BR112020000128B1 - DOUBLE ACTING PRESSURE BOOST LIQUID SPLITTING DEVICE, SYSTEM, FLEET AND USE - Google Patents

Abstract

The invention relates to a double acting pressure increasing liquid partition device (2), a system comprising the double acting pressure increasing liquid partition device (2), a fleet comprising the system and use of the device , system and fleet. The double-acting pressure-increasing liquid partition device (2) for a closed hydraulic circuit volume, the double-acting pressure-increasing liquid partition device (2) being capable of feeding and withdrawing a large quantity of hydraulic fluid under high pressures to and from at least one first pressure transfer device (1') and second pressure transfer device (1''), the pressure transfer devices (1', 1'') pumping fluids with particles with high volumes and pressures above 500 bar, where the double acting pressure increase the liquid partition device (2) is controllable by a variable flow supply through at least one first drive fluid port (24') and a second drive fluid port (24''), wherein the double-acting pressure-increasing liquid partition device (2) comprises: - a hollow cylinder housing (20) with a longitudinal extension, wherein the housing of cylinder (20) comprises at least (...).

Description

[001] The invention relates to a double acting pressure boosting liquid splitting device for a volume of closed hydraulic circuit, a system comprising the double acting pressure boosting liquid splitting device for a volume of closed hydraulic circuit, the double acting pressure boosting liquid splitting device being capable of feeding and withdrawing a large quantity of hydraulic fluid under high pressures to and from at least one first and second pressure transfer devices, the pressure transfer devices pumping fluids with particles in high volumes and pressures above 500 bars.

[002] The invention may form part of a larger pumping system comprising one or more of a pressure transfer device, a double-acting pressure boosting liquid splitting device and a flow regulating assembly (such as a valve manifold).

[003] The invention is suitable for use at high pressures, ranging from above 500 bars, and is especially suitable in hydraulic fracturing of oil/gas wells where it is difficult to pump fluids with particles such as proppants forming part of the fluid. However, the pumping system may also find use in other well applications, such as in drilling operations for pumping drilling fluids and cementing, shut-in and abandonment operations, completion or stimulation operations, acidification or nitrogen circulation.

Fundamentals of the invention

[004] Hydraulic fracturing (also fracturing, fracturing, fracturing, hydro-fracturing or hydrodeposition) is a well stimulation technique in which rock is fractured by a pressurized fluid, in the form of gel, foam, sand or water. Chemicals can be added to water to increase fluid flow or improve specific properties of the water, and such treated water is called slick-water. The process involves high-pressure injection of tracer fluid (liquid containing sand or other proppants and chemicals) into a wellbore to create cracks in deep rock formations through which natural gas, oil and brine will flow more freely. . Typically, mechanical piston pumps are used to pump discharge fluid under high pressures. These mechanical pumps have a very limited operating time due to mechanical wear and tearing on the sliding surfaces inside the pump caused by sand and particles in the pumped medium. Pumps that operate with particle-trapping liquids and/or demanding chemical fluids under high pressure have sealing surfaces that particles and/or abrasive chemical fluids (compounds) damage during operation. When seals are damaged, there can be leaks and other problems that result in the pump reducing its capacity. Furthermore, mechanical pumps operate at high speeds, which creates rapid pressure fluctuations throughout the entire unit (high number of cycles), which over time leads to fatigue breakdowns. Consequently, the operational life cycle of such pumps is very limited and dependent on the type of particles, quantity of particles, chemical composition and chemical concentration, as well as working pressure. In rotary pumps, the rotary seals (shaft), and expensive pump elements such as impellers and turbine wheels, are quickly worn out. In piston pumps, the piston is worn against the cylinder, resulting in leaks, low efficiency and collapse. Another well-known problem with plunger pumps is fatigue cracking of the fluid ends. The main cause of this is the combined stresses of pressure fluctuations and mechanical linear stress on the pistons. They are also limited by a maximum allowable rod load at the power end, making it necessary to match the piston size to the desired rate/pressure distribution.

[005] In general, plunger/plunger pump units are used.

[006] When a plurality of pumps are connected to the same flow line down the well, and are in line simultaneously, there is a risk that they will form interference patterns that coincide with the reference frequency of the flow line down to the well . This leads to flow lines moving around, which can lead to damage to equipment and personnel (called "snaking" because the flow line moves like a snake).

[007] In fracturing operations, when the pumps are turned off and hydraulic pressure is no longer applied to the well, small grains of hydraulic fracturing proppants keep the fractures open. Typically, proppants are made from a solid material, such as sand. The sand can be treated or synthetic sand or naturally occurring materials such as ceramics. In land fracking, typically a fleet called a "frack" comprising a number of trucks is transported and positioned at a location. Each truck is equipped with a pumping unit to pump discharge fluid into the well. Therefore, there are weight and physical limitations on the equipment to be used limited by the total weight capacities of the truck on the road and the physical limitations given by the trucks.

[008] A prior art, not suitable for fracturing, but which discloses a system where clean hydraulic fluid is separated from the liquid to be pumped, includes document EP 2913525 relating to a hydraulically driven diaphragm pumping machine ("pump"), in particular for water and materials that are difficult to pump. The system comprises at least two side-by-side pumping units. Each pumping unit comprises a pump cylinder and a hydraulic cylinder. The pump cylinder (reference signs related to EP 2913525, 1, 2) has a first lower end with a first inlet and outlet for liquid to be pumped and a second upper end with a second inlet and outlet for hydraulic fluid. The pump cylinder (1, 2) contains a bellows (3,4) closed at its lower end and open at its upper end for communication with hydraulic fluid. The outside of the bellows (3,4) defines a space for liquid to be pumped. The bellows (3,4) of the pump cylinder (1, 2) is arranged to be driven by hydraulic fluid supplied at its upper end, in terms of similar expansion and contraction to pump the liquid to be pumped adjacent to the first lower end of the pump cylinder (1, 2). pump cylinder (1, 2). The hydraulic cylinder is placed side by side with the pump cylinder (1, 2). The hydraulic cylinder (figure 10) has a first lower end associated with a hydraulic drive and a second upper end containing hydraulic fluid that communicates with the second upper end of the pump cylinder (1, 2). The hydraulic drive ends at its upper end with a drive piston (19, 20) slidably mounted on the hydraulic cylinder (figure 10). The hydraulic drives of the hydraulic cylinders (9,10) of the two pumping units are connected by a hydromechanical connection (25,27) designed to advance and retract the pistons (19, 20) of each hydraulic cylinder (9, 10).

[009] However, the solution in EP 2913525 is not applicable for hydraulic fracturing at high pressures (i.e. more than 500 bars) because of the cylindrical pump chamber. The cylinder shape of the pump chamber will not be able to withstand the high pressures experienced in combination with a large number of cycles when used in hydraulic fracturing. Furthermore, the bellows are polymer, resulting in the risk of particles being squeezed between the cylindrical wall and the bellows, with the possibility of damage to the bellows. Additionally, there is a hydraulic cylinder connected to each pump cylinder. The hydraulic cylinder is not configured to increase the pressures entering the lower side of the piston (19.20) because the effective area is smaller on the lower side of the piston (19.20) than on the upper side of the piston (19.20). Furthermore, regarding the polymer bellows, the lack of control over the direction of expansion leads to the possibility of the bellows coming into contact with the cylinder wall. This can lead to tearing and proppants being forced into the base material.

[010] Consequently, known systems have disadvantages in providing a double-acting pressure boosting liquid splitting device that can provide sufficient pressure on the high pressure side of the pump (above 500 bars), and which can operate two pump units, without the risk of ballooning of the pump chambers and possibly leaking through the seals in the double-acting pressure boost liquid partition device. Ballooning of the casing, i.e. the drive fluid pump housing, can occur as a result of high pressure differences between the inside of the drive fluid pump and the outside of the drive fluid pump. If the pressure inside the drive fluid pump is, for example, 1000 bars and the pressure outside the drive fluid pump is 1 atmospheric pressure (= 1.01325 bar = 1.01325 x 105 Pascals), the housing of the drive fluid pump may not be able to withstand such pressures and chamber ballooning may occur (i.e., the volume within the drive fluid pump may increase), resulting in potential leaks over the seals inside the drive fluid pump. drive fluid.

[011] Thus, an objective of the present invention is to resolve at least some of the disadvantages in relation to prior art solutions.

[012] More specifically, one of the objectives of the invention is to provide a landing system that can operate at pressures of up to 100 bars and above, without risk of leakage over the seals in the pump.

[013] Hydromechanical connections in general have some disadvantages, including: - cannot synchronize with multiple units, - cannot ramp up/down depending on pressure and flow (does not offer precise control of pump characteristics ), - it cannot be a partial stroke, - it cannot compensate for pressure/flow fluctuations in the flow, - it may never be able to overlap and make a laminar flow, - it generates a pressure drop over the control valve, the which leads to heating of the oil, and loss of efficiency in the range of 5 -10%.

[014] There is a problem with conventional pumps used for fracturing that parts in the system can break after a few hours and must be repaired. Thus, to provide redundancy in the system, fleets comprising a plurality of spare pumps is normal. This triggers the cost in both maintenance and man-hours, as one man can only operate a few trucks.

[015] All hydraulic systems have a degree of internal hydraulic fluid leakage, this will also occur in the closed loop hydraulic system over a number of cycles. This leakage will accumulate over a number of cycles, adding to or retracting from the closed volume, leading to the bellows contracting or stretching too far. Failure to control this will lead to premature failure of the bellows.

[016] Thus, an object of the present invention is to solve at least some of the disadvantages in relation to prior art solutions and more specifically to keep moving parts (pistons, seals) away from the particulate fluid (i.e. pumped medium). and avoid particles that damage moving parts.

[017] It is an object of the present invention to provide smooth and shock-free pumping of large flows at high pressures, reducing wear and tear on all components in the flow loop and at the same time providing a unit capable of seamlessly integrating and adapting to any pressure flow rate demand without the need for mechanical reaccumulation or changes. Furthermore, the ability of the present invention to synchronize with multiple units minimizes the potential snake risk.

[018] More specifically, one of the objectives of the invention is to provide a landing system that can operate at high pressures with high volume flow.

[019] Another objective is to provide a pumping system that has reduced weight, for example, the pumping system must be capable of being arranged and transported in standard trucks or trailers that form part of the so-called fracturing fleets. hydraulic.

[020] Another objective is to provide completely non-operating controlled bellows speed/stroke control to avoid pressure peaks, flow peaks and fluctuations.

[021] Another objective is to create a pump system for all pressure and flow configurations typically used in fracturing or other high pressure pumping industries, without the need for mechanical reconstruction.

[022] Another objective of the invention is to provide an advanced control and synchronization system for multiple units, to eliminate problems with conventional systems.

[023] Another objective is to provide a solution that can be used in new installations and connected to existing installations, such as retrofitting existing systems.

Summary of the invention

[024] The objectives are achieved by the invention as presented in the independent claims, where the detailed embodiments of the invention are defined in the dependent claims.

[025] The present invention provides significant improvements over known solutions, the invention relates to a double-acting pressure boosting liquid splitting device suitable for operating at extreme pressures, that is, pressures above 1,100 bars. The dual-acting pressure booster liquid splitting device can be used as a pressure booster to drive a pressure transfer device that again pressurizes a fluid medium to be pumped. The invention relates to a double acting pressure boosting liquid splitting device for a closed hydraulic circuit volume, the double acting pressure boosting liquid splitting device being capable of feeding and withdrawing a large quantity of hydraulic fluid under high pressures to and from at least a first pressure transfer device and second pressure transfer device, the pressure transfer devices pumping particulate fluids in high volumes and pressures above 500 bars, where the partition device of dual-acting pressure boosting liquid is controllable by a variable flow supply through at least a first drive fluid port and a second drive fluid port, wherein the pressure boost liquid partition device of double acting comprises: - a hollow cylinder housing having a longitudinal extension, wherein the cylinder housing comprises at least a first part and a second part having a first cross-sectional area (al) and a third part having a second area of cross-sectional area (a2) of a different size than the first cross-sectional area (al), - a rod, the rod having a cross-sectional area corresponding to the first cross-sectional area (al), and wherein a first part of the rod and the first part of the cylinder housing define a first piston chamber, and a second part of the rod and the second part of the cylinder housing define a second piston chamber, the rod further comprising a projecting portion having an area of cross-section corresponding to the second cross-sectional area (al), and the protruding portion and the third part of the cylinder housing define a first outer chamber and a second outer chamber, - protruding part defines a first area of the piston, and the rod defining a second piston area different from the first piston area and wherein, the first part of the rod, over at least a part of its length, is formed with a first internal recess extending from a first surface of end of the rod, wherein the first internal recess is in pressure communication with the first piston chamber, and the second part of the rod, over at least a portion of its length, is formed with a second internal recess extending from of a second terminal surface of the rod, wherein the second internal recess is in pressure communication with the second piston chamber.

[026] The dual-action pressure booster liquid partition device can be any device capable of increasing pressure in a fluid, such as pressure intensifier, booster, amplifier, etc.

[027] In contrast to traditional intensifiers or pressure boosters, the dual-acting pressure booster liquid splitting device according to the present invention preferably has the same volume in the first and second plunger chambers as the filling/inlet volume of an internal volume of, for example, a bellows in the pressure transfer device (ratio 1 : 1).

[028] The dual-action pressure boosting liquid splitting device is a device that is capable of separating or dividing two chambers from each other, thereby establishing a boosting effect. The double-acting pressure boosting liquid splitting device may be a double-acting pressure boosting liquid splitting fracturing device.

[029] The wall thicknesses of the hollow cylinder housing and rod are chosen so that the hollow rod expands proportionally with the expansion of the hollow cylinder housing at all pressures while maintaining clearance between the outer surface of the hollow rod and the inner surface of the cylinder housing substantially constant at all pressures. In other words, the balloon of the hollow rod opposes the balloon of the hollow cylinder shell. Specifically, the optional first and second plunger chambers will be subjected to extreme pressures. All transitions are conformal to avoid stress concentrations. The rod is therefore hollow in order to compensate for the ballooning effect of the hollow cylinder housing 20 during a pressure cycle. Preferably, the balloon of the hollow rod is proportionately or marginally smaller than the balloon of the hollow cylinder housing to prevent any extrusion gap between the hollow rod and the hollow cylinder housing from exceeding permissible limits. If this clearance is too large, leakage will occur over the first and second seals, resulting in unequal volumes of hydraulic fluids in the first and second piston chambers. The thickness of the hollow cylinder housing and the walls of the hollow rod, i.e. the walls surrounding the first and second recesses are chosen so that they deform similarly/equally in the radial direction, and the optional first and second seals Proportioned between the outer surface of the hollow rod and the inner surface of the cylinder housing are also protected ensuring a long service life of the first and second seals.

[030] The protruding portion of the rod is the same shape as the surrounding third part of the hollow cylinder housing, for example, if the surrounding third part is cylindrical, the protruding part is also cylindrical, or if the third surrounding part is rectangular or polygonal , the protruding part is rectangular or polygonal.

[031] The rod, including part of the protruding portion, is preferably manufactured in one piece.

[032] It is clear that all hydraulic systems have a degree of internal leakage of hydraulic fluid, however, throughout the description and claims, the term closed-loop hydraulic system has been used for such a "closed" system to distinguish systems that are not defined by a defined volume.

[033] And preferably equal volumes in each of the first and second piston chambers when the volume entering, for example, the bellows in the pressure transfer device.

[034] In one aspect, the first drive fluid port may be disposed in the first outer chamber and the second drive fluid port may be disposed in the second outer chamber, and a first plunger port may be disposed in the first drive chamber. plunger and a second plunger port may be disposed in the second plunger chamber.

[035] In one aspect, during use of the dual-action pressure booster liquid splitting device, the rod is driven back and forth, allowing pressurized liquid to flow into the first drive fluid orifice. and out of the second drive fluid hole, then to be reversed to go in the opposite direction.

[036] In one aspect, the first piston area is larger than the second piston areas in a fixed ratio. However, the relative difference between the first and second piston areas can be even greater depending on the specific design. The fixed ratio is equal to the pressure boosting capacity of the double acting pressure boosting liquid partition device.

[037] In one aspect, the dual-acting pressure boosting liquid splitting device may comprise a dual-acting pressure boosting liquid splitting device position sensor for detecting rod position. The double-acting pressure boost liquid partition device position sensor may possibly be in communication with a control system, such as an oil management system/oil management system valve.

[038] In one aspect, the dual-acting pressure regulation of the liquid partition may comprise a first seal between the first part and the rod and a second seal between the second part and the rod, the first and second seals being configured to be lubricated, ventilated and cooled by a lubrication system.

[039] In one aspect, the first plunger chamber and the second plunger chamber are part of a closed-loop hydraulic system, respectively.

[040] The invention further relates to a system comprising: - double acting pressure boosting liquid splitting device as described above, - hydraulic pump unit pressurizing the double acting pressure boosting liquid splitting device double through a first port and a second port, - at least two pressure transfer devices in fluid communication with the first piston port and the second piston port, respectively, with the first and second pressure transfer devices being configured to be pressurized and discharged by the double acting pressure boost liquid splitting device, and depressurized and charged by the double acting pressure boosting liquid splitting device assisted by a slurry/mud feed pump during loading , - a flow regulator assembly comprising an inlet manifold and an outlet manifold, wherein the flow regulator assembly is configured to distribute fluid between the inlet manifold, the pressure cavities in the pressure transfer devices, and the pressure manifold. exit.

[041] The system may be a fracturing system, such as a system used in fracturing operations.

[042] The optional bellows in the first and second pressure transfer devices can be returned to the first position, that is, the compressed state, by the aid of the supply pressure in the liquid to be pumped from a supply pump. The liquid to be pumped, i.e. the supply pressure of the pumping liquid from the supply pump to be pumped, provides a pressure that helps in compressing the bellows to the first position. In this compression phase, the pressure in the liquid being pumped is equal to the pressure of the hydraulic fluid in the internal volume of the bellows, and retraction will be a result of the double-acting pressure booster liquid splitting device creating a pressure differential across volume at the time of retraction. When the double acting pressure boost liquid splitting device retracts, there will be a differential volume that the volume of fluid pumped, supplied and pressurized by the feed pump (mixer) (i.e. the feed pump is supplying fluid from fracturing into the pressure cavity), will compensate by compression of the bellows. In the extended state, that is, when the bellows begins to extend through the pressurized fluid that fills the internal volume, the pressure in the hydraulic fluid is equal to the pressure in the liquid to be pumped (that is, the supply pressure in the hydraulic manifold). inlet and/or the liquid reservoir to be pumped). When the pressure in the pressure cavity exceeds the supply pressure of a closed first valve, and when the pressure exceeds the pressure in the discharge piping, a second valve will open and fluid will flow into the well. This compression and extension of the bellows will occur sequentially in the pressure transfer device.

[043] The pressure transfer device may comprise a pressure chamber housing and at least one connecting port, wherein at least one connecting port is connectable to a double-acting pressure boosting liquid splitting device through of a fluid communication means, the pressure chamber housing comprises: - a pressure cavity within the pressure chamber housing, and at least one first port for inlet and/or outlet of fluid to the pressure cavity, - a bellows defining an internal volume within the pressure cavity, and wherein the internal volume is in fluid communication with the connecting port, wherein the pressure cavity has a central axis (C) with an axial length (L'; L ") defined by the distance between the connecting hole and the first hole and a variable cross-sectional area over at least a part of the Axial Length (L', L"), and wherein the bellows is configured to move in one direction substantially parallel to the central axis (C, C") over a part of the axial length (L' L") of the pressure cavity.

[044] In one aspect of the system, the dual-acting pressure boosting liquid splitting device may be configured to sequentially pressurize and discharge, and depressurize and charge, at least two pressure transfer devices, such that a device pressure transfer is pressurized and discharged while the other is depressurized and charged, and vice versa. The double acting pressure boost liquid splitting device is controlled by a variable flow provided by the hydraulic pump unit. This flow can be controlled in a way that allows overcoiling of the pressure transfer devices when four or more are working together. This gives the possibility of pulsation damping and continuous flow. This is one of the advantages compared to the common piston pump driven by a crankshaft that has a variable distribution throughout the complete cycle, which provides sinus curve releases.

[045] According to one aspect, the system may comprise four pressure transfer devices and two double-acting pressure boosting liquid splitting devices, each of the double-acting pressure boosting liquid splitting devices being configured to pressurize and discharge, and depressurize and charge, two pressure transfer devices, such that two of the pressure transfer devices are pressurized and discharged, while the other two pressure transfer devices are depressurized and charged, and vice versa. verse.

[046] According to one aspect, the two dual-acting pressure boosting liquid splitting devices can be configured to be operated individually so that they can pressurize and discharge, and depressurize and charge, two of the pressure transfer devices. pressure synchronously or asynchronously. The two dual-acting pressure boosting liquid splitting devices are actuated asynchronously to allow overlap and thereby provide a pulsation of pulsation-free overall characteristics.

[047] According to one aspect of the system, each of the two pressure transfer devices comprises a bellows and a bellows position sensor monitoring position of the bellows, and a control system adapted to receive monitoring data from the sensor. of position of double acting pressure booster liquid partition device and the bellows by comparing the position of the rod and the bellows.

[048] In one aspect of the system, the pressure transfer device may comprise a pressure chamber housing and at least one connecting port, the at least one connecting port being connectable to a boost liquid splitting device. of double-acting pressure through a fluid communication means, the pressure chamber housing comprises: - a pressure cavity within the pressure chamber housing, and at least one first port for fluid inlet and/or outlet to the pressure cavity, - a bellows defining an internal volume within the pressure cavity, and wherein the internal volume is in fluid communication with the connecting port, wherein the pressure cavity has a central axis with an axial length defined by distance between the connecting hole and the first hole and a variable cross-sectional area over at least a portion of the axial length, and wherein the bellows is configured to move in a direction substantially parallel to the central axis over a portion of the axial length of the pressure cavity. The bellows is preferably radially rigid and axially flexible and is arranged to extend and retract over at least a portion of the length of the pressure cavity. Thus, the pressure cavity has a different cross-section, for example, at least two different cross-sections, in its longitudinal direction. Preferably, the transition areas between different cross sections are smooth or continuous (without sharp edges). Such smooth or continuous transition areas prevent sedimentation and allow for higher pressures without weak points in the pressure cavity. That is, the forces applied to the pressure cavity come as a result of internal pressure. The geometry is optimized to make these forces as uniform as possible.

[049] The connecting hole is thus adapted for sucking hydraulic fluid and/or expelling pressurized hydraulic fluid into and out of the pressure cavity.

[050] The first orifice is adapted for inlet/outlet of liquid to be pumped into and discharged out of the pressure cavity.

[051] According to one aspect, the bellows can be connected to an internal surface of the pressure cavity. Preferably, the bellows is connected to an upper part of the pressure cavity with means that provide a fluid-tight connection between the bellows and the inner surface of the pressure cavity. As such, fluids are prevented from flowing from an internal volume of the bellows and into the pressure cavity.

[052] The bellows has a shape adapted to the shape of the pressure cavity such that the bellows, in all its operational positions, is restricted from contacting an internal surface of the pressure chamber housing. This means that the bellows, in all its operating positions, has a maximum extension in the axial and radial direction that is less than the restrictions defined by the inner surface of the pressure chamber housing.

[053] The invention further relates to a fleet comprising at least two trailers, each trailer comprising at least one system as described above.

[054] The invention further relates to the use of a double-action pressure boosting liquid splitting device as described above, a system as described above, or a fleet as described above in extraction or production of hydrocarbons.

[055] The invention further relates to the use of a dual-action pressure boosting liquid splitting device as described above, a system as described above in a fleet as described above in hydraulic fracturing operations.

[056] The invention further relates to the use of a double acting pressure boosting liquid splitting device as described above, the system described above or a fleet as described above in any of the following operations: plugging and abandonment, drilling, completion or stimulation operations, cementing, acidification, nitrogen circulation.

[057] The present invention provides significant improvements over known solutions. The pumping system and its associated components provide the possibility of pumping at pressures of up to 1500 bars and above with high volume flow. For example, the format provides for the possibility of pumping 1 m3 at 1000 bar pressure per minute or 2 m3 at 500 bar per minute and any ratio between rate and pressure. The invention provides flexibility with respect to desired pump rates and pressures, for example reduced flow rates at high pressures and high flow rates at reduced pressures, in all embodiments with a substantially laminar flow.

[058] A pumping system where the system according to the present invention can be used, can comprise one or more of a pressure transfer device, a double acting pressure boosting liquid splitting device and a regulator assembly (such as a valve manifold). A hydraulic pump unit typically pressurizes the double-acting pressure boosting liquid splitting device, wherein the double-acting pressure boosting liquid splitting device pressurizes the pressure transferring device. The optional bellows in the pressure transfer device functions as a "piston" between the hydraulic pressure side, i.e. the double-acting pressure boost liquid splitting device and the hydraulic pump unit on one side, and the medium to be pumped into a well on the other side. The bellows functions as an extension of the piston (rod) in the double-acting pressure boost liquid partition device. The bellows in the pressure transfer device separates clean hydraulic fluid (inside the bellows) from dirty fluid with particles (outside the bellows).

[059] The bellows is typically a fluid-tight barrier that separates the internal volume of the bellows and the volume between the exterior of the bellows and the interior of a pressure cavity in the pressure transfer device. That is, the bellows has a fixed outer diameter but is axially flexible, providing an annular gap (e.g. gap size at least corresponding to the particle diameter of particles in the fracturing fluid) between the inner surface of the pressure chamber housing and the bellows in all bellows positions and at all pressures. The bellows is preferably fixedly connected at the top of the pressure cavity, and the bellows is surrounded by the pressure cavity in all directions, i.e. below, radially and possibly partially on an upper side of the parts that do not form part of the connection hole for the hydraulic fluid entering and leaving the internal volume of the bellows. The total volume of the pressure cavity is constant, while the internal volume of the bellows changes. When the bellows extends and retracts within the pressure cavity, the remaining available volume of the pressure cavity changes. A volume of hydraulic fluid enters the interior of the bellows and displaces the volume of fluid to be pumped from the pressure cavity.

[060] The pumping system can be a positive displacement pump where variations in volume in the pressure transfer device are obtained using a fluid-tight bellows that is radially rigid and axially flexible. This configuration results in a bellows that moves substantially in the axial direction, while movements in the radial direction are prohibited or limited. When the bellows is in a first position, i.e., a compressed state, the volume remaining in the pressure cavity is greater, while when the bellows is in a second position, i.e., an extended state, the volume remaining in the pressure cavity is larger. pressure is lower. The dimension ratio of the inner surface of the pressure cavity and the outer surface of the bellows is designed such that a gap is formed between the inner surface of the pressure cavity and the outer surface of the bellows in all positions of the bellows, thus preventing particles are trapped between the inner surface of the pressure cavity and the bellows. Thus, the fracturing fluids surround the bellows and the gap is formed such that its minimum extent is greater than the largest particle size of the proppants. The radial rigidity of the bellows ensures that the bellows does not come into contact with the inner surface of the pressure chamber housing. The hydraulic fluid entering the internal volume of the bellows through the connection hole pressurizes the barrier, and due to the rigid properties of the bellows and/or the possible internal guide, all movement of the bellows is in the axial direction. The liquid to be pumped, for example discharge fluid, is pressurized by filling the internal volume of the bellows with hydraulic fluid, thereby increasing the displaced volume of the bellows, which results in less volume remaining in the pressure cavity outside the bellows, and an increase in the pressure of the liquid to be pumped. The liquid to be pumped is then passed through the first orifice and further out through a flow regulating assembly such as a valve manifold.

[061] The double-acting pressure boosting liquid splitting device does not have any sliding surfaces in contact with the liquid to be pumped. Thus, the lifespan of the parts is prolonged because there is no vulnerable part in sliding contact with any abrasive liquid to be pumped. Neither the pressure transfer device has any sliding surfaces in contact with the liquid to be pumped. The pressure transfer device is preferably pressure compensated such that the driving hydraulic pressure is the same as the pressure in the liquid being pumped, i.e., the fracturing fluid, and as such the bellows does not have to withstand the differential pressure between the internal hydraulic drive pressure and the pressure in the liquid to be pumped.

[062] The pressure cavity in the pressure transfer device can taper towards the first orifice, thus creating a natural funnel where sediments/proppants/sand can exit together with the fluid. Consequently, the first hole of the pressure chamber housing is preferably formed to prevent the accumulation of sedimentation (proppants/sand, etc.) by tilting the pressure cavity towards the first hole. The first orifice can therefore be arranged in a lower section of the pressure cavity so that sediment can exit through the first orifice by means of gravity.

[063] The pressure cavity may be elongated, egg-shaped, elliptical, circular, spherical, sphere-shaped or oval, or multi-bubbled (e.g., like Michelin) or have two parallel sides and at least one portion of cross-section smaller than the cross-section in the parallel portion.

[064] The bellows in the pressure transfer device may have a smaller radial and axial extent than an inner surface of the pressure chamber housing (i.e., defining the radial and axial extent of the pressure cavity), thereby forming a clearance between an outer circumference of the bellows and an inner circumference, i.e. the inner surface of the pressure chamber housing in all operating positions of the bellows. Thus, at all pressures, fluid is surrounding at least two sides of the bellows during operation of the pressure transfer device.

[065] The bellows can have a cylindrical shape or a concertina shape. The construction of the bellows cylinder provides minimum bellows loads since its entire surface is constantly in a hydraulically balanced state. The bellows may thus comprise a concertina-like side wall providing axial flexibility and a fluid-tight end cover connected to the bellows side wall. The concertina-shaped side wall may thus comprise a plurality of circular folds or convolutions provided in a neighboring relationship.

[066] Neighboring folds or convolutions can, for example, be welded together or connected together using other suitable fastening means, such as glue, mechanical connections. Neighboring folds or convolutions may be formed so that particles in the fracturing fluid are prohibited from being trapped between neighboring folds or convolutions in the bellows during bellows retraction and extraction. This can be achieved by realizing the operating range of the bellows, i.e. the predefined maximum extension and retraction of the bellows, so that the openings between neighboring pleats or between the pleats and the inner surface of the pressure cavity are always larger than the largest expected particle size. As such, the risk of trapped particles is minimized.

[067] The bellows is preferably made of a sufficiently rigid material: metal, composite, hard plastic, ceramic, or combinations thereof, etc., providing a fluid-tight bellows, which is radially rigid and axially flexible. The bellows preferably moves substantially in the axial direction, while movements in the radial direction are prohibited or limited. The bellows material is chosen to withstand large variations in pressure and chemicals in the fluid being pumped, thus minimizing fatigue and the risk of damage. If the bellows is made of metal, it can be used at higher temperatures than bellows that are made of more temperature-sensitive materials (i.e., materials that cannot operate at higher temperatures).

[068] It is clear that other parts that form part of the overall system can also be made from appropriate materials, depending on the demands of specific projects, such as metal (iron, steel, special steel or examples above). However, other materials can also be used, such as composite, hard plastic, ceramic or, alternatively, combinations of metal, composite, hard plastic, ceramic.

[069] The bellows may comprise a guide system coinciding with, or being parallel to, the central axis of the pressure cavity, and in which the bellows expands and retracts axially in a longitudinal direction along the central axis. In one aspect, the guidance system may comprise a guide.

[070] The bellows may comprise a guide system comprising a guide. The guide can be connected to a lower part of the bellows and can be configured to be guided into the pressure chamber housing. The guide in the pressure chamber housing can then form part of the inlet and outlet of hydraulic fluid into and out of the internal volume of the bellows. The guide may be coincident with, or parallel to, a central axis of the pressure cavity, and the bellows may expand and retract axially in a longitudinal direction along the central axis.

[071] The pressure transfer device may further comprise a bellows position sensor monitoring position and/or a temperature sensor that monitors the temperature of a drive fluid in the closed volume of the hydraulic circuit. Additionally, pressure sensors can be used. The bellows position sensor may be a linear position sensor. The bellows position sensor may be disposed in the connection hole and comprises axial passage openings for unrestricted fluid flow.

[072] The bellows position sensor may be a linear sensor, a reading device may be fixedly connected to the bellows position sensor, and a magnet may be fixedly connected to the guide, and wherein the reading device it can be an inductive sensor that can read the position of the magneto, so that the bellows position sensor can monitor the relative position of the magneto inductively, and thus the bellows.

[073] The inductive sensor may be an inductive rod adapted to read the position of a magnet, and thus the bellows.

[074] The bellows position sensor may comprise an inductive rod adapted to read the position of a magnet connected to the guide, so that the bellows position sensor inductively monitors the relative position of the magnet, and thus the bellows.

[075] The system may further comprise a control system for controlling the working range of a pump bellows and rod, and be configured to decide whether the bellows and rod operate within a predetermined position operating range defined by limitations. maximum values such as maximum retraction position and maximum extension position of the bellows, the control system being adapted to compare the position by calculating whether an amount of hydraulic fluid volume is outside the predetermined position operating range or not and/or by monitoring the positions of the bellows and double-acting pressure boosting liquid partition device and comparing with the predetermined position operating range. The system may have the capability to operate an oil management system valve to, based on the working range, drain or refill hydraulic fluid into the closed hydraulic circuit volume to keep the system operating in predetermined positions, and not moving. in failure, thus increasing the useful life of components in the system.

[076] The control system thus compares the signals from the bellows position sensor and the double-acting pressure boosting liquid partition device position sensor on the double-acting pressure boosting liquid partition device to decide whether the system operates within predefined working ranges.

[077] Additionally, the system may use a control system that, based on input from the potential temperature sensor(s), is able to decide when to use the oil management system valve to change (refill, drain) the oil in the closed hydraulic circuit system.

[078] The control system also allows partial stroke when working with large proppants and/or at startup. This is crucial in situations where the unit has had an unplanned shutdown where the pumped liquid is still a slurry, allowing the proppants to fall out of suspension and sediment. Partial pressure is then applied in order to resuspend the proppants into a slurry (suspended).

[079] The predetermined bellows position operating range can be defined by specific physical end positions for the bellows, for both compression and extension of the bellows. Alternatively, rather than physical extreme positions, end positions may be software-operated positions that indicate end positions. A signal can then be transferred to the control system indicating that the bellows has reached the end position(s). The physical or software-operated positions that provide the end positions can be integral parts of the bellows, for example as part of a guide system or a bellows position sensor, or separate from the bellows. The control system can then decide whether the bellows has reached its final position. If the bellows does not reach the end position, the control system may decide that an (expected) signal is not read, and instruct the oil management system valve to drain or refill the hydraulic fluid in the closed volume of hydraulic circuit.

[080] The volume flowing into and out of the internal volume of the bellows is monitored using the bellows position sensor which provides high accuracy and controlled acceleration/deceleration of the bellows at the pivot point of the splitting device. double acting pressure boosting liquid, which again results in reduced and smooth seating of the valves, i.e., downward sloping movement of the valves in the flow regulation system. The slow, controlled movement of the valves prevents or minimizes the risk of damaging the valve seats in the flow regulation system. Thus, to achieve this, the system is capable of monitoring the position of the double acting pressure boosting liquid partition device using the double acting pressure boosting liquid partition device position sensor, and when Approaching the end position the unit discharge speed is decreased to dampen/dampen the speed of the valve element before entering the valve seat.

[081] The double acting pressure boosting liquid partitioning device is preferably double acting wherein a primary side, defined by a first piston area, of the double acting pressure boosting liquid dividing device operates with a difference of pressure of 350-400 bars, and on the secondary side, defined by a second piston area, may have a multiple pressure, for example 1050 bars or higher, which will be similar to the pressure that the pressure transfer device, i.e. , the bellows and pressure cavity can operate under.

[082] The pressure transfer device can be operated by the hydraulic pump unit, for example, a central variable pump that controls the double-acting pressure boost liquid partition device. The hydraulic pump unit can have two flow directions and an adjustable displacement volume. The hydraulic pumping unit may be driven for example by any engine operable to operate such hydraulic pump units, such as diesel engines or other known engines/engines. However, it is clear that the described hydraulic pump unit can be exchanged for a variety of hydraulic pumps controlled by a proportional control valve system for pressurizing the double-acting pressure booster liquid splitting device and pressure cavity.

[083] The pressure transfer device is preferably pressure compensated, meaning that the bellows is hydraulically operated by guiding a quantity of oil or other hydraulic liquid into and out of the internal volume of the bellows by moving the bellows between a first position , that is, compressed state, and a second position, that is, extended state. In operation, there will be the same pressure on the hydraulic fluids in the internal volume of the bellows as on the fracturing fluid (i.e., medium to be pumped) in the pressure cavity outside the bellows. The liquid or medium to be pumped, for example fracturing fluid, being disposed below the bellows and in the space formed between the exterior of the bellows and the inner surface of the pressure chamber housing.

[084] It is also possible to provide a trailer, container or slider, comprising the double-acting pressure boosting liquid splitting device as defined above and/or the system defined above used in hydraulic fracturing together with a motor and necessary trim.

[085] Throughout the description and claims, it is intended that the liquid is pumped. The term should be understood as the liquid in the pressure cavity outside the bellows, for example, hydraulic discharge fluid, fracturing, fracturing, hydrofracture or hydrofuge fluid, or mud, stimulation fluid, acid, cement, etc.

[086] Intensifiers are available on the market today, but these intensifiers are based on the difference in area in combination with valves, that is, an auxiliary pressure pump without volume control. Such intensifiers utilize a plurality of smaller strokes to achieve the desired volume, which results in pressure loss and heat generation, which again reduces the life cycle of the pump. Furthermore, it is not possible to control such known pumps using hydraulic pumps and would not be able to contribute to the depressurization and loading of the bellows.

[087] These and other features of the invention will become clear from the following description of a preferred embodiment, given as a non-restrictive example, with reference to the attached drawings, in which:

Brief description of the drawings

[088] Figure 1 shows an operational configuration of the system comprising a double-acting pressure boosting liquid splitting device, in accordance with the present invention;

[089] Figure 2 is an enlarged view of the double-acting pressure boosting liquid partition device according to the invention;

Detailed description of a preferred embodiment

[090] Figure 1 shows an operational configuration of the system comprising a double-acting pressure boosting liquid splitting device in accordance with the present invention.

[091] Fig. 2 is an enlarged view of the double-acting pressure boost liquid partition device.

[092] This is a well stimulation pressure transfer device specifically designed for very high pressure (500 bars and above) at high rates (e.g., 1000 liters/minute or more for the specific system shown in Figure 1 ) pumping fluids, such as slurries, containing high amounts of abrasive particles. Two identical setups are shown in Figure 1, having a common double-acting pressure boosting liquid partition device 2, where the elements of the assembly on the left side are denoted with a single apostrophe (') and the elements in the identical configuration on the right side are denoted with a double apostrophe (").

[093] Details of the double acting pressure boosting liquid partition device 2 according to the invention are shown in Figure 2. Shown is a pressure transfer device 1', 1'' for pumping fluid at pressures above 500 bars, the pressure transfer device 1', 1'' comprising a pressure chamber housing and a connection port 3', 3'', the connection port 3', 3'' being connectable to a pressure transfer device double acting pressure booster liquid partition 2 through fluid communication means in the form of first valve port 26', 26'' and second valve port 27', 27'' and possibly through a management system valve of oil 16', 16''. The pressure chamber housing comprises a pressure cavity 4', 4'' and a first port 5', 5'' connecting the pressure cavity 4', 4'' to a well via a flow management system 13 The first port 5', 5'' acting as inlet and/or outlet of fluid or liquid to be pumped. There is further disclosed a bellows 6', 6'' disposed within the pressure cavity 4', 4'' and in which an internal volume 7', 7'' of the bellows 6', 6'' is in fluid communication with the door. connection cavity 3', 3'' and the internal volume 7', 7'' are prevented from communicating with the pressure cavity 4', 4''. The length of the pressure cavity L', L'', extending in a longitudinal direction between the connecting port 3', 3'' and the first port 5', 5'', has a variable cross-sectional area. The bellows 6', 6'' are configured to move in a direction substantially in the longitudinal direction, which in the drawing is coinciding with the central axis C', C'' of the pressure cavity 1', 1''.

[094] The pressure transfer device 1', 1'' comprises a bellows, exemplified as a hydraulically driven fluid-tight bellows 6', 6'' comprising an internal guide 9', 9'' and a position sensor. bellows 12', 12'' with an inductive rod 43, 43'' adapted to read a magnet 10', 10''. The magnet 10', 10'' can be fixedly connected to the guide 9', 9''. The guide 9', 9'' is itself guided in the pressure chamber housing, for example along the longitudinal extent of the connection port 3', 3''. In the disclosed example, the guide 9', 9'' is connected to the lower end of the bellows 6', 6'' at one end and is guided into the pressure chamber housing at the upper end thereof. The guide 9', 9' 'and therefore the magnet 10', 10'', follows the movement of the bellows 6', 6''. The bellows position sensor 12', 12'', for example the measuring rod 43', 43'' may comprise means for detecting and determining the position of the magnet 10', 10'' (and therefore the guide 9 ', 9'' and bellows 6', 6''), for example by inductive detection of the magnet position. Although the description describes that the magnet 10', 10'' is connected to the guide 9', 9'' which moves relative to the fixed measuring rod 43', 43', it is possible to arrange the magnet 10', 10'' stationary and for example the 9', 9'' inductive guide to monitor the position. Furthermore, it is possible to use sensors other than the linear position sensor described above, as long as they are capable of monitoring the exact position of the bellows 6', 6''.

[095] The bellows 6', 6'' are placed in a pressure cavity 4', 4'' with a defined clearance to the inner surface of the pressure chamber housing. The drive fluid is directed into and out of an internal volume 7', 7'' of the bellows 6', 6'' through a connecting port 3', 3'' at the top of the pressure cavity 4' , 4'' (i.e. the top of the pressure chamber compartment). The bellows 6', 6'' are fixedly connected at the top of the pressure cavity 4', 4'' to the inner surface of the pressure chamber housing by means known to the skilled artisan. The connecting port 3', 3'' is in communication with a double acting pressure increasing liquid partition device 2 and possibly an oil management system valve 16', 16'.

[096] The pressure transfer device 1', 1'' may further comprise an air vent (not shown) to vent air from the fluid to be pumped. Air ventilation may be any ventilation operable to extract or vent excess air from a closed system, such as any suitable valves (choke) or similar.

[097] The pumped medium, for example. fracturing fluid with particles, enters and leaves the pressure cavity 4', 4'' through a first port 5', 5'' at the bottom of the pressure cavity 4', 4'' (i.e., fracture chamber compartment). pressure). The first port 5', 5'' is in communication with a flow regulating device 13, such as a valve manifold. The flow regulating device 13 is explained in more detail below.

[098] Driven by the double-acting pressure boosting liquid partition device 2, the pressure cavity 4', 4'', in combination with the bellows 6', 6'', pumps the fluid by retracting and expanding the bellows 6 ', 6'' between your predefined minimum and maximum limitation. Keeping the bellows within this predefined minimum and maximum limitation extends the life of the bellows. To ensure that the bellows 6', 6'' operates within its preset limitation, this movement is monitored by the bellows 12', 12'' position sensor. Dynamically moving the bellows outside of these predefined minimum and maximum limitations can drastically reduce the life of the bellows. Without this control, the bellows 6', 6'' over time, as a result of internal leakage, particularly in the double acting pressure booster liquid partition device 2, will be overloaded by overextension (eventually fall out with the cavity of pressure 4', 4'' or super compress (retracts), causing particles in the fluid to deform or puncture the bellows 6', 6'' or generate delta pressure). A 9', 9'' central guide system, exemplified as 9', 9'' guide, ensures that the 6', 6'' bellows retract and expand in a linear manner, ensuring that the 6', 6'' bellows ' do not hit the side walls of the pressure cavity 4', 4'' and at the same time ensure accurate positioning readings of the bellows position sensor 12', 12''. Therefore, the 4', 4'' pressure cavity is specifically designed to withstand high pressures and cyclic loads while preventing sedimentation build-up. The defined distance between the external part of the bellows 6', 6'' and the internal dimension of the pressure chamber housing ensures the internal pressure balance of the bellows pressure 6', 6'' and the average pressure of the pump in the pressure cavity. pressure 4', 4''.

[099] This pressure cavity is designed to carry the cyclic loads to which this system will be subjected and to house the bellows and the bellows positioning system. The connecting port 3', 3'' has a cylindrical shape machined and honed through the base material of the pressure cavity 4', 4'' “body” and serves as part of the guide system below 9', 9'' a cylinder and piston configuration. The 4', 4'' pressure cavity is ideally shaped to avoid stress concentrations. The internal 9', 9'' bellows guide system guarantees linear movement of the 6', 6'' bellows without the need for an external guide.

[0100] The first hole 5', 5" from the bottom in the pressure cavity 4', 4", is shaped to prevent sedimentation accumulation by tilting or tapering the pressure cavity 4', 4" towards the first hole 5' , 5". Consequently, the accumulation of sedimentation is avoided because the sediments or particles in the liquid to be pumped naturally flow, i.e. by the aid of gravity, out of the pressure cavity 4', 4" which exits through the first orifice 5', 5 ". Without this inclined or tapered shape, sedimentation buildup may lead to problems during start-up of the pressure transfer device and/or sediment may accumulate and eventually surround lower portions of the outside of the bellows 6', 6".

[0101] The double-acting pressure boosting liquid partition device 2 comprises a hollow cylinder housing 20 having a longitudinal extension, wherein the cylinder housing comprises a first and a second part having a first longitudinal cross-sectional area al and a third part having a second cross-sectional area a2 of different size from the first and second parts. The double-acting pressure boosting liquid partition device 2 comprises a rod 19 movably disposed as a piston within the cylinder housing 20. The rod 19 has a cross-sectional area corresponding to the first longitudinal cross-sectional area al and defines a second piston area 31', 31", and wherein the rod 19, when disposed within the hollow cylinder housing 20, defines a second piston area 3, the first piston chamber 17' and a second piston chamber 17'. piston 17" in the first and second part of rod 19 further comprises a protruding portion 30 having a cross-sectional area corresponding to the second cross-sectional area a2 and the protruding portion defining a first piston area 30', 30" and a first chamber external 44' and a second external chamber 44" in the third part. A portion of the rod defining the first and second piston chambers 17', 17", over at least a portion of its length, is formed with a first recess 40' in pressure communication with the first piston chamber 17' and a second recess 40" in pressure communication with the second piston chamber 17".

[0102] The first piston chamber 17' comprises a first piston port 18' which is in communication with the internal volume 7' of the bellows 6', alternatively through the first valve of the oil management system 16'. Similarly, the second piston chamber 17" comprises a second piston port 18" which is in communication with the internal volume 7" of the bellows 6", alternatively through the second oil management system valve 16". The volumes within the first and second plunger chambers 17', 17" are varied with the rod 19 being extracted and retracted into/out of the respective first and second plunger chambers 17', 17". The rod 19 may comprise a position sensor. double acting pressure booster liquid division 21. First and second seals 22', 22" may be disposed between the protruding portion 30 of the rod and the first plunger chamber 17' and the second plunger chamber 17", respectively. Said first and second seals 22', 22" may be ventilated and cooled by a separate or common lubrication system 23', 23".

[0103] Rod 19 is driven back and forth, allowing a pressurized fluid, such as oil or other suitable hydraulic fluid, to flow into the first inlet/outlet port 24' and out of the second inlet/outlet port 24' 24", then to be reversed to go in the opposite direction. First and second inlet outlet ports 24', 24" are in communication with a hydraulic pump unit 11.

[0104] The first and second oil management system valves 16', 16" are positioned between the bellows 6', 6" and the double-acting pressure boost liquid splitting device 2 and are exemplified as two valves three-way valves that may comprise a first and second actuators 25', 25" operating the first and second three-way valves, respectively. The setups of the first and second valves of the oil management system 16', 16" and their connection to the different pressure transfer devices 1" are identical. Therefore, in the following, the system on the left side, that is, the system in communication with the first piston orifice 18', will be described in greater detail. The pressure transfer system valve oil management 16', in the drawings exemplified as a three-way valve, comprises three ports including a first valve port 26' in communication with the first plunger port 18', a second valve port 27' in communication with the pressure transfer device connection 3' and a third valve orifice 28' in communication with an oil reservoir 29'. Similarly, with reference to the pressure transfer device 1" on the right side, the oil management system valve 16" in communication with the second plunger port 18" comprises three ports including the first valve port 26" in communication with the second plunger port 18", a second valve port 27" in communication with the connecting port 3" of the pressure transfer device 1", and a third valve port 28" in communication with an oil reservoir 29" .

[0105] The hydraulic pump unit 1 may comprise central axial piston pumps that are controlled by position data from both the bellows position sensors 12', 12" and the liquid partition device position sensor double-acting pressure booster 21 in the double-acting pressure booster liquid partition device 2 and possibly in accordance with input data from the Human Machine Interface (HMI) and/or the control system. Hydraulic pumping 1 can be driven by an M motor just like any standard motor used in specific technical fields.

[0106] The flow regulating assembly 13, for example, a valve manifold, may be a flow regulating assembly common to the identical systems on the left and right sides of the Figure. With respect to the system on the left side, the flow regulator assembly 13 may comprise a pump orifice 36' in communication with the first orifice 5' of the pressure transfer device, a supply orifice 35' in communication with the liquid to be pumped through an inlet pipe 14 in the flow regulator assembly 13 and a discharge port 37' in communication with the discharge manifold 15 in the flow regulator assembly 13. To be able to switch and operate between the different inlets and outlets, The flow regulator assembly may comprise a supply valve 38' comprising a check valve that allows the supply of pump fluid when the pressure in the inlet piping 14 is greater than the pressure in the pressure cavity 4' and less than the pressure in the discharge valve 39'. The inlet manifold 14 is in communication with a feed pump and blender. The mixer mixes the liquid to be pumped, and the feed pump pressurizes the inlet piping 14 and distributes the mixed fluid to the pressure transfer devices 1" (pressure cavities 4', 4"). The mixer typically mixes the liquid to be pumped with particles such as sand and proppants. Such a feed pump and blender are known to those skilled in the art and will not be described in greater detail here.

[0107] Similarly, for the system on the right side of Figure, the flow regulator assembly 13 may comprise a pump port 36" in communication with the first port 5" of the pressure transfer device 1", a supply port 35 " in communication with the liquid to be pumped through an inlet manifold 14, and a discharge port 37" in communication with the discharge manifold 15. Furthermore, to be able to switch and operate between the different inputs and outputs, The flow regulator assembly may comprise a supply valve 38" which comprises a check valve that allows the supply of pump fluid when the pressure in the inlet piping 14 is greater than the pressure in the pressure cavity 4" and a pressure relief valve. discharge 39" allowing fluid to be discharged into the discharge piping 15 when the pressure in the pressure cavity 4" is greater than the pressure in the discharge piping 15 to pump fluids at high pressures and flow rates, e.g., into of a well.

[0108] The flow regulator assembly 13 distributes the pumped liquid between the inlet piping 14, the pressure cavity 4', 4" and the outlet piping 15 by using two check valves, one for the inlet and one for the outlet, and the charge/discharge port positioned between them. The supply valve 38', 38" positioned between the supply port 35', 35" and the pump port 36', 36' allowing the fluid to charge the pressure cavity 4', 4" when the bellows 6', 6" is retracting, that is, the liquid to be pumped provides pressure from below, assisting in the retraction/compression of the bellows 6', 6". The liquid boost pressure for the pressure transfer device in the inlet manifold 14 is typically in the range of 3 to 10 bars refilling the pressure cavity 4', 4" and preparing for the next dosing of a high pressure medium to be pumped into the well. When the bellows 6', 6" begins to extend (i.e., pressurized fluid is filling the internal volume 7', 7" of the bellows 6', 6"). The supply valve 38', 38" will close when the pressure exceeds the supply pressure in the inlet piping 14 and thus force the discharge valve 39', 39" to open and thus discharge the contents into the pressure cavity 4', 4" through the discharge port 37', 37" and in relation to the discharge pipe 15. This will occur sequentially in the configuration on the left side of the Figure and on the right side of the Figure, respectively.

[0109] Hydraulic pump unit 1 uses central axial piston pumps configured in an industrially defined closed hydraulic circuit volume, also called swash plate pumps. Wash plate pumps have a set of rotating cylinders containing pistons. The pistons are connected to the swash plate via a ball joint and are pushed against the stationary swash plate, which sits at an angle to the cylinder. The pistons draw in fluid during half a revolution and push fluid out during the other half. The greater the slope, the more the pump pistons move and the more fluids are transferred. These pumps have a variable displacement and can switch between the first inlet/outlet port 24' and the second inlet/outlet port 24' thereby directly controlling the double acting pressure boost liquid splitting device(s) 2

[0110] The oil management system valve 16', 16" is exemplified as a three-way valve. However, other setups can be used, such as an arrangement of two or more valves. The oil management system valve oil is controlled by a control system that can determine whether the correct volume of hydraulic fluid is circulated between the internal volume 7', 7" of the bellows 6', 6" and the first and second piston chambers 17', 17" by the use of position sensors in the bellows and double-acting pressure booster liquid partition device. At the same time, it allows the system to replace the oil in this closed hydraulic circuit volume if temperatures in the oil reach operational limits. This is done by isolating the second valve port 27', 27" from the double-acting pressure boost liquid dividing device and opening communication between the first valve port 26', 26" and the third valve port 28', 28", thereby allowing the rod 19 in the double-acting pressure boosting liquid partition device 2 to position itself in accordance with the bellows 6' position 6". The control system that controls the oil management system valve 16', 16" monitors the position of the bellows 6', 6" in coaxial relationship with the position of the plunger 19 and adds or withdraws oil from the system when the system reaches a maximum deviation limit. This will preferably do this automatically, stopping the bellows 6', 6" in a certain position and leaving the plunger 19 reset to a “bellows position”. A bellows position of the plunger 19 is typically corresponding to a position where the volumes of the first piston chamber 17' and the second piston chamber 17" are the same, which in most situations will be a position in which the bellows 6', 6" is in an intermediate position. Thus, the piston 19 is positioned , preferably, in relation to the actual position of the bellows 6', 6".

[0111] The double-acting pressure boosting liquid partition device 2 is, for example controllable by a variable flow supply, for example, from the hydraulic pump unit 1, through the first inlet/outlet orifice 24' and of the second inlet/outlet port 24". The protruding portion 30 comprising a first end (i.e., through the first piston area 30') in fluid communication with the first inlet/outlet port 24' and a second end (i.e. is, through the first piston area 30") in fluid communication with the second inlet/outlet port 24". Rod 19 further defines a second piston area 31', 31" smaller than the first piston area 30' , 30". Rod 19 separates the first and second piston chambers 17', 17" and is operated to vary the volumes of the first and second piston chambers 17', 17" by extracting and retracting the rod 19 into/out of the first and second piston chambers 17', 17", respectively. The rod 19 is partially hollow and comprises a first recess 40' and a second recess 40". The first and second recesses 40', 40" are separate from each other. Thus, fluid is allowed to flow between the first and second recesses 40', 40". The first recess 40' is in fluid communication with the first plunger chamber 17' and the second recess 40" is in fluid communication with the second piston chamber 17'.

[0112] The function of the double acting pressure booster liquid splitting device 2 is to ensure that a fixed volume of hydraulic fluid, e.g. oil, is loading/unloading the bellows 6', 6". At the same time, functions as a pressure amplifier (booster or intensifier). In the illustrated double-acting pressure booster liquid partition device 2, pressure is increased by having a first piston area 30', 30" larger than the second piston area. piston 31' in the first piston chamber 17' and second piston area 31" in the second piston chamber 17", respectively. There is a fixed relationship between the first piston area 30', 30" and the second piston area 31', 31", depending on the difference in the first and second piston areas. Thus, a fixed pressure in the first or second outer chamber 44', 44" gives a fixed pressure amplified by the pressure difference of the first and second piston areas. However, the inlet pressure can be varied to obtain a different pressure, but the ratio is fixed.Pressure amplification is vital to allow pumping of fluids well through the industrial hydraulic pump units 11 maximum normal pressure range that is driving the unit and is varied to improve the appropriate industry's need for pressures.

[0113] The dual-acting pressure boost liquid partition device 2 may comprise a dual-acting pressure boost liquid partition device position sensor 21 that continuously communicates with the global control system that can operate the oil management system valve 16', 16" for replenishing or draining hydraulic fluid from the closed hydraulic circuit volume based on input from the double acting pressure boost liquid splitting device position sensor 21 on the oil management system valve 16', 16" double acting pressure boost liquid partition 2 and bellows position sensor 12', 12". In the Figures, the double-acting pressure boost liquid partition device position sensor 21 is disposed between the rod 19 and the inner walls of the first or second plunger chamber 17', 17", so that the pressure sensor position of double-acting pressure boosting liquid partition device 21 is capable of continuously monitoring the position of the rod 19 and transmitting signals to a control system by comparing the position of the bellows 6', 6" and the piston or rod 19 in the liquid partition device 2. However, it is possible to arrange the double acting pressure boost liquid partition device position sensor 21 in other locations, including outside the double acting pressure boost liquid partition device 2 , as long as it can monitor the position of the rod 19. As such, any leakage or overfilling of hydraulic fluid in any of the first or second piston chambers 17', 17" can be detected and corrected (for example, when using the oil management system 16', 16" to reposition the rod offset position to zero according to the bellows position as described above).

[0114] Specifically, the first and second piston chambers 17', 17' will be subjected to extreme pressures. All transitions are conformal to avoid stress concentrations. The rod 19 in the double-acting pressure boosting liquid splitting device is preferably a hollow rod in order to compensate for the ballooning effect of the hollow cylinder housing 20 during a pressure cycle. Preferably, the hollow rod balloon 19 is proportionately or marginally smaller than the casing balloon to prevent any extrusion gap between the hollow rod and the housing from exceeding permissible limits. If this gap is too large, leakage will occur over the first and second seals 22', 22", resulting in unequal volumes of hydraulic fluids in the first and second piston chambers 17', 17". The thickness of the casing and the walls of the hollow rod, that is, the walls surrounding the first and second recesses 40', 40" are chosen so that they deform similarly in the radial direction, and the first and second seals 22' , 22" are also protected ensuring a long service life of the first and second seals 22', 22".

[0115] The control system has three main functions. The first main function of the control system is controlling the output characteristics of the pressure transfer device 1', 1": the pressure transfer device 1', 1" is capable of providing flow based on a number of parameters such as : flow, pressure, power or combinations of these. Furthermore, if two double-acting pressure boosting liquid splitting devices 2 are used, the pressure transferring device 1', 1" can deliver a pulsation-free flow up to 50% of the maximum theoretical rate, overlapping the two dual-acting pressure booster liquid splitting devices 2 in a manner that a reduction (tilt to double speed) is achieved when the other is reaching its rotating position. Thus, flow rates reduced to high pressures and high flow rates at reduced pressures, in all embodiments with a substantially laminar flow. This is achieved by having excess capacity on the hydraulic pump unit 1. As the rate increases, there will gradually be less space for the overlap and thereby an increasing amount of pulsations. The variable displacement hydraulic pump unit 1 in combination with pressure sensors and bellows position sensor 12', 12" and boost liquid partition device position sensor 21 double-action pressure pump is key to the flexibility the system offers. The control system, which can be computer-based, also allows for the possibility of multiple parallel pumping systems that act as one by linking them together with a fieldbus. This can be done by arranging the pumping systems in parallel and using the control system to force or operate the individual pumping systems asynchronously. This minimizes the risk of “snaking” due to interference.

[0116] The second main function of the control system is to provide complete control of the movement of the bellows 6', 6" through the cycles relative to the double acting pressure boosting liquid partition device 2. This is of relevance in closing/seating system of valves in flow regulator assembly 13 (e.g. supply port 35', 35", pump port 36', 36", discharge port 37', 37", supply valve 38', 38 ", discharge valve 39', 39") because there is a combination of factors, which need to work in synchrony for this system to function with these extreme pressures and distribution rates. As for a spring, it is important that the 6', 6" bellows operates within its design parameters, i.e., not stretching or over compressing, in order to have a long service life.

[0117] The third main function of the control system is the oil management system valve 16', 16" of the control system which actuates when the control system encounters a difference between the positions of the boost liquid splitting device pressure gauge 2 and bellows 6', 6" or that the temperature is outside predefined limits. The double acting pressure boosting liquid partition device 2 has generally the same strengths and failures as a hydraulic cylinder, is robust and accurate, but has a degree of internal leakage over the first and second seals 22', 22" which over time will accumulate as either a factor of addition or detraction in the closed hydraulic circuit volume between the first and second piston chambers 17', 17" and the internal volume 7', 7" of the bellows 6', 6". To solve these problems, both the bellows 6', 6" and the double-acting pressure boost liquid partition device 2 are equipped with position sensors 12', 12", 21 which continuously monitor the position of these units to ensure that they are synchronized according to the software-programmed philosophy. Over time, the internal leakage of the system will increase, and when the position deviation between the bellows 6', 6" and the double-acting pressure boosting liquid partition device 2 reaches the maximum allowable limit, the first and/or second valves of the oil management system 16', 16" will add or retract the volume necessary to re-synchronize the system (and preferably automatically adjust relative to a known position of the bellows 6', 6") In addition, there may be a problem that the liquid in the closed hydraulic circuit volume between the pressure transfer device 1', 1" and the double-acting pressure boosting liquid partition device 2 generates heat through friction by return flow and backwards. On top of that the first and second seals 22', 22" in the double acting pressure boosting liquid partition device 2 will also produce heat that will dissipate into the liquid (e.g. oil) in the closed hydraulic circuit volume. This problem can be addressed by using the same system to compensate for internal leakage. The closed-loop hydraulic volume can be replaced by the oil management system valve 16', 16". The control system detects a leak in the hydraulic circuit system and thus operates the first and/or second oil management system valve 16', 16" to allow a replacement of the closed hydraulic circuit volume isolating the bellows 6', 6 " in a compressed, retracted, position and allowing the double-acting pressure boost liquid splitting device 2 to discharge its volume into the reservoir (external) and refilling the same with cold oil from the cooling system. For the valves in the flow regulating system 13 (e.g., the supply port 35', 35", the pump port 36', 36", the discharge port 37', 37", the supply valve 38', 38", discharge valve 39', 39") to have a long service life. It is desirable that the seating of valves or holes 35', 35", 36', 36", 37', 37", 38', 38" is soft or soft, that is, the valve elements are not ash in their desired valve seats. To achieve this, the system monitors the position of the double-acting pressure boost liquid partition device 2 ( i.e., the piston or rod 19 in the double-acting pressure boosting liquid partition device), and when approaching the end position, the discharge speed of the hydraulic pump unit 1 is tilted downward to dampen the valve before seating to prevent forging of the check valve seat.

[0118] For purposes of explanation, systems and configurations have been established in order to provide a complete understanding of the system and its workings. However, this description is not intended to be interpreted in a limiting sense. Various modifications and variations of the illustrative embodiments, as well as other embodiments of the system, which are apparent to persons skilled in the art to which the claimed subject matter belongs, are considered to be within the scope of the present invention. Table 1: Reference List:

Claims (13)

1. Double-acting pressure-increasing liquid partition device (2) for a closed hydraulic circuit volume below under high pressures ranging above 500 bar, the double-acting pressure-increasing liquid partition device (2) being capable of feeding and withdrawing a large quantity of hydraulic fluid under high pressures to and from at least a first pressure transfer device (1') and a second pressure transfer device (1''), wherein the liquid partition device double acting pressure booster (2) is controllable by a variable flow supply through at least a first drive fluid port (24') and a second drive fluid port (24''), wherein the double acting pressure increasing liquid partition device (2) is characterized by comprising: - a hollow cylinder housing (20) with a longitudinal extension, wherein the cylinder housing (20) comprises at least a first part and a second part with a first cross-sectional area (a1) and a third part with a second cross-sectional area (a2) of different size from the first cross-sectional area (a1), - a rod (19), the rod (19) having a cross-sectional area corresponding to the first cross-sectional area (a1), and wherein a first rod part and the first cylinder housing part define a first piston chamber (17') and a second rod part and the second part of the cylinder housing define a second piston chamber (17''), wherein a first piston port (18') is disposed in the first piston chamber (17') and a second piston port (18') ') is disposed in the second chamber of the piston (17''), the rod (19) further comprises a protruding portion (30) with a cross-sectional area corresponding to the second cross-sectional area (a2), and the protruding portion and the third part of the cylinder housing (20) define a first outer chamber (44') and a second outer chamber (44''), wherein the first drive fluid port (24') is disposed in the first outer chamber (17') and the second drive fluid port (24'') is arranged in the second outer chamber (17''), the protruding part defines a first piston area (30', 30''), and the rod which defines a second piston area (31', 31'') different from the first piston area (30', 30''), wherein the first piston area (30', 30'') is larger than the second piston area (31', 31'') in a fixed proportion and wherein the first part of the rod (19), over at least a part of its length, is formed with a first internal recess (40') extending from a first end surface of the rod, wherein the first internal recess (40') is in pressure communication with the first piston chamber (17'), and the second part of the rod, over at least a part of its length, is formed with a second internal recess (40'') extending from a second end surface of the rod, wherein the second internal recess (40'') is in pressure communication with the second piston chamber ( 17'') and separated from the first piston chamber (17'). 2. Dual action pressure increasing liquid partition fracturing device (2) according to claim 1, characterized in that the rod (19), during use is actuated back and forth, allowing the pressurized liquid into sequence flows into the first drive fluid port (24') and out of the second drive fluid port (24'') and then reversed to go in the opposite direction. 3. Double acting pressure boosting liquid partition fracturing device (2) according to any one of the preceding claims, characterized in that it comprises a position sensor (21) of the double acting pressure boosting liquid partition device for detecting the position of the rod. 4. Dual-action pressure-boosting liquid partition fracturing device (2) according to any one of the preceding claims, characterized in that it comprises a first seal (22') between the first part and the rod and a second seal (22 '') between the second part and the rod, wherein the first and second seals (22', 22'') are configured to be lubricated, ventilated and cooled by a lubrication system (23). 5. Double-acting pressure-boosting liquid partition fracturing device (2) according to any one of the preceding claims, characterized in that the first plunger chamber (17') and the second plunger chamber (17'') make part of a closed-loop hydraulic system, respectively. 6. System, characterized in that it comprises: - a double-acting pressure boosting liquid partition fracturing device (2) according to any one of the preceding claims 1-5, - a hydraulic pump unit (11) pressurizing the device double-acting pressure-boosting liquid partition fracturing system (2) through the first port (24') and the second port (24''), - at least two pressure transfer devices (1', 1'') in fluid communication with the first plunger port (18') and the second plunger port (18''), respectively, the first and second pressure transfer devices (1', 1'') being configured to be pressurized and discharged by the double-acting pressure-boosting liquid partition fracturing device (2) and depressurized and loaded by the double-acting pressure-boosting liquid partition fracturing device (2) assisted by a mud/sludge feed pump during charging, - a flow regulating assembly (13) comprising an inlet manifold (14) and an outlet manifold (15), wherein the flow regulation assembly (13) is configured to distribute fluid between the manifold inlet (14), pressure cavities (4', 4'') in the pressure transfer devices (1', 1'') and in the outlet manifold (15). 7. System according to claim 6, characterized in that the double-acting pressure boosting liquid partition fracturing device (2) is configured to sequentially pressurize and discharge and depressurize and charge the at least two pressure transfer devices (1', 1''), so that one pressure transfer device (1', 1'') is pressurized and discharged while the other is depressurized and charged, and vice versa. 8. System, according to claim 6 or 7, characterized by comprising four pressure transfer devices (1) and two double-action pressure increasing liquid partition fracturing devices (2), each of the pressure-increasing liquid partition fracturing devices being double-acting pressure-boosting liquid partition fracturing (2) being configured to sequentially pressurize and discharge and depressurize and charge two pressure transfer devices (1), such that two of the pressure transfer devices (1) are pressurized and discharged while the other two pressure transfer devices (1) are depressurized and charged and vice versa. 9. System according to claim 8, characterized in that the two double-acting pressure-boosting liquid partition fracturing devices (2) are configured to be operated individually, so that they can pressurize and discharge and depressurize and load two of the pressure transfer devices (1', 1'') synchronously or asynchronously. 10. System according to any one of the preceding claims 6-9, characterized in that the two pressure transfer devices (1', 1'') comprise a bellows (6, 6'') and a bellows position sensor ( 12', 12'') monitoring position of the bellows (6', 6'') and a control system adapted to receive monitoring data from the position sensor of the double acting pressure increasing liquid partition device (21) and the bellows (6', 6'') comparing the position of the stem (19) and the bellows (6', 6''). 11. Fleet characterized by comprising at least two trailers, each trailer comprising at least one system according to any one of the preceding claims 6-10. 12. Use of a dual-action pressure-boosting liquid partition fracturing device according to any one of claims 1 to 5, a system according to claims 6 to 10 or a fleet according to claim 11 characterized for the extraction or production of hydrocarbons. 13. Use of a dual-acting pressure-boosting liquid partition fracturing device according to any one of claims 1 to 5, a system according to claims 6 to 10 or a fleet according to claim 11 characterized due to hydraulic fracturing operations.