WO2012169904A2 - Pompe broyeuse multi-étage - Google Patents

Pompe broyeuse multi-étage Download PDF

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Publication number
WO2012169904A2
WO2012169904A2 PCT/NZ2012/000085 NZ2012000085W WO2012169904A2 WO 2012169904 A2 WO2012169904 A2 WO 2012169904A2 NZ 2012000085 W NZ2012000085 W NZ 2012000085W WO 2012169904 A2 WO2012169904 A2 WO 2012169904A2
Authority
WO
WIPO (PCT)
Prior art keywords
impeller
pump
stage
shaft
vanes
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.)
Ceased
Application number
PCT/NZ2012/000085
Other languages
English (en)
Inventor
Warren Edwin UBELS
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.)
TECHNIPUMP Ltd
Original Assignee
TECHNIPUMP Ltd
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 TECHNIPUMP Ltd filed Critical TECHNIPUMP Ltd
Priority to AU2012267258A priority Critical patent/AU2012267258B2/en
Priority to NZ614617A priority patent/NZ614617B2/en
Publication of WO2012169904A2 publication Critical patent/WO2012169904A2/fr
Anticipated expiration legal-status Critical
Ceased 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
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D7/00—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04D7/02—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type
    • F04D7/04—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type the fluids being viscous or non-homogenous
    • F04D7/045—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type the fluids being viscous or non-homogenous with means for comminuting, mixing stirring or otherwise treating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/2261—Rotors specially for centrifugal pumps with special measures
    • F04D29/2288—Rotors specially for centrifugal pumps with special measures for comminuting, mixing or separating

Definitions

  • the invention relates to rotary pumps for non-homogenous liquids, to centrifugal pumps, especially multi-stage centrifugal pumps, and to the class of pumps that include comminuting means for breaking down solid material (such as fibre) that may be included in the material, such as fibrous material, manure or effluent to be pumped.
  • solid material such as fibre
  • Communication means that this type of pump is capable of macerating or chopping fibrous material suspended in a liquid being pumped into a finer suspension.
  • Effective is used as a collective term to refer to all liquids, including water, and suspensions, including suspensions of fibrous material that are pumped by pumps according to this invention.
  • Optaverse side as applied in this specification to a disk-shaped impeller or diffuser refers to the side carrying vanes, as shown for example in Figs 3 or 7, that is first encountered by incoming effluent, and the term “reverse side” refers to the other side.
  • dairy shed and feed pad (or feed lot) effluents have been disposed of by shifting them away, such as on to a paddock which is not currently being grazed.
  • the effluent is carried by tanker.
  • Alternatives include pumping the material in a relatively specialised form of centrifugal pump; one that is capable of shifting watery materials including suspended fibrous material (such as dung, or spilt grass, hay, straw or silage) without fear of blockage.
  • centrifugal pump one that is capable of shifting watery materials including suspended fibrous material (such as dung, or spilt grass, hay, straw or silage) without fear of blockage.
  • Such pumps generally overcome the possibility of becoming blocked by fibre by including means to break down, or comminute, the fibrous material.
  • GBl 147288 Baum describes a comminuting pump in which a left-handed and a right-handed screw stage, on the same shaft, provide converging flows to a common centrifugal stage. That design would remove an axial load on the shaft. Each screw is faced with a hard material. Note that the waste water treatment industry and the pulp and paper industry use single stage centrifugal comminuting pumps of a larger scale than the present multi-stage example.
  • An object of the present application is to provide a pump for reliably pumping suspensions in water such as dairy shed or feed pad effluent against a pressure head at relatively low to medium flows, or at least to provide the public with a useful choice.
  • the invention provides a multi-stage comminuting centrifugal type pump having a housing and an inlet for receiving a liquid to be pumped and an outlet for pressurised liquid and within pump which a rotatable shaft is made to rotate by a turning force provided by a motor, wherein the pump includes at least two stages; each stage including an impeller having a preferred direction of rotation mounted on to the rotatable shaft and confined within a housing, and a diffuser mounted on to the housing; where both the impeller and the diffuser are made from a hard material capable of retaining an edge, and wherein each stage includes comminution means each comprising a first radial surface, perpendicular to an axis of the shaft, including spiral vanes; said surface being placed close to a second radial surface including at least one comminution slot comprising a shallow radially or tangentially directed groove cut into the radial surface having at least one sharp or cutting edge on a trailing edge between the groove and the radi
  • each stage receives the liquid to be pumped in a sequence so that the pressure differential across all stages is added.
  • each impeller comprises a disk having an obverse face directed forwardly toward the inlet and a reverse face directed away from the inlet; each obverse face includes a plurality of curved vanes extended forwardly from the obverse face; each curved vane commencing near a central shaft mount of the impeller and terminating at an outer periphery of the impeller; a forward edge of every vane is finished with a flat radial surface in a common radial plane; each impeller has a smooth radial surface in another radial plane on the reverse face of the impeller save that the smooth surface is interrupted by a plurality of radially extended grooves, the trailing edge of each of which is provided with a cutting edge; each diffuser has an obverse face includes a plurality of curved vanes extended forwardly from the obverse face; each curved vane commencing an outer periphery of the diffuser and terminating near a central aperture of the diffuser, at least some of the curved va
  • the invention provides a multi-stage centrifugal type pump having a housing and within which a shaft is made to rotate, wherein the rotating shaft 101 has a base and a free end extended into the housing and engaging with each impeller; the rotating shaft has a relatively large diameter and is stiff; the rotating shaft is rotatably supported from near the base only, by bearing means including more than one rolling bearing (102) spaced apart and protected by sealing means between the bearings and the space containing pressurised liquid.
  • the invention provides that the last impeller comprises a disk of greater diameter than that of the other impellers, and pressurised liquid is permitted to access a space behind the reverse face of the last impeller; however back vanes and wear rings on the reverse face of the impeller reduce the pressure exerted by the liquid so that an axial force applied along the shaft is at least partially compensated.
  • the pump is provided with a suction box comprising a closed cavity sealed around the first impeller, and an inlet pipe is connected on to the suction box at a position above the axis of the shaft, so that when in use a pool of liquid will collect within the suction box and allow the pump, when operation commences, to prime itself and commence suction.
  • the pump is provided with an assembly comprising a venturi eductor and coaxial venturi jet mounted coaxially adjacent the free end of the shaft and directed toward the first impeller; the eductor substantially enclosing the input to the impeller, the assembly being
  • the number of slots and adjacent vanes between which comminution may take place are not the same number, so that vibration and noise are reduced.
  • vanes may pass closely over four slots thereby comminuting any suspended solids caught between the two.
  • the sealing means is placed over the rotating shaft at one end; the sealing means comprising a dust protection seal for the bearings, a flinger for throwing off any drips, the flinger 100 being exposed to the external environment, a wiping seal, a space filled with grease, and most importantly, a mechanical seal leading to the area filled (when in use) with a liquid at high pressure; the grease serving to prevent intake of air, and no other sealing means are applied along the interior side.
  • Fig 1 A cross-section through an example pump
  • Fig 1A Detail of Fig 1 ; a cross-section through the sealing means.
  • Fig 2 An external view of a pump with a motor attached.
  • Fig 3 Obverse side of an impeller disk from one stage. 120
  • Fig 4 Reverse side of an impeller disk from one stage.
  • Fig 5 Edge view of an impeller disk from one stage.
  • Fig 6 Reverse side of a diffuser ring from one stage.
  • Fig 7 Obverse side of the diffuser ring showing directing vanes.
  • Fig 8 A vertical sump pump.
  • Fig 9 Graph of performance, compared with existing effluent pumps.
  • Fig 10 A self-priming version.
  • Fig 11 A self-priming version including a venturi jet.
  • the present invention is a comminuting pump, which can macerate suspended fibrous solids such 130 as straw in effluents such as manure, or washdown from a cowshed or feedlot pad. It is a multistage centrifugal pump which can produce an output pressure of the order of 100 to 140 metres of water. It would be useful to reduce any axial force on the impeller shaft, which would become significant if several stages of impeller upon a common shaft are exposed, during use, to a pressure head on one side only. These examples use back vanes on the last of the impellers so that the axial force on the impeller shaft, is reduced, and use a wear ring.
  • each stage the vanes of a non- rotating diffuser are located in close proximity to the rear of a turning impeller disk.
  • close proximity is meant a clearance of perhaps 0.25 to 1 mm.
  • Each non-rotating diffuser has slots for causing comminution of suspended solids. Since comminution is provided for at two planes (both obverse and reverse) around each impeller of each stage, there is little opportunity for suspended 140 solids such as plant fibre to accumulate.
  • FIG 1 shows a longitudinal cross-section of the pump 100.
  • a sturdy rotatable shaft 101 extends to the left side of the drawing and includes a spline for attachment of a driving means such as a 1 1 kW directly coupled three-phase AC induction motor (as in Fig 2) or a belt, chain or gear drive.
  • a driving means such as a 1 1 kW directly coupled three-phase AC induction motor (as in Fig 2) or a belt, chain or gear drive.
  • a driving means such as a 1 1 kW directly coupled three-phase AC induction motor (as in Fig 2) or a belt, chain or gear drive.
  • Such a motor has an almost constant speed.
  • Two sets of roller or ball bearing modules 102 inside a casing 102A support one end of the shaft despite overall sideways or axial forces applied to the shaft during use and serve as a thrust bearing.
  • the shaft is cantilevered from the base, supported by the bearings 102.
  • the far end 101 A of the 150 shaft 104 is not further supported by bearings.
  • a bell-shaped housing member 105 the interior of which may be open to the air, is used to mount the base of the pump housing on to the casing 102A.
  • the housing 106 is comprised of a series of cylindrical castings 108 109, 110 each forming part of a corresponding rotary diffuser. are secured to the base 104 and are tightened together by bolts such as 11 1 so as to seal the interior of the pump.
  • the last cylindrical casting 110 is preferably also formed into an inlet port 112 for connection to an inlet pipe for receiving liquids or suspensions (hereinafter referred to as "effluent") to be pumped.
  • the outlet port is at 124.
  • Sealing means for this pump is shown separately in Fig la, which is an enlarged portion of the middle of Fig 1.
  • Seals 125-132 are provided around the rotatable shaft 101. They separate the interior 103 of housing member 105, which may be air at atmospheric pressure, from the high
  • 125 is a rotating metal disc, which has close running clearances against a sealing ring 126 to provide pressure reduction in the seal chamber.
  • 127 is mechanical seal rotating assembly with a silicon carbide rotary face, which seals against the shaft with a rubber boot, and contains a spring to maintain seal face contact pressure.
  • 128 is a mechanical seal stationary seat made of silicon carbide which does not contact the shaft 101.
  • One preferred kind of seal is the "Type 21" elastomer bellows seal, supplied by John Crane of Slough, United Kingdom, in a selected size. 129 indicates a circumferential space which is
  • a final seal 132 has the purpose of protecting the main bearings 102 from contamination arising in the air space 103 and of holding lubricating grease in place.
  • each stage of the multi-stage pump includes comminution means.
  • Fibrous material will become comminuted or macerated as a result of shearing between the centripetal surfaces of the vanes on the side of each impeller closest to the input 112, which side is manufactured to comprise a flat plane, and the fixed facing surface attached to or comprising part of the housing ring such as 108 or 109.
  • Material which becomes lodged around the rotating 200 impeller vanes that are slanted will tend to move towards the space between the vanes and the fixed facing surface 114A.
  • This surface is another flat plane into which a series of slots have been cut or ground as shown in Fig 6, such that the trailing edge is relatively sharp.
  • the axial clearance between all rotating and fixed parts in this pump is deliberately made small so that shearing will occur.
  • the existence of cutting slots drawn as 402 and 605 may reduce efficiency by perhaps 10%, but allows the pump to work without interruption even if used to transfer feedlot effluent which often has a high fibrous content arising from straw and cattle dung.
  • Cast iron or more preferably "SG” iron spheroidal graphitic iron is preferred for the impellers and diffusers. It has a good surface hardness; greater than cast iron. The cast and machined or ground surfaces become passivated during use, so that corrosion is slow. Stainless steel parts may be used 220 for the impellers and diffusers in appropriate cases, although it is more costly and close
  • Fig 2 shows an external view of a pump with a motor provided as an integrated module, according to this example.
  • 201 represents an AC induction motor rated at about 1 lkW.
  • 202 is a bell-like connector between the motor and the bearing housing 102A pump, and preferably includes a flexible coupling between the motor shaft and the pump shaft, in case of any misalignment between the two shafts.
  • the bearing assembly 102/102A could be used as the bearing for the motor as well, if convenient.
  • 203 is a base or mounting plate.
  • Fig 3 shows the obverse side of a cast impeller plate or disk 120 which rotates anticlockwise.
  • Incoming effluent is directed near the boss 301.
  • This side has a small number such as 3 or 4 curved 230 impeller vanes; one labelled 117 rising from a surface 303, which, when rotating, fling the liquid or suspension being pumped towards the periphery. All vanes are typically included in the mould used for casting.
  • Each vane originates near the impeller plate near the central boss 301 and reaches a maximum height 302, shown hatched, at which it is ground or otherwise shaped into the same tangential plane as the other impellers.
  • the central boss has a keyway 304 to lock the impeller plate to the shaft 101.
  • the plate cannot move far laterally along the shaft because its vanes on the obverse side share a flattened surface 302 which skims over the notched but otherwise flat surface of the diffuser of Fig 6; except in the case of the last impeller
  • Fig 4 shows the reverse side of the impeller 120.
  • This side comprises a flat surface 401, shown hatched, which when in use skims over the vane-bearing side (shown in Fig 7) of the next diffuser 240 plate along the multi-stage pump.
  • the flat surface carries a small number, such as 4 comminuting slots 402 the edges of which are intended to shear any fibre that finds its way into the space.
  • 4 should have a relatively sharp trailing edge in order to shear any suspended fibres, although this might wear with use. It is desirable to use different numbers of vanes and slots, such as 4 vanes against 3 slots for example, to avoid noise and vibration that would occur if the counts of slots and vanes were the same.
  • the central boss is the same as that of Fig 3.
  • Fig 6 shows one non-rotating diffuser plate 109 of the pump, in reverse view.
  • the plane surface 604 is skimmed over by the vanes of the adjacent impeller.
  • the two slots 605 have sharp or relatively sharp trailing edges (in relation to the direction of rotation) in order to macerate any 250 fibrous material that becomes trapped or wrapped over the impeller vanes during use.
  • the slots may be formed during casting and the edges are preferably finished off with an angle grinder or the like.
  • Lug 601 is used at the time of assembly to line up the individual parts and to aid disassembly. These lugs can be knocked with a hammer to assist separation of the casings (diffuser external parts) during maintenance. Casings can tend to "glue" together over time.
  • Fig 7 shows the six fixed vanes of the preferred diffuser 109.
  • the high vanes share a common plane surface 704 (hatched) which, when in use, is skimmed over by the plane surface 401 of the impeller of Fig 4.
  • the six vanes are intended to return the liquid or effluent being pumped towards the central shaft and on to the next stage; at the same time decreasing any rotation that was imposed by the rotation of the impeller.
  • All vanes 260 are formed by casting in the preferred manufacturing process, and the plane surface 704 of the high vanes is finished by grinding or turning or any other appropriate process.
  • the outer shell of the diffuser 109 includes sealing means such as a stepped periphery that can accommodate a rubber ring or other seal for the stage, as is known.
  • Fig 8 shows an external view of a vertical sump pump 800 in which the motor 801 is located at some distance above the normally immersed pump assembly 804.
  • the entire assembly may be mounted on a pontoon or on a jetty, as required with reference to the safety of maintenance 270 engineers.
  • the paired ball or roller bearing assembly internally configured as described in Example 1, is inside the housing 802.
  • a cylinder of indefinite length 803 encloses a stout drive shaft and reaches into the liquid to be pumped. No further bearings are used.
  • One advantage is that if the sump runs dry, no damage will occur.
  • liquid enters the pump 804 at 805 and exits at 806.
  • Fig 8 is the use inside pump 804 of multi-stage comminuting parts including rotatable impellers and non-rotating diffusers as described in Example 1 with reference to Figs 1, 3, 4, 5, 6 and 7.
  • Fig 10 shows a self-priming pump.
  • the inlet 901 is located above the axis of the pump, and is provided with a flap valve 902 leading to inlet cavity or suction box 903, which has an inspection
  • This pump has two impellers; first stage 910 and second stage 911, together with comminuting diffusers and stators as described with reference to Figs 1, 3, 4, 5, 6 and 7.
  • the wear ring 912 that serves as a sealing collar on the second stage has typically 0.25 mm clearance around its periphery within the wear ring aperture 913 included as part of the bell housing 914.
  • an optional bleed pipe 905 of restricted aperture sucks any leaked fluid from the bell housing chamber 906 back into the suction box 908.
  • a flap valve may be included at the exit or vent 907 of pipe 905, to prevent back flow.
  • Fig 1 1 shows a venturi nozzle arrangement mounted coaxially with the axis of the shaft at the input end of a multi-stage pump 1 100, similar to that of Example 3.
  • a suction is created as a result of flow through the venturi eductor 1104 when a jet of liquid or mixed liquid and suspended solid matter ejected from venturi nozzle 1105 creates a partial vacuum and assists in driving liquid to be pumped toward the first impeller of the pump 1100.
  • the pump exhibits a significantly greater suction, applied through input port 901, than would a pump relying solely on impeller suction. Longer suctions lines may be used.
  • Fig 9 indicates performance of a two-stage (YM53-2stg), and a three-stage (YM53-3stg) pump according to this invention as solid lines, as compared with Reid & Harrison (Yardmaster, Matamata, New Zealand) single-stage effluent pumps type RH-10 (220) and RH-10 (215) shown here as dashed lines.
  • a first set of curves shows dependence of output flow in litres per second along the horizontal axis against head of pressure in metres of water on the vertical axis at the left 310 side. The maximum head against which flow is pumped is larger.
  • the vertical axis on the right shows power consumed in kilowatts.
  • the pumps according to this invention always show a lower power consumption.
  • the target of pumping against at least 100 metres head of water is met by a multi-stage centrifugal pump at good efficiency.
  • a large single-stage pump could not achieve the same pressure.
  • Fibrous material is comminuted. Since the entry side of all vanes is angled, any fibrous material 320 reaching an impeller tends to move axially, to within the space between the flat surface and
  • the pump cartridge a name used for the entire assembly of impellers and diffusers, can be replaced as a whole from time to time on account of wear, corrosion or damage.
  • the sealing means 125 and 126 is replaceable at the same time.

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

Abstract

L'invention porte sur une pompe broyeuse multi-étage utilisée, par exemple, avec des effluents agricoles d'étable ou de parc d'engraissement, est apte à développer une pression de sortie de 100 à 140 mètres d'eau tout en broyant les éventuels solides fibreux en suspension comme la paille. A chaque étage, les aubes d'un diffuseur non rotatif sont placées à proximité immédiate d'un disque rotatif qui comprend l'arrière d'un étage précédent du rotor et présentant des fentes servant pour le broyage des solides en suspension. Le rotor de chaque étage tourne à proximité d'une plaque fixe portant aussi des fentes de broyage. Est décrite une option d'étage d'aspiration assistée par venturi.
PCT/NZ2012/000085 2011-06-07 2012-06-06 Pompe broyeuse multi-étage Ceased WO2012169904A2 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
AU2012267258A AU2012267258B2 (en) 2011-06-07 2012-06-06 Multistage comminuting pump
NZ614617A NZ614617B2 (en) 2011-06-07 2012-06-06 Multistage comminuting pump

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
NZ593278 2011-06-07
NZ59327811 2011-06-07

Publications (1)

Publication Number Publication Date
WO2012169904A2 true WO2012169904A2 (fr) 2012-12-13

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ID=47296660

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/NZ2012/000085 Ceased WO2012169904A2 (fr) 2011-06-07 2012-06-06 Pompe broyeuse multi-étage

Country Status (2)

Country Link
AU (1) AU2012267258B2 (fr)
WO (1) WO2012169904A2 (fr)

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9438080B2 (en) 2013-03-08 2016-09-06 Regal Beloit America, Inc. Seal arrangement for a motor pump assembly and a motor for a pump including a seal arrangement
JP2018178933A (ja) * 2017-04-19 2018-11-15 株式会社荏原製作所 ポンプ
WO2020198411A1 (fr) * 2019-03-27 2020-10-01 Baker Hughes, A Ge Company, Llc Pompe horizontale à écoulement élevé et faible npshr à module d'amorçage
US10995581B2 (en) 2018-07-26 2021-05-04 Baker Hughes Oilfield Operations Llc Self-cleaning packer system
US11041374B2 (en) 2018-03-26 2021-06-22 Baker Hughes, A Ge Company, Llc Beam pump gas mitigation system
US11408265B2 (en) 2019-05-13 2022-08-09 Baker Hughes Oilfield Operations, Llc Downhole pumping system with velocity tube and multiphase diverter
US11441391B2 (en) 2018-11-27 2022-09-13 Baker Hughes, A Ge Company, Llc Downhole sand screen with automatic flushing system
US11643916B2 (en) 2019-05-30 2023-05-09 Baker Hughes Oilfield Operations Llc Downhole pumping system with cyclonic solids separator
US12152475B2 (en) 2022-10-18 2024-11-26 Baker Hughes Oilfield Operations Llc Intake fluid density control system
US12473804B2 (en) 2022-07-12 2025-11-18 Baker Hughes Oilfield Operations Llc External recirculation for gas lock relief
US12503933B2 (en) 2023-10-11 2025-12-23 Baker Hughes Oilfield Operations Llc Electric submersible pump gas evacuation system

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9438080B2 (en) 2013-03-08 2016-09-06 Regal Beloit America, Inc. Seal arrangement for a motor pump assembly and a motor for a pump including a seal arrangement
US10243422B2 (en) 2013-03-08 2019-03-26 Regal Beloit America, Inc. Seal arrangement for a motor pump assembly
JP2018178933A (ja) * 2017-04-19 2018-11-15 株式会社荏原製作所 ポンプ
US11041374B2 (en) 2018-03-26 2021-06-22 Baker Hughes, A Ge Company, Llc Beam pump gas mitigation system
US10995581B2 (en) 2018-07-26 2021-05-04 Baker Hughes Oilfield Operations Llc Self-cleaning packer system
US11441391B2 (en) 2018-11-27 2022-09-13 Baker Hughes, A Ge Company, Llc Downhole sand screen with automatic flushing system
WO2020198411A1 (fr) * 2019-03-27 2020-10-01 Baker Hughes, A Ge Company, Llc Pompe horizontale à écoulement élevé et faible npshr à module d'amorçage
US11408265B2 (en) 2019-05-13 2022-08-09 Baker Hughes Oilfield Operations, Llc Downhole pumping system with velocity tube and multiphase diverter
US11643916B2 (en) 2019-05-30 2023-05-09 Baker Hughes Oilfield Operations Llc Downhole pumping system with cyclonic solids separator
US12473804B2 (en) 2022-07-12 2025-11-18 Baker Hughes Oilfield Operations Llc External recirculation for gas lock relief
US12152475B2 (en) 2022-10-18 2024-11-26 Baker Hughes Oilfield Operations Llc Intake fluid density control system
US12503933B2 (en) 2023-10-11 2025-12-23 Baker Hughes Oilfield Operations Llc Electric submersible pump gas evacuation system

Also Published As

Publication number Publication date
AU2012267258A1 (en) 2013-10-03
AU2012267258B2 (en) 2016-04-07
NZ614617A (en) 2015-10-30

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