WO2016137927A1 - Procédés et systèmes de mise sous pression de fluides agressifs - Google Patents

Procédés et systèmes de mise sous pression de fluides agressifs Download PDF

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Publication number
WO2016137927A1
WO2016137927A1 PCT/US2016/019034 US2016019034W WO2016137927A1 WO 2016137927 A1 WO2016137927 A1 WO 2016137927A1 US 2016019034 W US2016019034 W US 2016019034W WO 2016137927 A1 WO2016137927 A1 WO 2016137927A1
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WO
WIPO (PCT)
Prior art keywords
fluid
harsh
tubulars
high pressure
piston
Prior art date
Application number
PCT/US2016/019034
Other languages
English (en)
Inventor
Sandeep Verma
Terizhandur S. Ramakrishnan
Jahir Pabon
John David Rowatt
Original Assignee
Schlumberger Technology Corporation
Schlumberger Canada Limited
Services Petroliers Schlumberger
Schlumberger Technology B.V.
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 Schlumberger Technology Corporation, Schlumberger Canada Limited, Services Petroliers Schlumberger, Schlumberger Technology B.V. filed Critical Schlumberger Technology Corporation
Priority to US15/552,749 priority Critical patent/US20180030968A1/en
Priority to CN201680021707.8A priority patent/CN107454926B/zh
Priority to RU2017131414A priority patent/RU2673895C1/ru
Publication of WO2016137927A1 publication Critical patent/WO2016137927A1/fr

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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
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
    • F04B9/103—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having only one pumping chamber
    • F04B9/105—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having only one pumping chamber reciprocating movement of the pumping member being obtained by a double-acting liquid motor
    • F04B9/1053—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having only one pumping chamber reciprocating movement of the pumping member being obtained by a double-acting liquid motor one side of the double-acting liquid motor being always under the influence of the liquid under pressure
    • 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
    • E21B41/00—Equipment or details not covered by groups E21B15/00 - E21B40/00
    • 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
    • E21B43/25—Methods for stimulating production
    • E21B43/26—Methods for stimulating production by forming crevices or fractures
    • E21B43/2607—Surface equipment specially adapted for fracturing operations
    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/02—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having two cylinders
    • 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
    • F04B15/00—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • 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
    • F04B19/00—Machines or pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B1/00 - F04B17/00
    • F04B19/20—Other positive-displacement pumps
    • F04B19/22—Other positive-displacement pumps of reciprocating-piston type
    • 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
    • F04B23/00—Pumping installations or systems
    • F04B23/02—Pumping installations or systems having reservoirs
    • 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
    • F04B23/00—Pumping installations or systems
    • F04B23/04—Combinations of two or more pumps
    • 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
    • F04B47/08—Pumps or pumping installations specially adapted for raising fluids from great depths, e.g. well pumps having motor-pump units situated at great depth the motors being actuated by fluid
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • F04B53/12—Valves; Arrangement of valves arranged in or on pistons
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • F04B53/162—Adaptations of cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F13/00—Pressure exchangers

Definitions

  • the subject disclosure relates generally to methods and systems for pumping a fluid from a surface of a well to a wellbore at high pressure. More particularly, the subject disclosure relates to a pressure exchanger which exchanges pressure energy from a high pressure flowing fluid system to a relatively low pressure flowing fluid system.
  • pump assemblies are used to pump a fluid from the surface of the well to a wellbore at extremely high pressure.
  • Such applications include hydraulic fracturing, cementing, and pumping through a coiled tubing, among other applications.
  • a multi-pump assembly is often employed to direct an abrasive containing fluid, or fracturing fluid through a wellbore and into targeted regions of the wellbore to create side "fractures" in the wellbore.
  • the fracturing fluid is pumped at extremely high pressures, sometimes in the range of 10,000 to 15,000 psi or more.
  • the fracturing fluids contain an abrasive proppant which both facilitates an initial creation of the fracture and serves to keep the fracture "propped" open after the creation of the fracture.
  • These fractures provide additional pathways for underground oil and gas deposits to flow from underground formations to the surface of the well. These additional pathways serve to enhance the production of the well.
  • Plunger pumps are typically employed for high pressure oilfield pumping applications, such as hydraulic fracturing operations. Such plunger pumps are sometimes also referred to as positive displacement pumps, intermittent duty pumps, triplex pumps or quintuplex pumps. Plunger pumps typically include one or more plungers driven by a crankshaft toward and away from a chamber in a pressure housing (typically referred to as a "fluid end") in order to create pressure oscillations of high and low pressures in the chamber. These pressure oscillations allow the pump to receive a fluid at a low pressure and discharge it at a high pressure via one-way valves (also called check valves).
  • one-way valves also called check valves
  • Multiple plunger pumps are often employed simultaneously in large-scale hydraulic fracturing operations. These pumps may be linked to one another through a common manifold, which mechanically collects and distributes the combined output of the individual pumps. For example, hydraulic fracturing operations often proceed in this manner with perhaps as many as twenty plunger pumps or more coupled together through a common manifold.
  • a centralized computer system may be employed to direct the entire system for the duration of the operation.
  • a method of pumping an oilfield fluid from a well surface to a wellbore comprises operating at least one low pressure pump to pump a harsh fluid; operating at least one high pressure pump to pump a clean fluid; using a piston which is in contact with clean fluid in its direction of movement and which pushes the clean fluid using the pressure from the high pressure pump in order to provide pressure to the harsh fluid, thereby pumping the harsh fluid into the wellbore.
  • the harsh fluid is not in contact with the piston assembly when pressurized by the high pressure pump.
  • the harsh fluid is not in contact with either side of the piston.
  • a system for pumping an oilfield fluid from a well surface to a wellbore comprises at least one low pressure pump in communication with a supply of harsh fluid; at least one high pressure pump in communication with a clean fluid; and a tubular comprising a piston assembly, wherein the piston assembly is in contact with clean fluid in its direction of movement and the piston assembly pushes the clean fluid using the pressure from the high pressure pump in order to provide pressure to the harsh fluid, thereby pumping the harsh fluid into the wellbore.
  • harsh fluid under high pressure is not in contact with the piston.
  • a system for uninterrupted high pressure pumping of an oilfield fluid from a well surface to a wellbore includes at least one pair of tubulars, each comprising a piston assembly, with one tubular of a pair in a high pressure cycle phase while another tubular of the pair is in a low pressure cycle phase.
  • Figures 1-5 are schematics depicting an embodiment of the subject disclosure at multiple stages of a half cycle;
  • Figures 6-10 are schematics depicting another embodiment of the subject disclosure at multiple stages of a cycle where the embodiment includes a "stop" element toward the end of the tubular and a check valve in the piston;
  • Figure 11 depicts one design of a piston for embodiments of the subject disclosure.
  • Figures 12a - 12f depict multiple stages of a sequence of operation of an embodiment of the subject disclosure using check valves.
  • Embodiments of the subject disclosure generally relate to a pumping system for pumping a fluid from a surface of a well to a wellbore at high pressure and more particularly to such a system that includes using clean fluids to transfer pressure to the harsh fluids. This provides a low cost of operation for these systems.
  • FIG. 1-5 depict an embodiment of the subject disclosure operating at multiple points of a half-cycle.
  • System 10 includes two storage tanks 20, 30, three pumps 42, 44, 46, two (complementary) tubulars 50, 60 with respective first ends 50a, 60a and second ends 50b, 60b having respective pistons 55, 65, ten solenoid valves SV-1 through SV-10, and a series of pipes 71-78 that contain clean fluid 95, e.g., water, and a series of pipes 81-85 often containing harsh fluids 96.
  • the clean fluid 95 is shown in the Figures with a lighter color and the harsh fluid 96 is shown with a darker color.
  • Storage tank 20 is provided for the clean fluid while storage tank 30 is provided for the harsh fluid.
  • Pump 42 is a high pressure pump for the clean fluid.
  • "high" pressure is to be understand as a relative term relative to “low” pressure, and in various embodiments can generate 5,000 psi, or 10,000 psi, or 15,000 psi, or more, or pressures therebetween.
  • the high pressure pump may be a triplex or a quintuplex pumps.
  • Pumps 44 and 46 are low pressure pumps for the clean and harsh fluids respectively.
  • low pressure is to be understood as a relative term relative to “high” pressure, and in various embodiments can generate 20 psia, or 60 psia, or 100 psia or pressures therebetween or other lower or higher pressures that are lower than the high pressure pump pressure.
  • the low pressure pumps may be C Pumps.
  • storage tank 20 is coupled to low pressure pump 44 via pipe 71.
  • the output of low pressure pump 44 is coupled to a second end 50b of the tubular 50 via pipe 72 and valve SV-5 and to a second end 60b of the tubular 60 via pipe 73 and valve SV-6.
  • Storage tank 20 is also coupled to high pressure pump 42 via pipe 74.
  • the output of high pressure pump 42 is coupled to a first end 50a of the tubular 50 via pipe 75 and valve SV-1 and to the first end 60a of tubular 60 via pipe 76 and valve SV-2.
  • Storage tank 20 is further coupled to the first end 60a of tubular 60 via pipe 77 and valve SV-4 and to the first end 50a of tubular 50 via pipe 78 and valve S V-3.
  • Storage tank 30 is coupled to low pressure pump 46 via pipe 81.
  • Low pressure pump 46 pumps harsh fluid from storage tank 30 to the second end 50b of tubular 50 via pipe 82 and valve SV-7 and to the second end 60b of tubular 60 via pipe 83 and valve SV-8.
  • the second ends of tubulars 50 and 60 are also coupled to a high pressure manifold (not shown) via valves SV-9 and SV-10 respectively.
  • valves SV-2 and SV-10 are opened in order to fill tubular 60 with clean fluid (thereby pushing piston 65 to the second end 60b of tubular 60).
  • SV-1 and SV9 are opened in order to fill tubular 50 with clean fluid (thereby pushing piston 55 to the second end 50b of tubular 50).
  • valves SV-1 and SV-9 are closed. Valves SV-6 and SV-3 are then opened in order to introduce a predetermined amount of clean fluid 95a to the second-end side of piston 55.
  • valve SV-5 is then closed. With valve SV-5 closed, pump 46 is started, and valves SV-7 and SV-3 are opened. Valve SV-7 permits the injection of harsh fluid on the second end side of the piston 55 into tubular 50, and valve SV-3 permits clean fluid ejected from the front end 50a of tubular 50 to be directed back to storage tank 20. Harsh fluid is injected into tubular 50 until piston 55 travels to the first end 50a of tubular 50.
  • valves SV-1, SV-4, SV-6 and SV-9 are open and valves SV-2, SV-3, SV-5, SV-7, SV-8 and SV-10 are closed.
  • clean fluid from tank 20 may be pumped under high pressure via pump 42 and valve SV-1 into the first end of tubular 50 in order to push piston 55 forward.
  • Piston 55 in turn, displaces the clean fluid buffer 95a directly in front of it and the harsh fluid 96 in front of the clean fluid buffer toward the second end 50b of tubular 50 and out through valve SV-9 and pipe 85 to the high pressure manifold which is connected to the wellhead.
  • clean fluid 95 from tank 20, pipe 71, low pressure pump 44, pipe 73 and valve SV-6 is introduced to the second end side of piston 65 in tubular 60.
  • both pistons 55, 65 have clean fluid 95, 95a on both sides of the pistons.
  • the arrangement of having valves SV-1, SV-4, SV-6 and SV-9 open and the other valves closed continues until, as shown in Fig. 2, a predetermined amount of clean fluid is introduced to the second end side of piston 65.
  • valve SV-6 is closed and valve SV-8 is opened so that harsh fluid may be injected from tank 30, via low pressure pump 46, pipe 83 and valve SV-8 into the second end side of tubular 60b, as shown in Fig. 3.
  • valves SV-1, SV-4, SV-8 and SV-9 open and the other valves closed, harsh fluid 96 continues to be ejected from tubular 50 under high pressure via pipe 85 and valve SV-9 toward the wellbore, while clean fluid 95 continues to be ejected from tubular 60 under low pressure via pipe 77 and valve SV-4 to the storage tank until the pistons 55 and 65 nearly reach the respective first and second ends 50b, 60a of their respective tubulars 50, 60 as seen in Fig. 4 with all harsh fluid having been ejected out of tubular 50.
  • valves SV-1, SV-4 SV-8, and SV-9 are closed, and valves SV-7, SV-3, SV-2 and SV-10 are opened to reverse the directions of the pistons 55, 65, and start the second half of the cycle.
  • clean fluid under high pressure is injected into tubular 60 via valve SV-2 to cause harsh fluid 96 to be ejected from tubular 60 to the high pressure manifold via valve SV-10.
  • harsh fluid 96 from storage tank 30 is injected via valve SV-7 under low pressure into the second end 50b of tubular 50, and clean fluid 95 is ejected from the first end 50a of tubular 50 back to the clean fluid storage tank 20 via valve SV-3.
  • valves SV-1, SV-4, SV-8 and SV-9 would be re-opened and valves SV-2, SV-3, SV-5, SV-6, SV-7 and SV-10 would be closed and a new cycle would start.
  • valves SV-1, SV-4 SV-8, and SV-9 may remain open until the pistons reach the ends of their respective tubulars as seen in Fig. 5 such that the entire contents of the tubulars are discharged.
  • the amount of the clean fluid 95a ejected from the second end 50b of tubular 50 may be sufficient to flush the harsh fluid from the segment of pipe 85 from the second end 50b of tubular 50 and valve SV-9, thereby prolonging the operating life of this valve.
  • valves SV-1, SV-4 SV-8, and SV-9 would be closed, and valves SV2, SV-10, SV-5 and SV-3 would be opened to reverse the directions of the pistons 55, 65, and start the second half of the cycle.
  • clean fluid under high pressure is injected into the first end 60a of tubular 60 in order to cause harsh fluid to be ejected from the second end 60b of tubular 60 via valve SV-10 toward the wellbore.
  • valve SV-5 is closed and valve SV-7 is opened in order to permit harsh fluid 96 to fill tubular 50 "behind" the clean fluid buffer 95a adjacent the piston.
  • this arrangement could continue until pistons 55 and 65 are pushed back to the arrangement of Fig. 2, or to the arrangement of Fig. 1, such that (in either case), a complete cycle would be completed. If the pistons are pushed back to the arrangement of Fig.
  • valves SV-1, SV-4, SV-6 and SV-9 would be re-opened and valves SV-2, SV-3, SV-5, SV-7, SV-8 and SV-10 would be closed and a new cycle would start. If the pistons are pushed back to the arrangement of Fig.
  • valves SV-1, SV-9, SV-8 and SV-4 are re-opened and the remainder of the valves are closed and a new cycle starts.
  • the cycles of the above-described embodiments are repeated between the two tubulars to maintain a constant discharge rate of high pressure harsh fluid.
  • the cycles may alternate between the arrangement shown in Fig. 1 to the arrangement shown in Fig. 4, or the arrangement shown in Fig. 1 to the arrangement shown in Fig. 5, or the arrangement shown in Fig. 2 and the arrangement shown in Fig. 4, or the arrangement shown in Fig. 2 to the
  • the cycles may be changed such that the standard cycle is Fig. 1 to Fig. 4, but occasionally the cycle might extend to the arrangement of Fig. 5.
  • the tubulars are between two and six inches in diameter and between ten and forty feet in length. In other embodiments, the tubulars have smaller or larger diameters and shorter or longer lengths.
  • valves are check valves.
  • the internal diameters of the tubulars and/or pipes 84 and 85 are coated with a hard, abrasion resistant coating to withstand pumping of harsh slurries under high pressures.
  • valves are electrically powered and are under the control of a processor.
  • sensors may be provided to detect the position of one or both pistons 55, 65, and the sensors may be coupled to the processor so that the processor may open and close the valves accordingly.
  • the tubulars are positioned to be horizontal (i.e., perpendicular to gravitational forces).
  • the lifetime of the piston assemblies 55, 65 are increased as a result of the injection of a small amount of clean fluid as a protective (buffer front) layer between the piston assemblies and the harsh fluid.
  • the amount of clean fluid utilized as the protective layer may be predetermined, and in one embodiment is chosen to be in excess of the dispersion length ID of the harsh fluid.
  • the dispersion length may be calculated as follows. [0039] Consider a pipe of diameter d and length / and a flow rate is fixed at q. A fluid of tracer concentration C when introduced into a pipe of length /, undergoes dispersion. A step profile in C is smeared over a length scale ID, which over a sufficiently large / becomes Gaussian. For a sufficiently large Reynolds number, Re, the calculation relies on turbulent flow friction that provides an estimate for velocity profile. For laminar flow, dispersion is induced by shear and is non-Gaussian.
  • Density p, viscosity ⁇ , flow rate q, and diffusion coefficient s are given.
  • the objective is to estimate the dispersion length ID or a function thereof. Results for two different pipe diameters, approximately 10 cm and 7.5 cm corresponding to nominal sizes of 4 inches and 3 inches respectively are provided. The average velocity is
  • the friction velocity may be obtained from /, which in turn may be used to infer the dispersion coefficient D according to
  • the dispersion length ID may be obtained from the dispersion coefficient D according to
  • a buffer length l b may be chosen to be a multiple of the dispersion length
  • the buffer length l b may be chosen according to In other embodiments, the buffer length may be
  • the buffer length may be twice the dispersion length. In another embodiment, the buffer length is approximately (defined herein to be plus or minus 20%) three times the dispersion length.
  • Dispersion is Gaussian for a very long tube, i.e., for those situations where radial diffusion renders the concentration to be a function of axial distance.
  • dispersion coefficient D is given by the Taylor-Aris theory according to
  • the dispersion coefficient D of eq. (6) is the longitudinal dispersion coefficient which indicates how much mixing occurs between two types of fluid parallel to the direction of motion.
  • the characteristic dispersion. length is equal to where the convection time
  • the dispersion length result becomes irrelevant and may be ignored for cases where the radial diffusion length given by (p * convection time) 5 is very small compared to the tubular radius. In most cases this condition is met, and hence the longitudinal dispersion length is limited by the tubular length. In other words, where the radial diffusion length is very small compared to the tubular radius, the dispersion length is taken to be equal to the longitudinal dispersion length which will often be larger than the tubular length (and therefore ineffective for buffering).
  • flow within tubulars that are used to inject harsh fluid under high pressures toward a wellbore is purposely maintained in turbulent flow in order to prevent the harsh fluid from coming into contact with the forward moving faces of the pistons in those tubulars.
  • System 110 is similar to system 10 of Figs. 1-5, and where elements are the same or substantially the same, the same notation number is utilized Thus, system 110 is shown to include two storage tanks 20, 30, two pumps 42, 46, two (complementary) tubulars 50, 60 with respective first ends 50a, 60a and second ends 50b, 60b having respective check valve pistons 155, 165 and stop elements 158, 168, eight solenoid valves SV-1, SV-2, SV-3, SV-4, SV-7, SV-8, SV-9 and SV-10, and a series of pipes 74-78 that contain clean fluid, e.g., water, and a series of pipes 81-85 often containing harsh fluids.
  • clean fluid e.g., water
  • Storage tank 20 is provided for the clean fluid while storage tank 30 is provided for the harsh fluid.
  • Pump 42 is a high pressure pump for the clean fluid
  • pump 46 is a low pressure pumps for the harsh fluid.
  • storage tank is coupled to high pressure pump 42 via pipe 74.
  • the output of high pressure pump 42 is coupled to a first end 50a of the tubular 50 via pipe 75 and valve SV-1 and to the first end 60a of tubular 60 via pipe 76 and valve SV-2.
  • Storage tank 20 is further coupled to the first end 60a of tubular 60 via pipe 77 and valve SV-4 and to the first end 50a of tubular 50 via pipe 78 and valve SV-3.
  • Storage tank 30 is coupled to low pressure pump 46 via pipe 81.
  • Low pressure pump 46 pumps harsh fluid from storage tank 2 to the second end 50b of tubular 50 via pipe 82 and valve SV-7 and to the second end 60b of tubular 60 via pipe 83 and valve SV-8.
  • the second ends of tubulars 50 and 60 are also coupled to a high pressure manifold (not shown) via valves SV-9 and SV-10 respectively.
  • Tubular 50 is provided with a check valve piston 155 and a stop 158, while tubular 60 is provided with a check valve piston 165 and a stop 168.
  • the stops limit the movement of the check valve pistons in the tubulars as further described below, and may be designed in a variety of ways. In non-limiting examples, the stop elements may be inner rings, discrete parts of rings, strainers, or anything that will impede the movement of the piston.
  • the check valve pistons allow for clean fluid to flow through the check valve at the end of the harsh fluid discharge cycle and flush the check valve, tubular, downstream piping and valves with clean fluid as further described below.
  • valves SV- 1 and SV-2 (and SV-9 and SV-10) are opened in order to fill tubulars 50 and 60 with clean fluid 95 (thereby pushing pistons 155 and 165 toward the second ends 50b and 60b of the tubulars 50 and 60). All other valves are in the closed position.
  • the check valve pistons 155 and 165 reach stops 158 and 168 inside the tubulars, the check valves in the pistons open at a cracking pressure to permit the remainder of the tubulars to fill with clean fluid.
  • the clean fluid provided to the right of the stops act as the buffers 95a.
  • the stops may be chosen to be at a location which will provide the desired buffer size.
  • valves SV-2, SV-9. and SV-10 are closed, and valves SV-4 and SV-8 are opened, and pump 46 is started.
  • harsh fluid is directed into end 60b of tubular 60 and pushes piston 165 back toward end 60a of the tubular.
  • piston 165 reaches end 60a of the tubular, the harsh fluid 96 fills the tubular 60 except for a buffer 95a as seen in Fig.6.
  • tubular 50 which was previously filled with clean fluid 95 is now receiving harsh fluid 96 via valve SV-7 and clean fluid 95 is being discharged back to storage tank 20 via valve SV-3.
  • the pressure of the harsh fluid 96 is higher than the pressure of the clean fluid 95 so the check valve stays closed.
  • the check valves in both pistons are designed to open when the pressure on the clean fluid side is higher than the pressure on the harsh fluid side by a preset amount, referred to as the cracking pressure.
  • Fig. 7 shows the same valve arrangement as Fig. 6, with the two pistons 155, 165 having advanced to the middle of the tubulars 50, 60 after a period of time. Piston 155 is moving to the left (toward end 50a of tubular 50) and piston 165 is moving to the right (toward end 60b of tubular 60), and the check valves in both pistons are closed.
  • the piston 165 After some further time, and as seen in Fig. 8, the piston 165 reaches the stop 168 along the inner diameter of the tubular 60 before piston 155 reaches first end 50a of tubular 50 (as it is moving faster in this embodiment). Once piston 165 reaches stop 168, the piston 165 will be unable to move despite the pressure exerted by the high pressure clean fluid 95. Because piston 165 is unable to move, pressure builds on the clean fluid side, and this leads to the opening of the check valve in piston 165 which permits high pressure clean fluid to move past the piston 165 and discharge into pipe 84 and valve SV-10, thereby cleaning that pipe and valve. In addition, the movement of the clean fluid past the piston 165 effectively recharges the buffer 95a; i.e., removing elements of the harsh fluid that may have dispersed into the buffer fluid.
  • valves SV-2, SV-3, SV-7 and SV-10 may be closed and valves SV-1 , SV-9, S V-8, and S V-4 may be opened.
  • the high pressure clean fluid 95 will then start to flow into tubular 50 via SV-1, pushing piston 155 and the clean fluid buffer 95a toward tubular end 50b, thereby pressurizing the harsh fluid 96 which is discharged through SV- 9 toward the high pressure manifold.
  • harsh fluid 96 will be provided to the tubular end 60b, thereby pushing the clean fluid buffer 95a, piston 165, and clean fluid 95 in the tubular 60 toward tubular end 60a.
  • FIG. 10 The system configuration a short time later is shown in Fig. 10 with piston 155 pushing the buffer 95a and the harsh fluid 96 toward tubular end 50b, and piston 165 pushing clean fluid 95 toward tubular end 60a.
  • This configuration is substantially the same as the one shown in Fig. 7, except the tubulars are switched; i.e., tubular 50 is providing the harsh fluid 96 for output to the wellbore, and tubular 60 is being filled with harsh fluid 96 with clean fluid 95 draining back to storage tank 20. This process is continued and the tubular that is providing harsh fluid for the wellbore are switched at regular intervals to provide a steady flow rate of high pressure harsh fluid 96.
  • each of the pistons utilizes a check valve having a low cracking pressure so that the piston will continually discharge clean fluid to the harsh fluid side during the harsh fluid discharge cycle.
  • the flow rate of clean fluid through the check valve will be determined by the machined geometry through the piston and the friction on the piston rings.
  • the check valve, downstream flow geometry on the piston, and the friction drag on the piston are designed so that the volume of clean fluid on the back of the piston grows at the desired rate so that the final volume is enough to "flush" the downstream check valves with the clean fluid.
  • the fluid discharge through to the harsh fluid side is tangential in nature and may cause the piston to rotate in reaction thereto.
  • Piston (assembly) 17S comprises a cylindrical block 1100 having at least one circumferential piston ring 1101 extending around the block, and defining a fluid passageway 1103 which houses a spring loaded check valve 1105. Downstream of the check valve 1103 the fluid passageway 1103 splits into a plurality of streams that flush harsh fluid away from the piston rings 1101.
  • Figs. 12a - 12f a sequence of operation is shown in Figs. 12a - 12f.
  • the start of the cycle is shown in Fig. 12a, with tubular SO completely filled with the harsh fluid 96 and tubular 60 at the end of the discharge cycle, filled with clean fluid 95.
  • tubular 50 is provided with high pressure clean fluid
  • the piston 175a in tubular 50 starts moving to the right such that harsh fluid 96 is discharged from tubular end 50b at high pressure.
  • the size of the clean fluid buffer 95a increases as the piston 175a moves toward tubular end 50b.
  • enough clean fluid has moved past the piston 175a to ensure that when piston 175a does reach tubular end 50b (in Fig. 12e), harsh fluid 96 will have been flushed from the exit pipe and valve (SV-9).
  • tubular 50 ejects harsh fluid 96 to the high pressure manifold
  • tubular 60 is filled up -with the harsh fluid 96 under low pressure, and clean fluid 95 contained in tubular 60 is discharged via tubular end 60a at low pressure back to the storage tank.
  • the process continues as shown in Figs. 12b, 12c, 12d and 12e.
  • the harsh fluid 96 is in contact with piston 175b, albeit not during the high-pressure discharge cycle, and only under low pressure conditions.
  • piston 175b has a check valve 1105
  • the harsh fluid 96 will not move to the clean fluid side of the check valve and tubular.
  • tubular 60 is not under high pressure in this portion of the cycle, the harsh fluid is unlikely to cause damage to the piston.
  • the pistons 175a and 175b push on clean fluid, thereby avoiding damage from the harsh fluid.
  • a high viscosity protective layer between the piston and the harsh fluid will help to extend the operating life of the piston assembly.
  • the low pressure pump 46, and/or storage tank 30 may not be desirable if there is a continuous supply of the harsh fluid at low pressure available from upstream operations.
  • different types of high pressure generation devices may be utilized, including, without limitation, reciprocating pumps, centrifugal pumps, rotary screw compressors, and lobe pumps.
  • the clean fluid may comprise a gas.
  • the embodiments effectively provide pressure exchangers which exchange pressure energy from high pressure clean fluid systems to relatively low pressure harsh fluid systems for use in pressurizing the harsh fluids and directing them to a wellbore as high pressure harsh fluids without the harsh fluid contacting identified portions of the pressure exchangers.
  • processor may include a computer system.
  • the computer system may also include a computer processor (e.g., a microprocessor, microcontroller, digital signal processor, or general purpose computer) for executing any of the methods and processes described above.
  • a computer processor e.g., a microprocessor, microcontroller, digital signal processor, or general purpose computer
  • the computer system may further include a memory such as a semiconductor memory device (e.g., a RAM, ROM, PROM, EEPROM, or Flash-Programmable RAM), a magnetic memory device (e.g., a diskette or fixed disk), an optical memory device (e.g., a GD-ROM), a PC card (e.g., PCMCIA card), or other memory device.
  • a semiconductor memory device e.g., a RAM, ROM, PROM, EEPROM, or Flash-Programmable RAM
  • a magnetic memory device e.g., a diskette or fixed disk
  • an optical memory device e.g., a GD-ROM
  • PC card e.g., PCMCIA card
  • the computer program logic may be embodied in various forms, including a source code form or a computer executable form.
  • Source code may include a series of computer program instructions in a variety of programming languages (e.g., an object code, an assembly language, or a high-level language such as C, C++, or JAVA).
  • Such computer instructions can be stored in a non-transitory computer readable medium (e.g., memory) and executed by the computer processor.
  • the computer instructions may be distributed in any form as a removable storage medium with accompanying printed or electronic documentation (e.g., shrink wrapped software), preloaded with a computer system (e.g., on system ROM or fixed disk), or distributed from a server or electronic bulletin board over a communication system (e.g., the Internet or World Wide Web).
  • a removable storage medium with accompanying printed or electronic documentation (e.g., shrink wrapped software), preloaded with a computer system (e.g., on system ROM or fixed disk), or distributed from a server or electronic bulletin board over a communication system (e.g., the Internet or World Wide Web).
  • a communication system e.g., the Internet or World Wide Web
  • the processor may include discrete electronic components coupled to a printed circuit board, integrated circuitry (e.g., Application Specific Integrated Circuits (ASIC)), and/or programmable logic devices (e.g., a Field Programmable Gate Arrays (FPGA)). Any of the methods and processes described above can be implemented using such logic devices.
  • ASIC Application Specific Integrated Circuits
  • FPGA Field Programmable Gate Arrays

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Mining & Mineral Resources (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Fluid Mechanics (AREA)
  • Environmental & Geological Engineering (AREA)
  • Physics & Mathematics (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Treatment Of Water By Oxidation Or Reduction (AREA)

Abstract

L'invention concerne des procédés et des systèmes se rapportant à un échangeur de pression qui échange l'énergie d'une pression entre un système de fluide propre haute pression et un système de fluide agressif à pression relativement basse, destiné à être utilisé pour mettre sous pression le fluide agressif et pour diriger le fluide vers un puits de forage sous la forme d'un fluide agressif haute pression sans que le fluide agressif ne vienne en contact avec des parties identifiées de l'échangeur de pression.
PCT/US2016/019034 2015-02-23 2016-02-23 Procédés et systèmes de mise sous pression de fluides agressifs WO2016137927A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
US15/552,749 US20180030968A1 (en) 2015-02-23 2016-02-23 Methods and systems for pressurizing harsh fluids
CN201680021707.8A CN107454926B (zh) 2015-02-23 2016-02-23 用于对苛刻流体加压的方法和系统
RU2017131414A RU2673895C1 (ru) 2015-02-23 2016-02-23 Способы и системы для нагнетания агрессивных текучих сред

Applications Claiming Priority (2)

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US201562119392P 2015-02-23 2015-02-23
US62/119,392 2015-02-23

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CN (1) CN107454926B (fr)
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CA3119312A1 (fr) * 2018-11-09 2020-05-14 Flowserve Management Company Dispositifs d'echange de fluide ainsi que commandes, systemes et procedes associes
US12092136B2 (en) 2018-11-09 2024-09-17 Flowserve Pte. Ltd. Fluid exchange devices and related controls, systems, and methods
MX2021005198A (es) * 2018-11-09 2021-07-15 Flowserve Man Co Dispositivos de intercambio de fluidos y sistemas y metodos relacionados.
MX2021005195A (es) * 2018-11-09 2021-07-15 Flowserve Man Co Dispositivos de intercambio de fluidos y controles, sistemas y metodos relacionados.
US11470038B1 (en) 2020-05-19 2022-10-11 Marvell Asia Pte Ltd. Line side multiplexers with protection switching
US11629582B2 (en) * 2020-08-25 2023-04-18 Colina Liquid plunger method and apparatus

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20070196219A1 (en) * 2004-03-26 2007-08-23 Putzmeister Aktiengesellschft Device and method for controlling a two cylinder thick matter pump
US20080193299A1 (en) * 2007-02-12 2008-08-14 Kenneth Doyle Oglesby High pressure slurry plunger pump
US20120063936A1 (en) * 2010-09-10 2012-03-15 Phoinix Global LLC Modular fluid end for a multiplex plunger pump
US20130115115A1 (en) * 2011-11-08 2013-05-09 Soilmec S.P.A. High pressure pumps for injecting cement mixtures
US8708049B2 (en) * 2011-04-29 2014-04-29 Schlumberger Technology Corporation Downhole mixing device for mixing a first fluid with a second fluid

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19503986A1 (de) * 1995-02-07 1996-08-08 Hudelmaier Ulrike Verfahren und Vorrichtung zum Fördern von Beton oder anderen Dickstoffen
JP3432679B2 (ja) * 1996-06-03 2003-08-04 株式会社荏原製作所 容積式真空ポンプ
WO2005067518A2 (fr) * 2004-01-12 2005-07-28 Kenneth Doyle Oglesby Pompe a boue a piston haute pression
CA2476032C (fr) * 2004-08-27 2008-11-04 Westport Research Inc. Commande hydraulique et methode d'exploitation
US7845413B2 (en) * 2006-06-02 2010-12-07 Schlumberger Technology Corporation Method of pumping an oilfield fluid and split stream oilfield pumping systems
DK3052814T3 (da) * 2013-10-03 2020-06-08 Energy Recovery Inc Fraktureringssystem med hydraulisk energioverførselssystem
CN204113634U (zh) * 2014-09-26 2015-01-21 厦门理工学院 一种带浮动连接砼活塞连接装置的混凝土泵送机构
US10161421B2 (en) * 2015-02-03 2018-12-25 Eli Oklejas, Jr. Method and system for injecting a process fluid using a high pressure drive fluid

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20070196219A1 (en) * 2004-03-26 2007-08-23 Putzmeister Aktiengesellschft Device and method for controlling a two cylinder thick matter pump
US20080193299A1 (en) * 2007-02-12 2008-08-14 Kenneth Doyle Oglesby High pressure slurry plunger pump
US20120063936A1 (en) * 2010-09-10 2012-03-15 Phoinix Global LLC Modular fluid end for a multiplex plunger pump
US8708049B2 (en) * 2011-04-29 2014-04-29 Schlumberger Technology Corporation Downhole mixing device for mixing a first fluid with a second fluid
US20130115115A1 (en) * 2011-11-08 2013-05-09 Soilmec S.P.A. High pressure pumps for injecting cement mixtures

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CN107454926A (zh) 2017-12-08
RU2673895C1 (ru) 2018-12-03
AR103757A1 (es) 2017-05-31
CN107454926B (zh) 2019-06-04
US20180030968A1 (en) 2018-02-01

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