. It is important to ensure that no gas enters the driver and extending downwardly from the driver 26 is a cylindrical seal housing 75 locating seals 76 which seal with the rotating coupling 72. In that the liquid level in the chamber 55 is above the level of the seals, gas is prevented from entering the driver 26.
  • seal arrangement shown in Figure 6 is substantially the same as that shown in Figures 2 and 5 and includes rigid discs 80 supporting three flexible discs 81 which allow for downward leakage but not upward gas passage.
  • FIG. 8 A more sophisticated arrangement is shown in Figure 8 to guard against the possibility of the liquid level in the chamber 55 falling.
  • a cup 82 is fixed to the shaft 23 to retain a level of liquid therein.
  • the sealing arrangement of rigid and flexible discs 80 and 81 is that same as that shown in Figure 6.
  • the pump In the event of the lubricant bearing flush supply being shut off or failing, the pump would be stopped automatically.
  • the seal 81 would close against the coupling 72 under the action of pressure from the pump suction, preventing gas entering the driver while the pump is stationary.
  • a non-return valve sited in the flush supply line (not shown) would prevent product and gas backfeeding through the pipe.
  • the liquid within the upper chamber 55 will drain down through the bearings 31 and 32 and labyrinths 60 and 61 into the suction chamber Upon restarting the pump, the lubricant flush will be run for sufficient time to refill the upper chamber 55 before turning the pump.
  • the flexible disc seals 81 are flexible enough to be displaced by leakage flow from the driver bearings, creating a small clearance while running. However, the overhang and flexibility must be such that the seal closes against the coupling 72 when subjected to reverse pressure and does not invert or blow back and permit the passage of gas.
  • the seal shown in Figures 2 and 5 is shown running on the outside of the coupling 72, it could equally be run on the driver shaft extension 71 or the pump shaft 23 (see Figures 6 and 8). It will be appreciated that other types of seal arrangements could be used. Elaborating on the comments made in relation to Figure 8, a problem may occur once the pump is stationary and the pressure either side of the seal has equalised.
  • lubricant bearing flush flow is divided between the upper and lower chambers 55 and 56.
  • Lubricant flows from the chamber 56 into the pump chamber via the bearings 39 and the labyrinths 62. In this way, not only is lubrication achieved but also- a cooling effect is achieved due to the continuous flow of lubricant past the gears 35, 36 and thence to the bearings 62 before exiting from the chamber 56.
  • This embodiment of a pump has several advantages, the first of which is that the pump body may remain in situe and connected to the well supply line but still allowing replacement of the pump element and driver unit which contains all the moving parts and internal lubrication passageways.
  • the vertical arrangement allows ease of assembly beneath the sea. Proprietary bearings are used and lubricant flow through them is controlled by labyrinths, the passageway arrangement allowing a single lubricant bearing flush supply to be used.
  • the top seal assembly operation provides for a simple sealing arrangement obviating the necessity for a pressurised seal system.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Abstract

Une pompe (10) a un corps (11) qui possède une entrée (12) et une sortie (13) de matières. La pompe possède une paire d'arbres à hélice (22, 23) engrenants ainsi qu'un entraîneur (26) de pompe. Les arbres sont tourillonnés pour la rotation et forment une unité, démontable selon le besoin, avec l'entraîneur (26) de pompe. Une chambre d'étanchéité (55) contient un lubrifiant à une pression supérieure à celle de l'aspiration de la pompe, une colonne d'alimentation (70) reliant la chambre d'aspiration et la chambre d'étanchéité (55) afin d'assurer un niveau de lubrifiant dans la chambre d'étanchéité (55) égal ou inférieur à la hauteur de la colonne d'alimentation, ainsi qu'un système d'étanchéité (75, 76) qui sert à établir l'étanchéité entre l'entraîneur (26) et la chambre d'étanchéité (55) à un hauteur inférieure à celle de l'extrémité supérieure de la colonne d'alimentation (70).
PCT/GB1990/001398 1989-09-08 1990-09-10 Ameliorations relatives aux pompes WO1991003647A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB898920340A GB8920340D0 (en) 1989-09-08 1989-09-08 Improvements in pumps
GB8920340.0 1989-09-08

Publications (1)

Publication Number Publication Date
WO1991003647A1 true WO1991003647A1 (fr) 1991-03-21

Family

ID=10662755

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/GB1990/001398 WO1991003647A1 (fr) 1989-09-08 1990-09-10 Ameliorations relatives aux pompes

Country Status (3)

Country Link
AU (1) AU6340990A (fr)
GB (1) GB8920340D0 (fr)
WO (1) WO1991003647A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0775812A1 (fr) * 1995-11-22 1997-05-28 Ishikawajima-Harima Heavy Industries Co., Ltd. Agencement d'étanchéité pour un dispositif de suralimentation entraîné par un moteur
WO2010126650A3 (fr) * 2009-04-30 2011-03-24 General Electric Company Procédé et appareil de gestion de débit de fluide dans un système de pompe à vis

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN115451027B (zh) * 2022-09-16 2024-06-25 湖南崇德科技股份有限公司 一种立式滑动轴承系统

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE747143C (de) * 1941-04-04 1944-09-11 Galassi Ortolani & Mueller Kreiselpumpe
GB1009823A (en) * 1962-05-18 1965-11-10 Mowid Anstalt Submersible centrifugal waste pump
GB2115876A (en) * 1982-03-02 1983-09-14 Dunham Bush Inc Lubrication in a meshing-screw gas-compressor
EP0297274A2 (fr) * 1987-06-29 1989-01-04 Joh. Heinr. Bornemann GmbH + Co. KG Dispositif de transfert consistant en une pompe avec un moyen d'entraînement
EP0327844A2 (fr) * 1988-02-06 1989-08-16 Lu Fengsheng Motopompe submersible totalement sèche et système d'étanchéité annexé

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE747143C (de) * 1941-04-04 1944-09-11 Galassi Ortolani & Mueller Kreiselpumpe
GB1009823A (en) * 1962-05-18 1965-11-10 Mowid Anstalt Submersible centrifugal waste pump
GB2115876A (en) * 1982-03-02 1983-09-14 Dunham Bush Inc Lubrication in a meshing-screw gas-compressor
EP0297274A2 (fr) * 1987-06-29 1989-01-04 Joh. Heinr. Bornemann GmbH + Co. KG Dispositif de transfert consistant en une pompe avec un moyen d'entraînement
EP0327844A2 (fr) * 1988-02-06 1989-08-16 Lu Fengsheng Motopompe submersible totalement sèche et système d'étanchéité annexé

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0775812A1 (fr) * 1995-11-22 1997-05-28 Ishikawajima-Harima Heavy Industries Co., Ltd. Agencement d'étanchéité pour un dispositif de suralimentation entraîné par un moteur
WO2010126650A3 (fr) * 2009-04-30 2011-03-24 General Electric Company Procédé et appareil de gestion de débit de fluide dans un système de pompe à vis
GB2481767A (en) * 2009-04-30 2012-01-04 Gen Electric Method and apparatus for managing fluid flow within a screw pump system
US8419398B2 (en) 2009-04-30 2013-04-16 General Electric Company Method and apparatus for managing fluid flow within a screw pump system
GB2481767B (en) * 2009-04-30 2015-09-16 Gen Electric Method and apparatus for managing fluid flow within a screw pump system

Also Published As

Publication number Publication date
GB8920340D0 (en) 1989-10-25
AU6340990A (en) 1991-04-08

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