[go: up one dir, main page]

WO2024254670A1 - Admissions côté bas pour pompes de fond de trou, et appareils et procédés associés - Google Patents

Admissions côté bas pour pompes de fond de trou, et appareils et procédés associés Download PDF

Info

Publication number
WO2024254670A1
WO2024254670A1 PCT/CA2023/050806 CA2023050806W WO2024254670A1 WO 2024254670 A1 WO2024254670 A1 WO 2024254670A1 CA 2023050806 W CA2023050806 W CA 2023050806W WO 2024254670 A1 WO2024254670 A1 WO 2024254670A1
Authority
WO
WIPO (PCT)
Prior art keywords
low
side intake
intake
fluid
intake section
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.)
Pending
Application number
PCT/CA2023/050806
Other languages
English (en)
Inventor
David Dyck
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.)
INFLOW SYSTEMS Inc
Original Assignee
INFLOW SYSTEMS Inc
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 INFLOW SYSTEMS Inc filed Critical INFLOW SYSTEMS Inc
Priority to PCT/CA2023/050806 priority Critical patent/WO2024254670A1/fr
Publication of WO2024254670A1 publication Critical patent/WO2024254670A1/fr
Anticipated expiration legal-status Critical
Pending legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B47/00—Pumps or pumping installations specially adapted for raising fluids from great depths, e.g. well pumps
    • F04B47/02—Pumps or pumping installations specially adapted for raising fluids from great depths, e.g. well pumps the driving mechanisms being situated at ground level
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B43/00—Methods or apparatus for obtaining oil, gas, water, soluble or meltable materials or a slurry of minerals from wells
    • E21B43/12—Methods or apparatus for controlling the flow of the obtained fluid to or in wells
    • E21B43/121—Lifting well fluids
    • E21B43/128—Adaptation of pump systems with down-hole electric drives
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B43/00—Methods or apparatus for obtaining oil, gas, water, soluble or meltable materials or a slurry of minerals from wells
    • E21B43/34—Arrangements for separating materials produced by the well
    • E21B43/38—Arrangements for separating materials produced by the well in the well
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B47/00—Pumps or pumping installations specially adapted for raising fluids from great depths, e.g. well pumps
    • F04B47/06—Pumps or pumping installations specially adapted for raising fluids from great depths, e.g. well pumps having motor-pump units situated at great depth
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D13/08—Units comprising pumps and their driving means the pump being electrically driven for submerged use
    • F04D13/10—Units comprising pumps and their driving means the pump being electrically driven for submerged use adapted for use in mining bore holes
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/426—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps
    • F04D29/4293—Details of fluid inlet or outlet
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/445—Fluid-guiding means, e.g. diffusers especially adapted for liquid pumps
    • F04D29/447—Fluid-guiding means, e.g. diffusers especially adapted for liquid pumps rotating diffusers

Definitions

  • This document relates to intakes and gas separators for downhole pumps, and related apparatuses and methods.
  • the present disclosure relates generally to separation of gas and liquid phases of downhole fluids at the intake of a downhole rotary pump and more particularly to low-side intakes with a rotating shaft extending therethrough to maximize pump efficiency and drawdown and production rates, especially in gassy wellbores, and high deviation or horizontal wellbores with unstable flow regimes.
  • Hydrocarbons such as oil and gas
  • Hydrocarbons are produced or obtained from subterranean reservoir formations that may be located onshore or offshore through wells.
  • Pump systems for example, electrical submersible pump (ESP) systems and progressive cavity pump (PCP), may be used when reservoir pressure alone is insufficient to produce hydrocarbons from a well. Presence of free gas in a fluid being pumped and the resulting multiphase flow behavior of the fluid has a detrimental effect on pump performance and motor cooling. The presence of gas in a pump reduces the pressure created within each pump stage, which reduces output of the pump.
  • ESP electrical submersible pump
  • PCP progressive cavity pump
  • gas lock In extreme situations, high concentrations of gas within a pump result in a condition commonly referred to as “gas lock”, where gas is so prevalent within enough stages of the pump, that flow ceases in the intended direction. Reducing the concentration of gas, reducing the size of the bubbles, and increasing the pressure in the fluid that enters the main pump stages improves pump performance and may improve the operating temperature and stability of the motor.
  • gas avoiders which are low-side intakes for pumps installed at high inclinations, active gas separators, which use centrifugal forces (like a cyclone) to separate liquid from gas, reverse-flow (dip-tube) gas separators which use gravity to separate liquid from gas, and gas handlers which homogenize the flow and reduce the size of bubbles, and provide an increased pressure at the first main stage of the ESP.
  • active gas separators which use centrifugal forces (like a cyclone) to separate liquid from gas
  • reverse-flow (dip-tube) gas separators which use gravity to separate liquid from gas
  • gas handlers which homogenize the flow and reduce the size of bubbles, and provide an increased pressure at the first main stage of the ESP.
  • Existing gas avoiders have a short intake length and are not well optimized for intermittent (e.g. sluggy) flow conditions at the pump intake, which is typical of horizontal wells.
  • gas avoider effectiveness can be improved with a longer intake that also provides a more uniform inflow profile thereby reducing the downwards velocity in the casing to substantially lower than the bubble rise velocity.
  • a more effective, efficient and reliable gas avoider pump intake is proposed in the present disclosure.
  • Traditional gas avoiders used with ESPs typically have a short intake section because of the costs and challenges associated with a shaft rotating within, and a general lack of awareness and understanding of multiphase flow dynamics in the wellbore adjacent to gas avoider intake devices.
  • Flow rates with ESPs are typically high and flow velocity adjacent to a gas avoider device is also high.
  • the vertical component of the velocity adjacent to a low-side intake is proportional to the flow rate divided by the length of the intake.
  • the vertical component of the velocity adjacent to a low-side intake largely controls the effectiveness of gas avoidance.
  • Prior gas avoiders are typically so short that the vertical component of the velocity adjacent to the device exceeds the bubble rise velocity which substantially limits the effectiveness of gas avoidance.
  • many devices have failed because they create a restricted flow area, leading to high velocities through the restriction and excessive pressure drop at the suction end of the pump, which may cause undesirable cavitation, gas breakout, and starving of the pump of liquid. Because of the requirement for large flowing cross sectional areas and the accommodation of a shaft, the clearances are typically tight, which limits the length that an eccentrically weighted component can be made and run in a well with a dogleg without binding/bending/seizing.
  • a low-side intake section for a downhole rotary pump comprising: a rotatable thru-shaft part between downstream and upstream ends of the low-side intake section; and an eccentrically weighted part configured for free axial rotation to orient one or more inlet openings toward a base of the low-side intake, the one or more inlet openings connected to feed a fluid outlet at the downstream end.
  • An intake is disclosed for a downhole pump with a thru-shaft and an eccentrically weighted component that freely rotates to orient inlet openings towards the low side of the wellbore, with a feature that restricts flow through inlet openings towards the downstream end to provide a more uniform inflow profile along its length thereby improving gas avoidance efficiency.
  • a multi-stage low-side oriented intake is disclosed for a downhole pump with a thru-shaft, wherein each intake stage is delineated from the next stage by at least a shaft support bearing, and each intake stage includes an eccentrically weighted component that rotates independently from an eccentrically weighted component of another intake stage.
  • Embodiments of gas avoiders of the present disclosure provide a more uniform inflow profile along its length that improves gas avoidance effectiveness by reducing the downward velocity of liquid in the casing below a bubble rise velocity.
  • Embodiments of gas avoiders of the present disclosure enable a longer overall intake section to be utilized.
  • the length-to-housing diameter (L:D) ratio of the overall intake section may be greater than 3:1, 6:1, or 10:1, by providing shaft support bearings between multiple intake stages, each with an independent eccentrically weighted component.
  • Embodiments of gas avoiders of the present disclosure enable a longer overall intake section to be utilized while also providing a more uniform inflow profile along its length without a large pressure loss by locating impellers between two or more intake stages, each stage comprising an independent eccentrically weighted component.
  • Embodiments of gas avoiders of present disclosure obtain a more uniform inflow profile within each stage (an eccentrically weighted component) by having less flow area in an inlet opening towards a downstream end; because the overall flow area is high, excessive velocity and pressure drops do not result.
  • Embodiments of gas avoiders of the present disclosure obtain a more uniform inflow profile along the length of an eccentrically weighted component by having tapered or partial length weights that restrict inflow towards the downstream end.
  • Embodiments of gas avoiders of the present disclosure with impellers between intake stages improves upon typical limitations of extended intakes by controlling the inflow profile with an impeller that adds energy, rather than a restriction that dissipates energy.
  • a challenge for all gas avoiding intakes is that gas is several orders of magnitude more mobile than liquid.
  • Relative mobility through restrictions is typically inversely proportional to density and viscosity.
  • the volumetric flow rate of gas may increase by at least an order of magnitude compared to liquid through the same restriction with the same pressure drop, and therefore a substantial volume of gas is allowed to break through and ‘bypass’ the gas avoider.
  • impellers when exposed to gas instead provide less volumetric flowrate and less developed pressure compared to liquid.
  • the impeller downstream of that stage may cause the gas breakthrough event to be at least an order of magnitude smaller ( ⁇ 1/10 the volume of gas ingested) as compared to a similar device where a restriction is used in a similar location for controlling the inflow contribution of multiple stages.
  • ESP While the main use case may be in an ESP with a downhole electric motor and seal section positioned below the pump, it should be interpreted to be applicable to any downhole rotary pump which has a shaft passing through the intake (i.e., this intake system may be used with centrifugal or axial or positive displacement rotary downhole pumps that are driven either from surface via sucker rods, continuous rods, or driven from a downhole motor that may be electric or hydraulic, or other).
  • ESP is implied to mean a centrifugal type pump which rotates in the range of 500 to 20,000 RPM driven by a downhole electric motor.
  • PCPs are positive displacement pumps, sometimes known as “screw pumps”, they operate in the range of 10 to 500 RPM and are typically driven from a motor or engine on surface using drive rods.
  • This intake system may also be used in conjunction with vane pumps or twin-screw pumps in downhole applications.
  • Embodiments of intakes of the present disclosure improve the efficiency and reliability of pumping a gas laden fluid, for example, one or more downhole fluids associated with a hydrocarbon recovery or production operation. It is designed to ingest and process larger total volumes of fluid while allowing larger total volumes of gas to be vented past the pump up the casing annulus in order to provide higher levels of drawdown and production, while improving reliability and efficiency of the pump.
  • the present disclosure illustrates some embodiments where components are arranged within an outer housing where the outer housing forms the primary structural member, and other embodiments where flanged connections are used between stages. It may be understood that certain embodiments of the present disclosure may be assembled within a housing; or alternatively, each stage may be coupled to the next and each stage may carry the structural loads directly without the need for a housing; connections (where shown) are typically flanged, although threaded or other connection types may be equally used. Seals between components are typically face seals engaged by compression in the stack of internal components within the housing, however O-rings or other sealing elements may also be used but are omitted from the figures for the sake of clarity and simplicity.
  • the low-side intake section is structured to relatively progressively increase a restriction to intake flow, through the one or more inlet openings, toward the downstream end.
  • the low-side intake section is structured to relatively progressively increase the restriction to intake flow to equalize inflow along an axial length of the one or more inlet openings.
  • the one or more inlet openings are one or more of shaped, patterned, or arranged to progressively decrease intake flow area per axial unit length toward the downstream end. A ratio of decreasing intake flow area per axial unit length is greater than 2:1.
  • the one or more inlet openings each comprise a hole, slot, or tapered slot.
  • the eccentrically weighted part has a weighted housing that is hollow and defines a fluid flowpath to the fluid outlet.
  • the one or more inlet openings are defined through a wall of the weighted housing.
  • the weighted housing is cylindrical.
  • One or more eccentric weights are mounted or formed on one or both an interior surface and an exterior surface of the weighted housing.
  • One or more baffles are defined, on an interior surface of the weighted housing, to regulate intake flow from the one or more inlet openings to the fluid flowpath.
  • the one more baffles are structured to decrease a radial overflow clearance defined between the one or more inlet openings and the fluid flowpath toward the downstream end.
  • the one or more baffles comprise a pair of baffles, one on either lateral side of the one or more inlet openings.
  • the one or more baffles are defined by one or more eccentric weights.
  • One or more baffles are defined, on an exterior surface of the weighted housing, to regulate intake flow from an exterior surface of the weighted housing to the one or more inlet openings.
  • the one or more baffles are structured to increase in radial thickness, toward the downstream end.
  • the one or more inlet openings are structured and arranged to provide consistent flow area per axial unit length toward the downstream end.
  • An intake part of the low-side intake section defines the one or more inlet openings.
  • a ratio of the overall length of the intake part to an outer diameter of the low-side intake section is greater than 2:1.
  • the low-side intake has an outer housing within which the eccentrically weighted part is located, the outer housing defining one or more housing inlet openings.
  • Upstream and downstream couplers are at the upstream and downstream ends, respectively of the low-side intake section.
  • One or more radial bearings support the rotatable thru-shaft upstream and downstream of the one or more inlet openings.
  • Radial bearings supporting the rotatable thru- shaft at both the upstream and downstream ends.
  • a plurality of the low-side intake sections are coupled together, as stages. Each low-side intake section is configured to permit independent rotation of the eccentrically weighted part relative to the other of the low-side intake sections.
  • Radial bearings supporting the rotatable thru-shaft at between intake sections.
  • Each low-side intake section defines a fluid flowpath between the one or more inlet openings and the fluid outlet.
  • the fluid flowpaths of the low-side intake sections connect to collectively pass fluids from the low-side intake sections downstream.
  • the fluid flowpaths of the low-side intake sections connect in parallel to collectively pass fluids from the low-side intake sections downstream through an inner common fluid flowpath.
  • an inner housing is located radially inward of the eccentrically weighted part, the inner housing defining an inner common fluid flowpath that extends between the upstream and downstream ends of the at least one low-side intake section, and is connected to receive fluid from a downhole inner common flowpath and the fluid outlet of the at least one low-side intake section.
  • the fluid outlet of the at least one low-side intake section is at the downhole end of said low-side intake section.
  • the fluid outlet of the at least one low-side intake section is at the uphole end of said low-side intake section.
  • an inner housing is located radially inward of the eccentrically weighted part, the inner housing defining an inner common fluid flowpath that extends between the upstream and downstream ends of the at least one low-side intake section, and is connected to receive fluid from one or both the fluid outlet of the at least one low-side intake section or the fluid flowpath of a low-side intake section located downhole of the at least one low-side intake section.
  • the inner common fluid flowpath of the at least one low-side intake section is connected to receive fluid from the fluid flowpath of the low-side intake section located downhole of the at least one low-side intake section.
  • the inner common fluid flowpath of the at least one low-side intake section is connected to receive fluid from a fluid flowpath of a low-side intake section located uphole of the at least one low-side intake section.
  • the low- side intake section comprises an outer housing in which the eccentrically weighted part is located, the outer housing defining one or more housing inlet
  • an outer fluid chamber is defined between the outer housing and the eccentrically weighted part, and is connected to feed fluid from the one or more housing inlet openings through the low-side oriented inlet openings to the fluid flowpath.
  • the outer fluid chamber is structured to feed fluid to the low-side oriented inlet openings toward the upstream end.
  • the outer fluid chamber is structured to feed fluid to the low-side oriented inlet openings toward the downstream end.
  • One or more impellers are between adjacent low-side intake sections, and structured to convey fluid from the fluid flowpath of each low-side intake section into the inner common fluid flowpath of the low-side intake section, or into the inner common fluid flowpath of an uphole low-side intake section.
  • Each impeller has a radially inward vane portion and a radially outward vane portion, which are structured to convey fluids received from the inner common fluid flowpath and the fluid flowpath, respectively.
  • Each low-side intake section comprises an impeller structured to convey fluid from the fluid flowpath into the inner common fluid flowpath.
  • Each impeller has a radially inward vane portion and a radially outward vane portion, which are structured to convey fluids received from the downhole inner common fluid flowpath and the fluid flowpath, respectively.
  • Each impeller is structured to convey fluids via the radially outward vane portion generating a higher relative pressure than the radially inward portion.
  • Each of the low-side intake sections comprises an impeller.
  • Each of the low-side intake sections comprise an impeller; the fluid flowpaths of the low-side intake sections connect in series to collectively pass fluids from the low-side intake sections downstream; and each impeller comprises a primarily axial-flow impeller.
  • a downhole rotary pump has a downhole motor; a downhole pump; and a low-side intake section or the multi-stage low-side intake located between the downhole motor and the downhole pump, with the rotatable thru-shaft connected between the downhole motor and downhole pump.
  • the feature that restricts flow through inlet openings towards the downstream end is an inlet opening pattern with a varied flow area per unit length, having a ratio of flow area per unit length towards an upstream end to the flow area per unit length towards a downstream end, this ratio being greater than 2:1.
  • the flow area per unit length varies in an inlet opening pattern of an eccentrically weighted component.
  • the flow area per unit length varies in an opening pattern of an outer housing that is disposed radially outwards from an eccentrically weighted component.
  • the opening pattern comprises holes, or slots, or a tapered slot.
  • An eccentrically weighted component comprises a generally cylindrical tube with inlet openings oriented towards the lowside by means of weights on both sides of the inlet openings, wherein the feature that restricts flow through inlet openings towards the downstream end is a non-uniform profile of the weights along the length of the inlet openings. Said weights with a non- uniform profile are attached to the inside of the tube. Note: Here the taper’s purpose is to preferentially restrict flow through the lowside-inlets towards the suction-end. The low clearance between the weights and a central body (inner housing or shaft) limits the flow entering the inlet opening from accessing the hydraulic flow area towards the high side of the annular flowpath formed within the eccentrically weighted component.
  • Said weights with a non-uniform profile are attached to the outside of the tube. For the purpose of preferentially restricting flow towards the suction-end between the eccentrically weighted tube and the perforated housing. Said weights with a non-uniform profile are attached to both the inside and outside of the tube. Said non-uniform weights are used with inlet opening pattern that is not varied (and the weights alone provide a uniform inflow profile).
  • the non-uniform profile comprises a radial thickness profile (taper) that approaches closer to the central shaft towards the downstream end.
  • the non-uniform profile comprises a partial length weight wherein the upstream end of the weight is at an axial position that is downstream of the inlet openings upstream end.
  • the eccentrically weighted component is external to the main structural member (which supports tension pressure torque bending loads etc.). For the purpose of providing a long lowside-inlet section, said combined lowside-inlet section length (with multiple stages) being greater than an acceptable length of unsupported shaft.
  • An intake stage defines an axial flowpath for axial flow of fluid from another intake stage at the upstream end to its downstream end, said flowpath being through the eccentrically weighted component.
  • the eccentrically weighted component is inside an outer housing.
  • the eccentrically weighted component is external to the main structural member (which supports tension pressure torque bending loads).
  • An impeller is disposed between two intake stages for the purpose of encouraging greater flow from the upstream stages.
  • An intake stage comprises an inner housing, the inner housing forms an axial flowpath for flow from another intake stage at the upstream end to its downstream end.
  • the impeller comprises a radially outward portion through which only the inflow of the same intake stage passes, and a radially inward portion through which at least the flow from an upstream stage passes.
  • Vane design is different on the radially inward portion of the impeller from the vane design on the outward portion of the impeller, such that the vane design on the outward portion is structured to create more pressure at a lower flow rate as compared to the inward portion.
  • the flow through the radially inward and radially outward portions of the impeller are in an uphole direction, the eccentrically weighted component is downhole of the impeller of the same stage.
  • the flow through the eccentrically weighted component and the outer portion of the impeller is in a downhole direction, and the flow through the inner portion of the impeller is in an uphole direction, the eccentrically weighted component is uphole of the impeller of the same stage, and the inward portion passes the flow of the intake stage and an upstream stage.
  • the intake stage comprises an outer housing and an inner housing; an eccentrically weighted component is disposed between the inner housing and outer housing; the outer housing having a pattern of openings; the eccentrically weighted component having inlet openings that orient towards the low side; the inner housing comprising an axial flowpath.
  • An intake stage comprises a feature that restricts flow through inlet openings towards the downstream end of each stage. The ratio of the overall length of the inlet openings to outer diameter exceeds a ratio of 4:1.
  • Fig.1A is a side elevation view of a rotary pump disposed on the end of a production tubing string in a wellbore that penetrates an underground formation substantially horizontally, the pump being substantially horizontal incorporating an intake device.
  • Fig.1B is a cross section view, taken along the 1B section lines of Fig.1A, of a wellbore through a low- side oriented intake with a fluid level showing vertical velocity vectors of the liquid and gas.
  • Fig.2A is a side perspective view of an embodiment of an intake device with an eccentrically weighted component within a perforated outer housing and a tapered opening pattern in the housing comprised of slots.
  • Fig.2B is a side perspective view of an embodiment of an intake device with an eccentrically weighted component within a perforated outer housing and a tapered opening pattern in the housing comprised of circular holes.
  • Fig.3A is a longitudinal perspective section view of an embodiment of an intake device with an eccentrically weighted component within a perforated outer housing.
  • Fig.3B is a bottom view of an eccentrically weighted component with an inlet opening comprised of a single tapered slot.
  • Fig.3C is bottom view of an eccentrically weighted component with an inlet opening comprised of a single tapered slot pattern.
  • Fig.4A is a perspective (isometric) longitudinal section view of an embodiment of an eccentrically weighted component with tapered weights mounted internally on each side of the inlet opening of the eccentrically weighted component.
  • Fig.4B is a longitudinal section view of an embodiment of an intake device with an eccentrically weighted component within a perforated outer housing and tapered weights mounted internally and externally on each side of the inlet opening(s) of the eccentrically weighted component.
  • Fig.4C is a bottom view of an eccentrically weighted component with tapered and partial length weights mounted externally on each side of a tapered inlet opening pattern of an eccentrically weighted component.
  • Fig.5A is a perspective view of an embodiment of an intake device with an eccentrically weighted component that is external to the main structural member.
  • Fig.5B is a cross section view taken along the 5B section lines from Fig.5A.
  • Fig.5C is a bottom view of the eccentrically weighted component of Fig.5A.
  • Fig.6A is a longitudinal section view of an intake device with an eccentrically weighted component similar to Fig.5 with multiple stages axially connected together (in series).
  • Fig.6B is a longitudinal section view of an intake device with an eccentrically weighted component similar to Fig.4C with multiple stages axially connected together (in series).
  • Fig.7A is a longitudinal section view of an intake device similar to Fig.6A with impellers between two or more stages (in series).
  • Fig.7B is a longitudinal section view of an intake device similar to Fig.6B with impellers between two or more stages (in series).
  • Fig.8A is a longitudinal section view of an intake device similar to Fig.7A wherein the flow from an upstream intake stage is through an inner housing (stages arranged in parallel while Figs.6 and 7 were arranged in series).
  • Fig.8B is a longitudinal section view of an intake device similar to Fig.7B wherein the flow from an upstream intake stage is through an inner housing.
  • Fig.8C is a detail view of the area denoted by the circle 8C of Fig.8B, illustrating the junction between stages of Fig.8B.
  • Fig.8D is a detail longitudinal section view of similar to Fig.8C with an alternate configuration wherein the flow direction within each eccentrically weighted component and the outward portion of the impeller is in a downhole direction; an inner housing contains the flow from the stage and an upstream intake stage.
  • Couple or “couples,” as used herein are intended to mean either an indirect or direct connection.
  • a first device couples to a second device, that connection may be through a direct connection such as a shaft, flange or weld connection, or through an indirect electrical connection or a shaft coupling via other devices and connections.
  • fluid is used to refer to generally liquids or gasses or mixtures thereof.
  • liquid refers to a fluid which is primarily, or primarily intended, to be composed of liquid and typically includes the presence of some gas which may be dissolved or entrained in the liquid as bubbles.
  • gas refers to a fluid which is primarily, or primarily intended, to be composed of gas and typically includes the presence of some liquid which may be carried with the gas as mist, droplets, a film, or even as slugs or waves. Gas may be wet, and for thermal operations may be primarily composed of water vapor (steam) or solvent vapor.
  • the term “uphole” is used to refer to the downstream location relative to fluid flow within the pump, corresponding to the direction that fluids are pumped up and out of the wellbore.
  • “downhole” refers to the upstream location relative to fluid flow within the pump, regardless of the horizontal or vertical orientation of the device or wellbore.
  • the term “upper”, or “top” is used to refer to the orientation relative to gravity within a substantially horizontal wellbore, corresponding to the direction that gas will naturally separate or stratify within a substantially horizontal wellbore.
  • bottom or “lower” refers to the orientation relative to gravity within a substantially horizontal wellbore, corresponding to the direction that liquids will naturally separate or stratify within a substantially horizontal wellbore.
  • impeller may be used broadly to refer to rotating components with vanes in this disclosure. Impellers are typically coupled to the shaft via keys or splines, which transmits rotation and torque from the motor to each impeller, although of such keyway or spline is not typically visible in the present drawings. The thrust loads generated by impellers are typically supported axially by the adjacent diffusers in a ‘floater’ design or transmitted through sleeves on the shaft in a ‘compression’ design.
  • Impeller flowpath designs may range from axial-flow designs where the diameter and cross section are constant, helicoaxial flow design where the diameter increases between the fluid entry flowpath and the fluid exit flowpath, radial flow design where the flowpath turns in a radial outward direction, and compression stages where the cross section decreases between the fluid entry flowpath and the fluid exit flowpath.
  • Impeller vane designs may be straight, forward swept, or backward swept, and the profiles of the vanes may be straight, curved at the tip, gradually curved, or angled - the curves or angles in the vane profile may be in either an uphole or downhole direction.
  • Impellers may have two flowpaths separated by a wall – an inward and an outward flowpath.
  • the inward and outward flowpaths may have a similar or different flowpath designs. Certain embodiments of such configuration options are shown as illustrative embodiments throughout this disclosure, but do not cover the full range of options in order to keep the number of figures to a reasonable amount. In locations where a single impeller is located, multiple impellers may be located acting in series, without departing from the spirit of this disclosure. [0037]
  • the term “diffuser” may be used broadly to refer to non-rotating vaned components in this disclosure.
  • the diffusers when paired with axial-flow impellers the diffusers may primarily straighten the flow, and when paired with helicoaxial or radial flow impellers the diffusers may serve to straighten the flow and redirect the flow from a radially outward position to a radially inward at the entrance of the next impeller.
  • the cross-sectional flow area in a diffuser may be increased between the fluid entry flowpath and the fluid exit flowpath which helps convert dynamic pressure to static pressure.
  • Diffuser vanes may be forward swept or backward swept, and the profiles of the vanes may be curved at the tip, gradually curved, or inclined in either an uphole or downhole direction.
  • Diffuser designs may include inserts for impeller seals, impeller supports, shaft seals and shaft supports such as bearings (bushings), and some of the illustrative embodiments throughout this disclosure have been simplified to not show these components as separate pieces, even though they would be present in a typical functional assembly.
  • Diffusers may be sealed and supported within the housing in a resilient manner, such as O-rings - throughout this disclosure a groove for an O-ring may be shown but the O-rings themselves are not shown for the sake of simplicity, even in the assembly cross section views.
  • Diffusers may be sealed and supported upon one another and held in place by a compressive force holding the diffusers together. Typically when diffusers are supported by compression there are interlocking features that prevent a diffuser from spinning. Diffusers may be located upstream or downstream of an impeller. Additionally, thrust bushings, seals and other features functioning to support the adjacent impellers may be used but are not shown. [0038] Impellers and diffusers may be manufactured by a suitable technique in mass production such as by casting, but may also be manufactured with other techniques including machining or 3D printing. [0039] The intake of an ESP is typically located uphole of the seals and motor. The intake is located downhole of the pump.
  • the present disclosure relates generally to the separation of gas and liquid phases of downhole fluids at the intake of a downhole rotary pump and more particularly to an intake and gas separator system to maximize pump efficiency and potential drawdown, especially in gassy wellbores with high flow rates, and high deviation or horizontal wellbores with unstable flow regimes.
  • In gravity-based separators bubbles rise in an upward direction while liquid preferentially flows in a downward direction forming a primary mechanism by which gas separates.
  • Gravity-based separators may be separated into two classes, which may be selected between depending on the inclination at which they are used.
  • Non-horizontal inclination applications e.g., between 0 degrees inclination (vertical) and 88 degrees inclination, they may reverse the flow direction of the flow which limits the amount of gas that can flow in a downhole direction through a flowpath - these may be known as reverse- flow separators, dip tubes, liquid concentrating intakes and other names.
  • the present disclosure is regarding the other class of gravity based separators known as gas avoiders or low-side intakes; and are typically used in substantially horizontal applications (e.g., typically greater than 60 degrees inclination).
  • Gas avoiders operate based on the principle of gravity-based segregation of phases in the wellbore outside of the intake.
  • the flow regimes in which gas avoiders may work include stratified, churn, and slug flow.
  • Prior art low- side intakes are substantially less effective in churn and slug flow and at high flow rates due to their short length.
  • the vertical component of the velocity in the wellbore adjacent to a gas avoider intake must be relatively low to function effectively.
  • Gas avoiders rely on the buoyancy of gas bubbles to rise in the opposite direction that liquid is flowing, therefore the velocity in the low-side of the wellbore (where gas separation is occurring) must be below the bubble rise velocity. Velocity of bubbles is the subject of various studies, and larger bubbles rise faster and are more easily avoided.
  • a typical rule of thumb accepted by industry for sizing dip-tube style gravity-based separators may be a liquid velocity of approximately 6 inches/second for 1 ⁇ 4” bubble sizes.
  • Long intakes and multi-stage intakes with impellers arranged between stages are proposed in PCT application No. CA2022050335 and U.S. Pat. Application No.17/962,323 and C.A. Pat. No. 3,177,821. This same-family disclosure by the present inventor did not include gas avoider or low-side configurations.
  • a multi-stage gravity-based gas separator is proposed in U.S. Pat. No.11,131,180 with multiple stages arranged in parallel.
  • a limited-entry port disposed on the inner housing may be located toward the bottom of each separation stage where the size of said port increases in lower stages (to offset the friction pressure drop for fluid flowing up the inner housing).
  • these restrictions are at the suction end of the pump restrictions may result in gas breakout (or steam flashing in thermal operations), or other flow assurance challenges such as wax, asphaltene, or scale deposition.
  • Another limitation of this approach is that limited entry ports will allow higher volume flow rates of an undesirable fluid (gas), compared to the desired fluid (liquid); therefore, stages which are not functioning effectively and are allowing gas entry may “overcontribute” leading to degraded overall performance.
  • impellers which uses an impeller between each gravity-based gas separation stage improves upon both of these limitations.
  • the impeller causes a pressure increase in the system (vs. a pressure drop in the prior art) and provides the pressure necessary to overcome the frictional pressure loss for liquid flow up the inside tubular which allows for approximately equal (approximately includes nominal deviations from equal) or greater contribution from the lower stages, and may allow for higher reliability avoiding flow assurance challenges, or increase the potential drawdown in the well to increase production.
  • impellers create more pressure when full of liquid compared to gas; therefore, any stages which are exposing the impeller to gas will contribute relatively less volume flow rate as compared to other stages of which the impellers are full of liquid.
  • Impellers have an “autonomous” behavior that is favorable for causing entry of liquid at higher volumetric flow rates than gas when exposed to the same backpressure which may be a significant improvement relative to prior art passive restriction devices.
  • This disclosure did not contemplate the use of eccentrically weighted components for function at substantially horizontal inclination.
  • Gas avoiders as disclosed, with eccentrically weighted components have been used with ESPs as discussed below and in other referenced prior art.
  • the effectiveness of prior art gas avoiders with eccentrically weighted components and a shaft extending therethrough has been limited in gassy wellbores by their short length, and a lack of design features to create a more uniform inflow profile.
  • Prior art that falls in this category appears to have a L:D ratios less than 2:1 and lack design features to provide a more uniform inflow profile over their length.
  • the downward velocity of fluids in the wellbore adjacent to the intake is typically higher than a bubble rise velocity, and a liquid volume reserve adjacent to the inlet openings is typically too small to be practically useful to maintaining liquid inflow during passage of a gas slug.
  • the inflow profile is not uniform, and the highest downward velocity in the wellbore is adjacent to the suction end of the pump which increases the probability and frequency of gas coning into the pump.
  • No.11,162,338 uses an eccentrically weighted component external to the structural housing and is centralized to standoff from the casing wall.
  • the L:D ratio shown in the figures is less than 1:1.
  • a gas avoider intake as disclosed in U.S. Pat. No.9,494,022 uses an eccentrically weighted component external to the structural housing.
  • the L:D ratio shown in the figures is approximately 1.5:1.
  • a gas avoider intake as disclosed in U.S. Pat. No.8,919,432 connects two intake stages in series, with a L:D ratio of approximately 3.3:1. The two intake stages are indexed by 36 degrees in order to provide uniform indexing between 10 total intake – 5 in each stage. Eccentrically weighted components are not utilized.
  • a diffuser between the stages may appear to be shown is not labelled or discussed.
  • An interior flowpath 535 for flow from an upstream stage is provided through a fluted passageway.
  • the device appears to be relatively long for the purpose of accommodating an interesting internal passageway/valve geometry, and despite a reasonably long length, it does not provide a large flow area for inflow, nor does it consider provision of a uniform inflow profile.
  • a gas avoider intake as disclosed in U.S. Pat. No.11,299,973 with an inner eccentrically weighted component, a rotating shaft extending therethrough, and an impeller (auger) located towards the lower end of the inner flowpath. Only a single stage is used.
  • No.7,980,314 uses multiple weighted components within a stage, each to blocking the upper inlet openings in a ring.
  • the weighted components are not eccentrically weighted.
  • Shaft support bearings are not provided between inlet openings.
  • the L:D ratio shown in the figures is approximately 1.7:1.
  • a gas avoider intake as disclosed in U.S. Pat. No.5,588,486 does not include a shaft extending therethrough for a rotary pump.
  • the L:D ratio is approximately equal to 4.9:1 as shown in Fig.3, although this figure is not shown to scale.
  • the L:D ratio shown in Fig.5 is approximately equal to 1.8:1.
  • a tapered inlet opening profile is proposed.
  • a limitation of the single-tapered-slot inlet opening is that in order to effectively provide a uniform inflow profile, the slot must be excessively narrow towards the uphole end as the length is increased. Additionally, practical issues such as limited stiffness, bending, and warping during slot-cutting, become problematic as the L:D ratio is increased. A hole or slot pattern avoids these practical slot-length constraints.
  • a similar disclosure in U.S. Pat. No.10,883,354 does not include the tapered inlet opening profile and instead seeks to use a screen, neither does it include a shaft.
  • a gas avoider intake as disclosed in U.S. Pat. No.11,060,389 does not include a shaft extending therethrough for a rotary pump.
  • a dip tube style gas separator as disclosed in U.S. Pat. No.10,267,135 does not include a shaft extending therethrough for a rotary pump. It has a large L:D ratio, which is made practically possible by the absence of an eccentrically weighted component (it’s actually a dip-tube style separator), and the lack of a rotating shaft. It has a tapered hole pattern seeking to provide a more uniform inflow profile.
  • No.7,270,178 uses an inner eccentrically weighted component and weights which may not be installed over the full length of the inlet opening.
  • the configuration of the weights is not shown, and do not appear to be designed in a manner to control the inflow profile through the inlet openings, nor is the interaction between the weights and the inflow profile considered. It does not include a shaft extending therethrough for a rotary pump.
  • Embodiments of the present disclosure may use multiple gas avoider stages arranged in parallel with an impeller disposed between an inner flowpath and the gravity separation chamber of each stage may improve the gas avoidance efficiency and flow rate capacity of such device while also providing a pressure boost through the impeller to compensate for the frictional pressure losses, and frictional losses may be reduced because the flow rate through each stage (upstream of an impeller) is lower.
  • a wellbore 1 may receive fluids through openings between wellbore and reservoir 3 (for example perforations, screens, ports or other lower completions assembly devices as is known in the art). Fluid flowing in wellbore toward a downhole pump 4 may flow past a downhole rotary motor 6 (which may be electric, hydraulic or other).
  • While a downhole motor 6 is shown, rotation and power may also be provided to the pump of the present disclosure via sucker or continuous rods from a surface drive head. Fluids may be taken in from the wellbore to the downhole rotary pump 9, through intake 10 of the present disclosure. Gas that bypasses the pump intake and any gas that may be exhausted from an active gas separator may flow to surface within the wellbore 1, typically in an annulus 5 formed between the wellbore 1 and the production tubing 2. Liquids within the pump have their pressure boosted sufficiently to overcome the hydrostatic head, friction pressure, and surface backpressure and flow up the production tubing 2 to a surface gathering or collection system for further processing and sale.
  • a wellbore 1 may be substantially horizontal, or otherwise highly deviated.
  • a low-side intake apparatus 10 may be located in a substantially horizontal portion of the wellbore (e.g. inclination between 60 ⁇ and 110 ⁇ from vertical). At this inclination, the flow regime in the wellbore adjacent to the intake 10 may be substantially segregated (which may include stratified, churn, or slugging flow regimes). The primarily liquid phase 7 of fluid in wellbore flowing toward the pump may tend to accumulate on the low-side of the wellbore 1. The accumulation on the low-side may be enhanced by the eccentric components of the production string laying towards the low-side (the gas preferentially flows up the larger/wider part of the eccentric annulus towards the high side).
  • the primarily gas phase 8 of fluid in wellbore flowing toward the pump may tend to accumulate on the high side of the wellbore. While the pump 10 will naturally rest on the low-side of the wellbore 1 where it is ideally submerged in liquid, unstable flow and coning of gas which has a higher relative mobility (lower viscosity and density) may result in free gas entering the intake of the pump even with a low-side oriented inlet. Many horizontal gas avoiders have been proposed attempting to locate or preferentially open inlet holes that are oriented toward the low-side of the pump. Examples include those discussed in detail above and additionally Pat.
  • the present disclosure may form a restriction in only a portion of the inlet opening towards the downstream end, which may be useful to control the inflow profile, and may have a large cumulative flow area through the inlet opening (typically greater than the flow area in the inner flowpath through the device); which is different than a restriction formed by having a restricted inlet opening, as per many prior art devices.
  • Impellers between stages may also provide a beneficial autonomous behavior because stages exposed to liquid may pull the liquid at higher rates into the device compared to stages exposed to gas, compared to prior art designs where gas will preferentially flow into any holes where gas is present because of the lower viscosity and density of the gas.
  • Fig.1 shows a uniformly slotted outer housing which houses inner eccentrically weighted component(s), although the reader should understand that configurations with outer eccentrically weighted component(s) may also be used in the same location.
  • FIG.1B a cross section view of an intake device at Section 1B showing an intake device 10 in a wellbore 1 with a stratified flow where primarily liquid 7 occupies the lower portion of the wellbore while primarily gas 8 occupies the upper portion of the wellbore.
  • the device 10 may comprise a rotatable thru-shaft part, such as a shaft 20, between downstream and upstream ends 10A, 10B, respectively (Fig.1A), of the device 10.
  • the device 10 may comprise an eccentrically weighted part configured for free axial rotation to orient one or more inlet openings 41 toward a base of the low-side intake.
  • the one or more inlet openings 41 may be connected to feed a fluid outlet at the downstream end, such as connects the intake to the pump 9. If multiple stages are used, as discussed in other figures, each stage has a fluid outlet 48B from a fluid flowpath 48.
  • the device 10 may be structured to relatively progressively increase a restriction to intake flow, through the one or more inlet openings 41, in a direction toward the downstream end.
  • the device 10 may be structured to relatively progressively increase the restriction to intake flow to equalize inflow along an axial length of the one or more inlet openings.
  • the one or more inlet openings 41 may be one or more of shaped, patterned, or arranged to progressively decrease intake flow area per axial unit length toward the downstream end.
  • the reference to restricting intake flow refers to the restricting of flux of intake flow through an entry point of the one or more inlet openings at an axial location of the section.
  • the reference to a progressive increase or decrease may refer to the fact that the increase or happens or develops gradually or in stages in an axial direction along the tool.
  • Another more mathematical way of describing the intent of embodiments of the present disclosure to restrict intake flow toward a downstream end of an intake section is by referring to the specific flow coefficient.
  • Specific flow coefficient may be defined as the flow coefficient per unit of length of an intake section.
  • Cvs Q / dL (SG / dP) ⁇ 0.5
  • Cvs the Specific flow coefficient
  • dL is a unit of length
  • SG is the specific gravity of the fluid
  • dP is the pressure drop from the wellbore outside the inlet openings to the intake fluid flowpath.
  • Specific flow coefficient may progressively decrease towards a downstream end of an intake section and thus provides a more uniform inflow profile over the length of the inlet openings.
  • the specific flow coefficient is a function of the inlet opening geometry and any baffles proximate to the inlet openings. Less flow area in the inlet openings results in a lower Cvs.
  • the intake device 10 may comprise an outer housing 30 with openings 31, and an inner eccentrically weighted component comprising a main body 40, weights 42, and inlet opening(s) 41; with a central shaft 20 running therethrough.
  • the eccentrically weighted part (body 40) may be located within the outer housing 30, the outer housing defining one or more housing inlet openings 31. Upstream and downstream couplers 21, 22, at the upstream and downstream ends, respectively, may be present.
  • the eccentrically weighted part (main body 40) may have a weighted housing that is hollow (and may be cylindrical as shown) and defines a fluid flowpath to the fluid outlet.
  • the one or more inlet openings 31 may be defined through a wall of the weighted housing as shown.
  • the liquid 7 to gas 8 interface 7’’ may not be uniform between left and right sides of the intake device 10, which may be common in transient operating conditions. Focusing first on the left side where there is a liquid level, the vertical velocity vectors in the liquid 7’ are shown. The velocity increases as one moves downwards within the crescent shaped annulus formed between the intake device 10 and the wellbore 1.
  • the vertical velocity of the liquid may be less than a bubble rise velocity and the intake may function to avoid gas as desired.
  • the downward velocity at the interface increases and at a certain level may exceed the bubble rise velocity.
  • gas may be coned at a velocity 8’ that is higher compared to velocity of the liquid 7’ due to the relative mobility of gas versus liquid – this is the condition shown with higher velocity gas on the right hand side, and gas may breakthrough in a pathway 8’’ of potentially small channels through the device and liquid level.
  • the pathway that liquids and gas flow may be between the wellbore 1 and the outer housing 30, and between the outer housing 30 and the eccentrically weighted component 40 as shown by the dashed line 8’’.
  • This annular gap between the outer housing 30 and the eccentrically weighted component 40 may be partially restricted by external weights on the eccentrically weighted component (not shown in this Fig.)
  • gas breakthrough events are highly undesirable, and an object of this disclosure is to reduce the frequency and severity of gas breakthrough events by reducing the peak vertical velocity 7’ of the liquid 7 within this annular space by means of the inflow-contributing length of the intake.
  • Fig.2A an example tapered inlet opening profile in an outer housing 30 of an intake device is shown.
  • End connections, adjacent intake stages, and internal components are not shown.
  • the downstream end is at the left side of the page and there is less flow area within the inlet openings 31 towards this downstream end.
  • Slots may be a preferred shape of inlet openings 31 in an outer housing due to their ease of manufacture using a slotting saw (which would not generate the rounded ends on the slots as shown in this Fig.), and such proves sufficient within the housing despite a large open area and a defined and limited maximum gap width for exclusion of debris.
  • Slots may be rolled-top to provide a keystone profile as is known in the art of slotted liner manufacture which improves resistance to plugging.
  • Slots may be sized for the purpose of restricting inflow towards the downstream end, and also for excluding large debris which might otherwise damage or plug the intake device or pump.
  • Typical slot widths for an intake housing with a tapered flow profile may range from 0.010” to 0.500”. For simplicity, there are only 3 ‘steps’ shown, each step comprising a grouping of similar rows of slot design. The slot width shown is relatively large at 0.200” and a housing OD of 5.375”.
  • CFD computational fluid dynamics
  • FIG.2B similar to Fig.2A, an example tapered inlet opening profile in an outer housing 30 of an intake device is shown where the inlet openings are circular holes.
  • FIG.3A an intake device 10 is shown with a single stage and an inner eccentric weighted component. An isometric view showing the tool cut along a vertical longitudinal section line is shown. The section line intersects the outer housing inlet openings 31 and the center of inlet openings 41 of the eccentrically weighted component, which for the purpose of this figure happens to be oriented perfectly to the low-side.
  • the device is shown horizontally, at an inclination of 90 ⁇ , but may be useful at any substantially horizontal inclination, such as the range between 45 ⁇ and 100 ⁇ .
  • Bearings 44 allow free rotation at low torque of the eccentrically weighted component, and may also function to seal the ends.
  • the eccentrically weighted component allows gravity to orient the inlet openings towards the low-side.
  • Bearings may be constrained axially relative to the eccentrically weighted component by a retention feature 43 such as a snap ring installed in a groove.
  • Bearings may be supported at the downhole end (right) by a coupler 21 to the motor seal section and on the uphole end (left) by a coupler 22 to the pump or active gas separator.
  • the coupling between the outer housing 30 and the couplers 21 and 22 are not shown, and may have threaded type connections.
  • the couplers 21 and 22 may be connected to the adjacent pump and seal assembly, respectively, by flanged connections.
  • the coupler 21 to the motor seal section may be solid.
  • the coupler 22 to the pump has passageways for axial flow therethrough.
  • One or more radial bearings may support the rotatable thru-shaft 20 at one or both the upstream and downstream ends of the device 10. Radial bearings may support the rotatable thru-shaft at both the upstream and downstream ends.
  • both couplers 21 and 22 comprise radial bearings for shaft support.
  • a restriction towards the downstream end is not illustrated in Fig.3A; the reader may understand that a restriction towards the downstream end may be formed by a variety of features, as will be illustrated in subsequent Figures.
  • Features that may be used to form a restriction towards the downstream end may include at least: inlet openings in outer housing 31, inlet opening(s) of inner eccentrically weighted component 41, and weights 42.
  • Referring to Fig.3B an alternate eccentrically weighted component is shown wherein the inlet opening 41 is tapered.
  • the tapered inlet opening may provide a restriction to flow towards the downstream end (which may be on the uphole side, except for a configuration such as that shown in Fig. 8D) in order to provide a more uniform inflow profile along the length of the intake section.
  • the slot walls may be a tapered and non-linear contour in order to optimize the uniformity of the inflow profile along the length.
  • the L:D Ratio for the inlet opening of Fig 3B is approximately 4:1.
  • Holes 45 in the eccentrically weighted component main body 40 may be used for attaching eccentric weights 42, which may be visible as shown through the slot, although this alignment is not a necessary feature.
  • the inflow restriction for that portion of the intake may be provided by a combination of the inlet flow area and the flow area between the weights – this behavior will be discussed further in the further figures.
  • Fig.3C an alternative eccentrically weighted component is shown wherein the inlet opening 41 consists of a series of slots.
  • the slot width and length may be varied from the uphole end to the downstream end in order to achieve a more uniform inflow profile.
  • Discrete slots may be advantageous over a single large slot by retaining more strength and straightness within the eccentrically weighted component (avoiding warpage after cutting the slot), which enables the use of longer lengths within a single stage.
  • the L:D Ratio of this intake is 6.8:1.
  • Weights 42 are visible between some of the slots and contribute to the restriction of inflow towards the downstream end of the elongated intake section.
  • the weights 42 do not extend the full length of the intake in order to provide less restriction to the flow from the slots at the furthest upstream end of the intake.
  • the weights may be located on the inner side of the eccentrically weighted component and extend on the upstream end to an axial position that is at least past the furthest downstream slot.
  • the preferred L:D Ratio of a low-side intake section may be similar or longer to what is shown here in Fig.4C; however, because showing the full length requires a smaller drawing scale making it harder to see other features, the remaining Figs. will illustrate a shorter intake section length with a L:D Ratio of approximately 4:1.
  • the size of the weights and how far the center of gravity is moved eccentrically from the center of rotation will depend on the swirl forces exerted by fluid contacted by the central rotating shaft 20. It may be advantageous to use a relatively thin tubular main body for the eccentrically weighted component as the removal of large slots from it move the center of gravity in an undesirable direction. Tall weights may be advantageous for providing a substantial movement in the center of gravity, but also for restricting fluid inflow into the downstream end.
  • the shape of inlet openings 41 may be a single slot, multiple slots, multiple round holes, or any other combination shapes or combination of shapes that provide a restricted flow area towards the downstream end as compared to the upstream end. The amount of flow area per unit of length may change substantially from the downstream end.
  • a ratio of decreasing flow area per axial unit length may be greater than 2:1.
  • An intake part of the low-side intake section may define the one or more inlet openings 41.
  • a ratio of the overall length of the intake part to an outer diameter of the low-side intake section may be greater than 2:1.
  • the ratio of flow area per unit length at the upstream end to the flow area per unit length at the downstream end may be greater 2:1, and preferably greater than 5:1; however, due to constraints around how narrow a slot may be without plugging, and how much weight is lost from the low-side of the tube when very large openings are made, it may be practical to limit the maximum ratio to 20:1, or 10:1.
  • the inflow profile for any hole pattern may be readily simulated by a skilled worker using 3D computational fluid dynamics (CFD), and should consider potential alignment scenarios between the outer housing inlet openings 31 with the eccentrically weighted component inlet opening 41, along with the ecentralization of the device 10 in the wellbore 1, and the properties of the production fluid such as viscosity and density. While a uniform inflow profile along the full length of an intake is theoretically ideal, it practice, it may be preferable to instead bias the inflow profile based on CFD to provide a higher flow rate per unit-length from the upstream end, or the middle or the downstream end, depending on the inputs and boundary conditions used in the simulation.
  • CFD 3D computational fluid dynamics
  • optimization may be completed by a skilled worker using trial and error methods for various slot patterns in transient multiphase CFD simulation or physical experiments.
  • the length between shaft radial support bearings may be excessive for a shaft of a standard design to avoid vibration problems.
  • a variety of mechanical design solutions as are known to a skilled worker may be employed to avoid shaft vibration issues despite a length between radial support bearings that exceeds typical design parameters for radial shaft support spacing, such solutions may include options such as a larger diameter shaft, a hollow shaft, a shaft with more precise straightness tolerances, a sleeved shaft, or use of a material with a high bending-stiffness-to-weight ratio.
  • FIG.4A an alternative eccentrically weighted component is shown in a vertical-longitudinal half-section isometric view with tapered internal weights 42.
  • the inlet opening may be uniform along its length while the inflow restriction towards the downstream end of the intake section may be provided by the tapered weights 42.
  • the tapered weights become a close clearance with an internal central body which may be the shaft or an internal non-rotating housing (not shown in Fig.4A)
  • the close clearance restricts fluid flow from the low-side channel between the weights and into the rest of the flowpath within the eccentrically weighted component main body 40 towards the upper side.
  • the one or more inlet openings 41 may be structured and arranged to provide consistent flow area per axial unit length toward the downstream end.
  • the weights may extend full length towards the upstream end as shown, or they may be partial length at the upstream end as per Fig.3C.
  • Tapered weights are one example of the defining of one or more baffles, on an interior surface of the weighted housing, to regulate intake flow from the one or more inlet openings to the fluid flowpath.
  • the tapered weights, or other baffle structure may be structured to decrease a radial overflow clearance defined between the one or more inlet openings and the fluid flowpath, in a direction toward the downstream end.
  • the fluid flowpath may comprise a majority is separated from inlet openings by a baffle structure, and it is this majority portion which may be referred to as the fluid flowpath; notwithstanding the reader should understand that there may also be a minority portion of the fluid flowpath which is axially aligned with the inlet openings and this minority portion may also be in fluid communication with the fluid outlet, or this minority portion may be in fluid communication with the fluid outlet with a secondary baffle restricting axial flow from this minority portion of the fluid flowpath to the outlet (not shown).
  • one or more eccentric weights may be mounted or formed on an interior surface of the weighted housing.
  • An intake device is shown with an alternative eccentrically weighted component in a longitudinal section view that intersects the tapered weights with tapered internal weights 42 and tapered external weights 42’.
  • the cross section line does not intersect the outer housing 30 inlet openings 31, although some of the inlet openings 31 are visible behind the cross section line.
  • the eccentric weighted component 40 inlet opening is not visible.
  • External weights 42’ partially block the annular space formed between the eccentrically weighted component 40 and the outer housing 30. By restricting this annular flowpath with external weights 42’ towards the downstream end of the intake section, a more uniform inflow profile may be achieved.
  • the external weights are also useful for moving the center of gravity downwards in the eccentrically weighted component, and may be coupled to the main cylindrical tube of the eccentrically weighted component with a variety of techniques as would be understood by a skilled worker, for example using machine screws or rivets in holes 45, or by welding, brazing, etc; alternatively the weights and generally cylindrical tube may be integral.
  • Each eccentric weight 42 is shown for simplicity as a single piece coupled to the main body, which may be relatively expensive to manufacture; cheaper configurations may use multiple pieces to form the general profile of the tapered weight.
  • the tapered weights may be mounted or formed on an exterior surface of the weighted housing.
  • the one or more baffles may be structured to increase in radial thickness, in a direction toward the downstream end.
  • An alternative eccentrically weighted component is shown from a bottom view.
  • a tapered profile of inlet openings 41 with a slotted shape is shown, with a restrictive pattern towards the downstream end (left side of page).
  • Tapered external weights 42’ may be mounted to the main body 40 of the eccentrically weighted component with couplers in holes 45.
  • the tapered external weights extend partial length, covering the downstream end, but do not cover the full length of the inlet openings 41 towards the upstream end (right). External tapered weights may be useful for restricting flow through the annular space between an eccentric weighted component 40 and an outer housing 30.
  • Restricting flow through this annular space may improve the performance of the device. Restricting flow through this annular space may important for configurations where there is relatively lower open flow area in the outer housing, or if there is a relatively large gap between the eccentrically weighted component and the outer housing.
  • the example shown is an example of the use of a pair of baffles, one on either lateral side of the one or more inlet openings.
  • the interior flowpath area of the external eccentrically weighted component 40 may exclude the structural housing 35 as shown in Fig.5A, or alternatively the interior flowpath area of an external eccentrically weighted component may encompass (or encircle) the structural housing 35, with a cross section profile similar to that disclosed in US. Pat. No. 9,494,022.
  • the shaft 20 extends through the length of the intake.
  • the eccentrically weighted component comprises generally cylindrical couplings 46 on both ends which may be coupled to couplers 21 and 22 with bearings to permit free rotation of the weighted component. Bearings may be supported at the downhole end (right) by a coupler 21 to the motor seal section and on the uphole end (left) by a coupler 22 to the pump or active gas separator.
  • the bearings are internal and not visible in Fig.5; the connection between the structural housing 35 and couplers 21 and 22 are not shown and may be threaded type connections.
  • the couplers 21 and 22 may be connected to the adjacent pump and seal assembly, respectively, by flanged connections as shown.
  • the coupler 21 to the motor seal section on the downhole end may be solid (without a flowpath from below), when there is no other intake stage below.
  • the coupler 22 to the pump has passageways for axial flow therethrough. Both couplers 21 and 22 comprise radial bearings 23 for shaft support.
  • a metal guide channel 50 for the ESP power cable (typically referred to as a motor lead extension) may be used to prevent the cable from bending into a position that may interfere with the free rotation of the eccentrically weighted component 40.
  • Bearings and supporting the free rotation of the eccentrically weighted component 40 and seals between it and the couplers 21 and 22 are not shown; these seals and bearings may be arranged similar as shown other figures, or other various configurations of bearings and seals would be possible.
  • Fig.5B a cross section view at Section 5B showing an intake device with an eccentrically weighted component 40 that does not encompass (over its full length) the structural housing 35 or the shaft 20.
  • the shape of the eccentric weighted component 40 in this embodiment provides an eccentric center of gravity such that dedicated weighted components are not necessary.
  • a primary benefit of this configuration may be that a void space 51 external to the intake is formed adjacent to the intake.
  • This void space 51 effectively increases the cross section of the annular space between the intake and the wellbore, which reduces velocity of fluids in the wellbore which enhances gas separation in the wellbore, ultimately improving the effectiveness of gas separation.
  • the cable guide 50 may be held at an OD at least as large as the coupler 22, which may be larger than the maximum diameter of the eccentrically component 40 or the maximum diameter of end couplings 46. Inlet openings 41 are visible.
  • a multi-stage low-side intake device 10 may be provided for a downhole rotary pump comprising a plurality of the low-side intake sections (devices 10) coupled together. Each low-side intake section may define a fluid flowpath between the one or more inlet openings and the fluid outlet.
  • the fluid flowpaths of the low-side intake sections may connect to collectively pass fluids from the low-side intake sections downstream.
  • Illustrated is a vertical cross section view of an intake with a similar geometry to Fig.5A is shown, with multiple stages axially connected.
  • a shaft 20 runs through the entire length of the intake device and may be supported by radial bearings 23, which may be supported by vanes or ribs 24 inside couplers 21, 22, 25.
  • Couplers 25 between intake stages are shown with a flanged connection with fasteners 26 as bolts, which may be necessary for inserting an impeller as per the next figures; however, for the assembly in Fig.6A the coupler 25 may instead be a single piece.
  • An inner housing 35 supports structural loads through the intake and may be coupled to the couplers 212225 by threaded connections.
  • Each low-side intake section may be configured to permit independent rotation of the eccentric weighted part (body 40) relative to the other of the low-side intake sections.
  • Anti-backoff mechanisms for a threaded connection may be required such as set screws or retention pins or other means as would be understood by one skilled in the art.
  • the eccentrically weighted component 40 may be supported by bearings 44 which are retained by snap rings 43 within the couplers 46 at the ends of the eccentrically weighted component 40.
  • a seal may be formed between the couplers 21, 22, 25 and the ends of the eccentrically weighted component in order to prevent gas being ‘sucked in’ through the gap, especially the portion of the gap oriented towards the high side.
  • bearings 44 are shown at the smaller diameter seal location, however bearings may be used also (or instead) at the larger diameter seal location.
  • the tapered inlet opening profile 41 is not shown in detail in this figure, but as described and shown in other figures, it may include restricted openings towards the downstream end (left side of page).
  • the inlet openings in an upstream stage (right half of page) may be substantially larger than the inlet openings in a downstream stage.
  • a shaft 20 runs through the entire length of the intake device and may be supported by radial bearings 23, which are supported by vanes or ribs 24 inside couplers 21, 22, 25. Couplers may be supported on each other in axial compression and radially within the outer housing 30.
  • the eccentrically weighted component 40 may be supported bearings 44 which may be retained by snap rings 43 within the 46 at the ends of the eccentrically weighted component 40.
  • Weights 42 may be connected to the eccentrically weighted component 40 to orient the inlet openings 41 towards the low-side. In this embodiment, tapered internal weights are shown, with effects on the inflow profile as described earlier.
  • a seal may be formed between the couplers 212225 and the ends of the eccentrically weighted component in order to prevent gas being ‘sucked in’ through the gap oriented towards the high side.
  • a tapered inlet opening profile 41 is present although hard to see in this figure where the inlet opening is narrower towards the downstream end (left side of page) within each stage and each stage also has a progressively narrower inlet opening towards the downstream end as compared to the adjacent stage. Three intake stages are shown, but the reader may understand that any number of stages greater than two may be used to increase the length of the intake to increase the efficiency of gas avoidance.
  • the L:D Ratio is 14.3:1.
  • the exposed rotating shaft 20 may impart a swirl in the fluid which may be exposed to the eccentrically weighted component and may cause the eccentrically weighted component to spin.
  • the vanes 24 located between each stage may be swept the opposite direction to counteract the swirl from the shaft 20.
  • the details of couplings to the motor seal below and the pump above are not shown.
  • a mechanism for preventing rotation of the coupler may be required (but is now shown), which may include O-rings, set screws, interlocking components or keys or other similar couplers. O-rings may not be practical for use between an outer housing 30 with many openings and couplers 25.
  • each low-side intake section may comprise an impeller structured to convey fluid from the respective fluid flowpath 48 of each intake section into the fluid flowpath 48 of the adjacent section located uphole.
  • the fluid flowpaths 48 of the low-side intake sections connect to collectively pass fluids from the low-side intake sections downstream. While it may be described and claimed as each intake section comprising an impeller, this may be implemented by every section having an impeller, or by having one less impeller than there are stages, since the impeller may not be required for function at the junction at the pump inlet.
  • the number of impellers may be equal to n or n-1 (Fig.7A is shown with n-1 impellers, while Fig.8A following is shown with n impellers). Additionally, if multiple impellers are used generally at a location between stages where an impeller is described in the present disclosure, it does not depart from the spirit of the invention – the number of impellers may in fact be 2n, 2(n-1), 3n...etc. Components and arrangements are consistent with Fig.6A and only the differences are discussed here. Impeller 60 may be straddled by two couplers 25 on the upstream end and 25’ on the downstream end.
  • Both diffusers comprise vanes (24 and 24’ respectively), with the purpose of straightening any swirl or pre-swirl that may be induced by the rotating impeller 60 which may undesirably cause eccentrically weighted components 40 to spin.
  • the impeller is shown as a floating design where thrust loads may be born by the adjacent diffuser.
  • An alternative embodiment where sleeves or other components are used to constrain these components axially may equally be used.
  • the inlet openings 41 of an upstream stage may not comprise a larger flow area pattern as compared to the inlet openings 41 a downstream stage (left side of page), since the power from the impeller is sufficient to motivate the fluid flow the upstream stage.
  • the inlet opening profile varies within the eccentrically weighted component of each stage, as previously discussed.
  • Fig.7B a vertical cross section view of an intake with a similar geometry to Fig.6B is shown, with an impeller 60 between intake stages. Components and arrangements are consistent with Fig.6B and only the differences are discussed here. Impeller 60 may be straddled by two couplers 25 on the upstream end and 25’ on the downstream end. Both diffusers comprise vanes (24 and 24’ respectively), with the purpose of straightening any swirl or pre-swirl that may be induced by the rotating impeller 60 which may undesirably cause eccentrically weighted components 40 to spin.
  • the inlet openings 41 of an upstream stage may not comprise a larger flow area pattern as compared to the inlet openings 41 a downstream stage (left side of page), since the power from the impeller is sufficient to motivate the fluid flow from the upstream stage.
  • the inlet opening profile varies within the eccentrically weighted component of each stage, as previously discussed.
  • Fig.8A a vertical cross section view of an intake with a similar geometry to Fig.7A is shown, with an inner housing 35 substantially larger than the shaft 20 to form an annular inner common flowpath 36 for the flow from an upstream intake stage through the inner housing 35.
  • the inner housing 35 may be located radially inward of the eccentrically weighted part.
  • the inner common fluid flowpath 36 may extend between the upstream and downstream ends of the low-side intake section, for example having an inner common fluid inlet 36A and an inner common fluid outlet 36B at such ends.
  • the fluid flowpaths of the low-side intake sections may connect in parallel to collectively pass fluids from the low-side intake sections downstream into the inner common flowpath 36.
  • the inner common fluid flowpath 36 may be structured to receive fluid from a fluid flowpath located downhole of the fluid outlet of the fluid flowpath.
  • the inner common fluid flowpaths 36 may be connected to receive fluid from the fluid flowpaths of the low-side intake section located downhole of the at least one low-side intake section. Components and arrangements are consistent with Fig.7A and the substantial differences are discussed here.
  • the eccentrically weighted component 40 may be external to the structural housing 35.
  • the coupler 25’ between intake stages downstream of the impeller 60 may have a flowpath therethrough for the flow from upstream stage(s).
  • the coupler 25 upstream of the impeller 60 may have a flowpath that comingles the flow from an upstream eccentrically weighted component 40 and a further upstream eccentrically weighted component 40’.
  • Vanes 24 support shaft bearings 23.
  • the vanes 24 are only shown upstream of the impeller 60, however an alternative embodiment may have vanes also downstream in close proximity to the impeller 60. Vanes downstream of the impeller may prevent pre-swirl from the impeller from imparting a spin to the upstream eccentrically weighted component.
  • a “compression” design is shown, wherein a sleeve 20’ provides axial support to impellers 60.
  • the impeller 60 may have an axial flow design, or a helicoaxial design (not shown).
  • One advantage of this arrangement is the ability to substantially lengthen the overall intake, because the flow from upstream stages does not directly interact with the inflow from a downstream stage.
  • Another advantage is that the flow downstream of an impeller does not interact with an eccentrically weighted component 40, and therefore there is less risk of causing an eccentrically weighted component to spin.
  • Impellers 60 may have various designs throughout the length of an intake with multiple stages, for example, an upstream impeller 60’ may have a diameter, or a lower pitch, or less vanes relative to a downstream impeller 60.
  • the inner housing 35 may have a telescoping design wherein the diameter of the inner housing in upstream stages may be smaller. Because each stage is motivated by an impeller, the inlet opening profile 41 of each stage may be substantially the same, but still provide a relatively uniform inflow profile over the entire multistage intake length because of the impellers located between stages. The inlet opening profile varies within the eccentrically weighted component of each stage, as previously discussed. In alternative embodiments, impellers between intake stages or between certain intake stages are not necessary.
  • Fig.8B a vertical cross section view of an intake with a similar geometry to Fig.7B is shown, with an inner housing 35 substantially larger than the shaft 20 to form a flowpath 36 for the flow from an upstream intake stage through the inner housing 35.
  • Upstream flowpaths 36’ may be connected to feed fluid from the one or more upstream intake sections to the fluid flowpath 36.
  • the eccentrically weighted component 40 may be internal to housing 30 with openings 31.
  • the coupler 25’ between intake stages downstream of the impeller 60 may have a flowpath therethrough for the flow from upstream stage(s).
  • the coupler 25 upstream of the impeller 60 maintains separate flowpaths for the flow from an upstream eccentrically weighted component 40 and a further upstream eccentrically weighted component 40’.
  • the impeller 60 may have separate flowpaths and the flow may be comingled after passing the impeller 60, and is illustrated in Fig.8C.
  • Vanes 24 support shaft bearings 23.
  • the vanes 24 are only shown upstream of the impeller 60, however an alternative embodiment may have vanes also downstream in close proximity to the impeller 60.
  • a “compression” design is shown, wherein a sleeve 20’ provides axial support to impellers 60.
  • the inward portion of the impeller 60 may have an axial flow design, and the outward portion of the impeller 60 may have a helicoaxial design, although other impeller design types may be used.
  • One advantage of this arrangement is the ability to substantially lengthen the overall intake to improve gas avoidance effectiveness, and is enabled because the flow from upstream stages does not directly interact with the inflow from a given stage.
  • Another advantage is that the flow downstream of an impeller does not interact with an eccentrically weighted component 40, and therefore there is less risk of causing an eccentrically weighted component to spin.
  • the outward portion of the impeller with a helicoaxial or radial design is able go generate substantially more pressure (or head) compared to the inward portion with an axial design; and this is advantageous because it permits the entire inner flowpath 36 to operate an elevated pressure. This is advantageous because the positive pressure avoids concern of gas getting sucked into any leaky seals or connections. It is also advantageous because any intake stage which may happen to be intaking an undesirable higher concentration of gas will generate less pressure and flow rate through the outward portion of the impeller (and potentially gas locking entirely and backflowing), thereby autonomously blocking the excessive production of gas from any intake stage which happens to have allowed gas to inflow.
  • Impellers 60 may have various designs throughout the length of an intake with multiple stages, for example, an upstream impeller 60’ may have a lower pitch in the inward portion, or less vanes associated with the lower flowrate through impellers towards the upstream end of a multistage intake device. Additionally, in embodiment, not shown, the inner housing 35 may have a telescoping design wherein the diameter of the inner housing in upstream stages may be smaller. Because each stage is motivated by an impeller, the inlet opening profile 41 of each stage may be substantially the same, but still provide a relatively uniform inflow profile over the entire multistage intake length because of the impellers located between stages. [0075] Referring to Fig.8C a detail view of a junction between the stages of Fig.8B is shown.
  • the inner common fluid flowpath 36 is structured to receive fluid 70 from a fluid flowpath 48 located downhole of the fluid outlet 48B of the fluid flowpath 48.
  • Each impeller 60 may have a radially inward vane portion and a radially outward vane portion, which are structured to convey fluids from the upstream inner common flowpath (36’) and the fluid flowpath 48, respectively.
  • An impeller 60 has an outward portion (radially outward vane portion) for flow 70 from the eccentrically weighted component of the same stage.
  • An inward portion (radially inward vane portion) of impeller 60 is for flow 71 from an upstream stage.
  • the eccentrically weighted component 40 may be supported by external bearings 44 located between it and the housing 30.
  • the bearings may be located on the inside between the eccentrically weighted component 40 and a coupler 25 or 25’ (or couplers 21, or 22 as per other figures).
  • Each impeller may be structured to convey fluids via the radially outward vane portion generating a higher relative pressure than the radially inward portion.
  • Fig.8D a detail view of a junction between the stages of a multistage intake is shown.
  • the inner common fluid flowpath 36 is structured to receive fluid 70 from a fluid flowpath located uphole of the fluid outlet of the fluid flowpath.
  • the arrangement is similar to that of Fig.8C with a reversal in the flow direction in the eccentric weighted component 40 and the outward portion of impeller 60.
  • the impeller of an intake stage may be located downhole of the fluid flowpath of the intake section.
  • This configuration may be advantageous for the ability to combine the functions of a gas avoider wherein gas is separated by orientation within the wellbore, and a dip-tube gas separator wherein gas is separated by axial position within the wellbore because the flow 70 within the eccentric weighted component 40 is in a downhole direction. It may also be advantageous for compatibility of parts and inventory for a multistage dip tube style gas separator which may optionally include eccentric weighted components 40 for very high angle installations.
  • Prior art separators as per Canadian Pat.
  • Application No.3,177,821 may be improved for very high inclination pump applications such as installation at an inclination of greater than 80 degrees, or greater than 85 degrees, or greater than 88 degrees with this improvement, which is the addition of an eccentrically weighted component.
  • Table of Parts 1 Wellbore, 2 Production Tubing, 3 Openings between wellbore and reservoir, 4 Fluid flowing in wellbore towards pump, 5 The Annulus (between the wellbore wall and the pump or production tubing) which extends to surface as a distinct flowpath for gas, 6 Downhole rotary motor, 7 Primarily liquid phase of fluid in stratified or slugging flow in wellbore towards pump, 7’ vertical velocity vectors in the liquid adjacent to the inlet openings, 7’’ liquid-gas interface, 8 Primarily gas phase of fluid flow in wellbore towards pump, 8’ vertical velocity vectors in the gas adjacent to the inlet openings, 8’’ gas breakthrough pathway into the inlet 9
  • Rotary pump 10 intake apparatus, 10A - upstream end of apparatus 10, 10B

Landscapes

  • Engineering & Computer Science (AREA)
  • Mining & Mineral Resources (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Physics & Mathematics (AREA)
  • Environmental & Geological Engineering (AREA)
  • Fluid Mechanics (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

L'invention concerne divers outils de fond de trou, comprenant des séparateurs d'admission et de gaz pour une pompe rotative de fond de trou. De multiples admissions avec un composant à poids excentrique orienté par gravité sont prévues lesquelles assurent un profil d'entrée plus uniforme sur une longueur étendue pour améliorer l'efficacité d'évitement de gaz. L'invention concerne également des admissions à étages multiples conçues en parallèle et en série, éventuellement avec des roues entre étages. L'invention concerne également des appareils et des procédés associés.
PCT/CA2023/050806 2023-06-12 2023-06-12 Admissions côté bas pour pompes de fond de trou, et appareils et procédés associés Pending WO2024254670A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/CA2023/050806 WO2024254670A1 (fr) 2023-06-12 2023-06-12 Admissions côté bas pour pompes de fond de trou, et appareils et procédés associés

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/CA2023/050806 WO2024254670A1 (fr) 2023-06-12 2023-06-12 Admissions côté bas pour pompes de fond de trou, et appareils et procédés associés

Publications (1)

Publication Number Publication Date
WO2024254670A1 true WO2024254670A1 (fr) 2024-12-19

Family

ID=93851141

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CA2023/050806 Pending WO2024254670A1 (fr) 2023-06-12 2023-06-12 Admissions côté bas pour pompes de fond de trou, et appareils et procédés associés

Country Status (1)

Country Link
WO (1) WO2024254670A1 (fr)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019173909A1 (fr) * 2018-03-12 2019-09-19 Raise Production Inc. Système et procédé de séparation de puits de forage horizontal
WO2020072078A1 (fr) * 2018-10-05 2020-04-09 Halliburton Energy Services, Inc. Séparateur de gaz avec réservoir de fluide et admission auto-orientable
US20200141222A1 (en) * 2018-11-01 2020-05-07 Exxonmobil Upstream Research Company Downhole Gas Separator

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019173909A1 (fr) * 2018-03-12 2019-09-19 Raise Production Inc. Système et procédé de séparation de puits de forage horizontal
WO2020072078A1 (fr) * 2018-10-05 2020-04-09 Halliburton Energy Services, Inc. Séparateur de gaz avec réservoir de fluide et admission auto-orientable
US20200141222A1 (en) * 2018-11-01 2020-05-07 Exxonmobil Upstream Research Company Downhole Gas Separator

Similar Documents

Publication Publication Date Title
US11299973B2 (en) Gas separator with fluid reservoir and self-orientating intake
US9638000B2 (en) Method and apparatus for controlling the flow of fluids into wellbore tubulars
US8141625B2 (en) Gas boost circulation system
CA2639428C (fr) Separateur de gaz dans une enveloppe de systeme de pompage submersible electrique (esp)
US12292059B2 (en) Intakes and gas separators for downhole pumps, and related apparatuses and methods
US11162338B2 (en) Electric submersible pump (ESP) intake centralization
US20180094515A1 (en) Downhole Pumping Systems and Intakes for Same
US10260324B2 (en) Downhole separation efficiency technology to produce wells through a single string
CN117355662A (zh) 电潜泵（esp）气塞处理器和减轻系统
WO2016160016A1 (fr) Chambres d'équilibrage dans des pompes électriques submersibles
US12173590B2 (en) Electric submersible pump with improved gas separator performance in high viscosity applications
US11174872B2 (en) Anti-spin pump diffuser
WO2024072510A1 (fr) Extension d'admission de fluide d'ensemble pompe submersible électrique (esp)
WO2024254670A1 (fr) Admissions côté bas pour pompes de fond de trou, et appareils et procédés associés
US10260518B2 (en) Downhole electrical submersible pump with upthrust balance
CN109415934B (zh) 用于水平井中的聚合物注入的交替螺旋流控制装置
CA2581136C (fr) Separateur de gaz
CA3120183C (fr) Passage d'arbre de reamorcage a verrouillage de gaz dans une pompe de puits submersible et procede de reamorcage de la pompe
US10260321B2 (en) Inflow control device for polymer injection in horizontal wells
CN108590544B (zh) 一种水平井井下防砂防气装置及应用方法

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 23940955

Country of ref document: EP

Kind code of ref document: A1