Double-sphere energy exchanger

Abstract

The invention discloses a double-sphere energy exchanger. The double-sphere energy exchanger comprises an outer ring body, the liquid inlet exchange part penetrates through and is arranged at the top end of the outer ring body; the liquid discharge exchange part penetrates through and is arranged at the bottom end of the outer ring body; the first inner ball piece is arranged on the upper portion in the outer ring body, a first ball cavity is jointly formed by the first inner ball piece and the inner wall of the outer ring body, and the outlet end of the liquid inlet exchange piece extends into the first ball cavity; the second inner ball piece is arranged on the lower portion in the outer ring body, a second ball cavity is jointly formed by the second inner ball piece and the inner wall of the outer ring body, and the inlet end of the drainage exchange piece extends into the second ball cavity; the inner wall of the outer ring body, the first inner ball piece and the second inner ball piece jointly form an exchange cavity. And the liquid inlet exchange part, the first ball cavity, the exchange cavity, the second ball cavity and the liquid discharge exchange part are communicated in sequence. The reciprocating pump water injection system has the effect of solving the technical problems caused by pressure pulsation in the reciprocating pump water injection system.

Description

TECHNICAL FIELD

[0001] The present application relates to the field of reciprocating pump delivery technology, and in particular to a double-sphere energy exchanger. BACKGROUND

[0002] In the oil extraction process, water injection is a common method. Water injection equipment mainly uses centrifugal pumps and reciprocating pumps, which are selected according to the geological structure and well depth of the oil field. The process requires that the water injection equipment can stably output pressure to achieve smooth injection, which is crucial to the oil extraction effect of underground rock fractures.

[0003] Although centrifugal pump water injection is relatively smooth, its output pressure is limited and it is difficult to efficiently complete high-pressure (such as ≥ 30 MPa) water injection tasks. Therefore, for fault block or small fault block oil fields, reciprocating pumps are usually used for small-range high-pressure water injection for one or several wells, and this method has been widely used.

[0004] However, reciprocating pumps have inherent defects: they produce pressure pulsations when delivering media. The fewer the number of cylinders and the lower the reciprocation frequency, the more pronounced the pulsation phenomenon. Currently, the industry mainly uses bladder accumulators to reduce pulsation, but this device is limited by the performance of the bladder itself. Rubber bladders are difficult to adapt to specific high-temperature, super-high-pressure working conditions, and need to be pre-inflated (usually the inflation pressure is 60% of the set output pressure). During field operation, the initial water injection pressure is low, and as the water injection progresses, the downhole pressure gradually rises to the target value, which often does not match the initial inflation pressure. The operator has to release the gas in the bladder first, and then re-inflate after the downhole pressure is raised, which is a tedious process. Due to changes in working conditions, pulsation fluctuates at any time, and external conditions are difficult to match in real time, causing pipeline vibration, support loosening, and equipment life shortening, and more seriously, oil and water pulsation can affect underground reservoirs, ultimately reducing recovery efficiency and causing irreparable losses.

[0005] Therefore, there is obvious room for improvement in the prior art. It has become an urgent need in the industry to provide a technical solution that can revolutionize conventional pulsation reduction devices. SUMMARY

[0006] The present application proposes a double-sphere energy exchanger, which is designed to solve the technical problems caused by pressure pulsation in a reciprocating pump water injection system, and aims to provide a device that can stably output medium pressure.

[0007] Specifically, the basic principle of the double-sphere energy exchanger is to form a multi-stage damping mechanism for pressure pulsation by arranging multiple mixing and buffering units in series, each of which has the function of accelerating pressure reduction and decelerating pressure increase. When the medium with pulsation flows through the exchanger, each stage of the unit will sequentially absorb and consume a part of the pulsation energy, so that the pulsation wave peak is gradually smoothed. In addition, by combining units with different characteristic sizes (such as nozzle aperture, flow passage cross section), different frequency components of the pulsation can be effectively suppressed, thereby widening the damping frequency band of the entire device. Finally, the output medium after multi-stage processing has significantly reduced pressure and flow fluctuations, which can meet the strict requirements of oilfield downhole for smooth water injection.

[0008] The double-sphere energy exchanger provided by the application adopts the following technical solutions: A double-sphere energy exchanger comprises an outer ring body; a liquid inlet exchange member penetrating and arranged at the top end of the outer ring body; a liquid outlet exchange member penetrating and arranged at the bottom end of the outer ring body; a first inner sphere member arranged at the upper part of the outer ring body, which forms a first sphere cavity together with the inner wall of the outer ring body, and the outlet end of the liquid inlet exchange member extends into the first sphere cavity; a second inner sphere member arranged at the lower part of the outer ring body, which forms a second sphere cavity together with the inner wall of the outer ring body, and the inlet end of the liquid outlet exchange member extends into the second sphere cavity; wherein the inner wall of the outer ring body, the first inner sphere member and the second inner sphere member together form an exchange cavity; the liquid inlet exchange member, the first sphere cavity, the exchange cavity, the second sphere cavity and the liquid outlet exchange member are sequentially communicated to form a fluid flow path; and at least two energy exchange units for reducing pressure pulsation are arranged on the flow path, and the energy exchange units realize the conversion of fluid acceleration pressure reduction and deceleration pressure increase through the change of flow passage cross section.

[0009] By adopting the technical scheme, the fluid with pulse motion enters from the liquid inlet exchange member, and first performs preliminary energy exchange in the first ball cavity; then, the fluid enters the exchange cavity, which is a key buffer and energy conversion area. Then, the fluid flows into the second ball cavity for further energy balance, and finally is smoothly output through the liquid outlet exchange member. In the whole process, through the cross-section change of the flow channel (mainly various nozzles), the fluid repeatedly experiences the processes of "acceleration and pressure reduction" (kinetic energy increases, and pressure energy decreases) and "deceleration and pressure increase" (kinetic energy decreases, and pressure energy increases), and the pulsation energy is gradually consumed and converted in the process. The multi-stage series energy exchange units can absorb and weaken the pulsation wave for multiple times, realize wide-band attenuation of different frequency pulses, and finally output smooth flow. The scheme is based on the principle of fluid dynamics, has a solid structure, does not need to be inflated and maintained like a bladder accumulator, and is especially suitable for high-pressure and high-temperature working conditions.

[0010] Preferably, the liquid inlet exchange member includes a liquid inlet vertical pipe part and a liquid inlet horizontal pipe part in communication with each other, two ends of the liquid inlet horizontal pipe part are closed, and two first-stage nozzles are arranged on the side wall of the liquid inlet horizontal pipe part.

[0011] By adopting the technical scheme, after the fluid enters the liquid inlet horizontal pipe part through the liquid inlet vertical pipe part, the fluid is divided into two ends of the liquid inlet horizontal pipe part and is sprayed at high speed from the two 180°-symmetric first-stage nozzles, so that the fluid collides and mixes in the first ball cavity. The T-shaped structure and the symmetric nozzles force the fluid to collide and mix intensively before entering the core exchange area and before being finally output, which can most effectively consume the turbulent kinetic energy, eliminate large-scale vortex flow, lay a foundation for smooth flow, the reaction forces generated by the 180°-symmetric jets can be offset each other, reduce the vibration of the equipment itself, and improve the operation stability and service life.

[0012] Preferably, two pairs of second-stage nozzles are arranged on the spherical surface of the first inner ball member, and each pair of second-stage nozzles is symmetrically arranged relative to the center of the first inner ball member.

[0013] By adopting the technical scheme, in the first ball cavity, after the fluid is sprayed from the two first-stage nozzles and collides and mixes, the fluid is sprayed to the exchange cavity through the symmetrically arranged second-stage nozzles on the spherical surface. The spherical surface cooperates with the symmetric nozzles to guide the fluid to form a rotating flow field in the ball cavity, prolong the residence time of the fluid, promote the fluid of different speeds and pressures to mix and balance fully, and further dissipate the fatal and directional pulsation energy into harmless heat energy, thereby enhancing the pulsation attenuation effect. The two pairs of symmetrically arranged second-stage nozzles ensure that the flow field covers the whole spherical surface of the first inner ball member, avoid the fluid stagnation area, and improve the volume utilization rate and exchange efficiency.

[0014] Preferably, the inner wall of the exchange cavity is provided with a plurality of third-stage nozzles, including a speed-reducing pressure-increasing nozzle on the first inner spherical member and a speed-increasing pressure-reducing nozzle on the input end of the second inner spherical member By adopting the above technical scheme, the fluid enters the exchange cavity from the first spherical cavity through the speed-reducing pressure-increasing nozzle, the flow channel is expanded, the flow rate is reduced, and the pressure is increased, so that the kinetic energy is converted into pressure energy, and after buffering in the exchange cavity, the fluid enters the second spherical cavity through the speed-increasing pressure-reducing nozzle, the flow channel is contracted, the flow rate is increased, and the pressure is reduced, so that the pressure energy is converted into kinetic energy. Through the active and repeated conversion of kinetic energy and pressure energy, at the high pressure peak of the pulse, the fluid is accelerated to consume energy; at the low pressure valley, the kinetic energy of the fluid is recovered and converted into pressure energy, thereby greatly smoothing the pressure fluctuation. The exchange cavity and the nozzles with different functions on the two sides jointly constitute a complete "speed-reducing pressure-increasing + buffering + speed-increasing pressure-reducing" unit, which is the core of realizing multi-stage attenuation.

[0015] Preferably, the spherical surface of the second inner spherical member is provided with a pair of fourth-stage nozzles, and the pair of fourth-stage nozzles are arranged symmetrically along a 180° direction By adopting the above technical scheme, in the second spherical cavity, the fluid is shot towards the liquid discharge exchange member through the symmetrical fourth-stage nozzles, and through the active and repeated conversion of kinetic energy and pressure energy. At the high pressure peak of the pulse, the fluid is accelerated to consume energy; at the low pressure valley, the kinetic energy of the fluid is recovered and converted into pressure energy, thereby greatly smoothing the pressure fluctuation. The exchange cavity and the nozzles with different functions on the two sides jointly constitute a complete "speed-reducing pressure-increasing + buffering + speed-increasing pressure-reducing" unit, which is the core of realizing multi-stage attenuation.

[0016] Preferably, the liquid discharge exchange member includes a liquid discharge vertical pipe portion and a liquid discharge horizontal pipe portion, the two ends of the liquid discharge horizontal pipe portion are closed, and two final output nozzles are arranged on the side wall thereof, and the two final output nozzles are arranged symmetrically along a 180° direction.

[0017] By adopting the above technical scheme, after the fluid flows out of the second spherical cavity through the fourth-stage nozzles, the fluid is output after colliding and mixing again in the T-shaped pipe of the liquid discharge exchange member. The design of the T-shaped structure and the symmetrical nozzles forces the fluid to collide and mix strongly before entering the core exchange area and before being finally output, which can most effectively consume the turbulent kinetic energy, eliminate large-scale vortex flow, and lay a foundation for stable flow. The reaction forces generated by the 180° symmetrical jets can be offset, reducing the vibration of the equipment itself and improving the operation stability and service life.

[0018] Preferably, the center lines of the final output nozzles and the fourth-stage nozzles on the second inner spherical member are arranged in a 90° staggered manner.

[0019] By adopting the technical scheme, the fluid jetted from the fourth stage nozzle in the second spherical cavity is 90 degrees to the inflow direction of the final output nozzle of the liquid discharge exchange piece. This means that the fluid is not directly collided, but is cross-impinged, sheared and mixed at a certain angle. The 90-degree staggered arrangement produces more complex turbulent shear effect, which can more effectively break and dissipate the remaining small-scale vortex and secondary pulsation, and realizes the final "refinement" smoothing. This arrangement can avoid the vibration and energy loss caused by the fluid directly colliding with the liquid discharge pipe wall, and make the flow more smooth.

[0020] Preferably, the outer ring body is composed of two half spherical shells and a cylindrical part, and is welded into an elliptical closed container.

[0021] By adopting the technical scheme, the outer ring body is a pressure-bearing shell, and its shape has an important influence on stress distribution. The elliptical closed container can conveniently form the first spherical cavity and the second spherical cavity with the first inner spherical piece and the second inner spherical piece, facilitate the collision of fluid in the spherical cavity to reduce pressure pulsation, and further reduce pressure pulsation through the rebound of fluid in the spherical cavity. In addition, the elliptical closed container has more uniform stress distribution when bearing high pressure, which can significantly improve the pressure limit and safety of the equipment, and thus is very suitable for high-pressure water injection working conditions in oil fields.

[0022] Preferably, the liquid inlet exchange piece and the liquid discharge exchange piece are both in inverted T-shaped structure, and the inner diameters of the vertical pipe parts and the horizontal pipe parts are equal.

[0023] By adopting the technical scheme, the additional pressure loss and vortex phenomenon caused by sudden change of pipe diameter can be avoided, so that the energy exchange can be more concentrated at the designed nozzle, thereby improving the efficiency of energy exchange.

[0024] Preferably, the cross-sectional shape of the first stage nozzle and the final output nozzle is elliptical. By adopting the technical scheme, the contact area of the elliptical jet with the surrounding fluid is larger, the entrainment and mixing capacity is stronger, and the pulsation energy can be dissipated faster.

[0025] In summary, the present application has at least one of the following beneficial technical effects: 1. By at least two stages of energy exchange units in series, using flow passage cross-section change to realize "acceleration pressure reduction" and "deceleration pressure increase" conversion, the pulsation wave is gradually absorbed and weakened, and the final output is very smooth flow. The multi-stage flow passage / nozzle combination design of different sizes can effectively cover the main frequency and harmonic frequency generated by the reciprocating pump, and the attenuation frequency band is wider, and the effect is much better than that of a single-stage buffer. 2. Based on the principle of fluid dynamics, the core component is a metal welded structure, which completely avoids the problems of rubber aging and frequent maintenance of traditional bladder type accumulators, and is especially suitable for harsh oilfield water injection conditions such as high pressure (≥30 MPa) and high temperature, with long equipment life and high running stability; 3. By using multiple means such as symmetric nozzles, ball cavity rotation mixing, T-shaped tube collision, 90° staggered shearing, etc., the mixing and collision of fluids are greatly promoted, and harmful pulsating energy is efficiently dissipated as heat. At the same time, the symmetric layout makes the fluid reaction forces cancel each other out, reducing equipment vibration, and designs such as an oval outer ring body optimize stress distribution, further ensuring safety under high pressure. BRIEF DESCRIPTION OF DRAWINGS

[0026] Figure 1 is a partial cross-sectional view of the double-sphere energy exchanger in this embodiment; Figure 2 is a partial cross-sectional view of the double-sphere energy exchanger in this embodiment; Figure 3 is a partial cross-sectional view of the double-sphere energy exchanger in this embodiment; Figure 4 is a partial cross-sectional view of the upper half of the double-sphere energy exchanger in this embodiment; Figure 5 is Figure 4 is a cross-sectional view along A-A; Figure 6 is a cross-sectional view of the first inner sphere, the second inner sphere, and part of the outer ring body in this embodiment; Figure 7 is a partial cross-sectional view of the lower half of the double-sphere energy exchanger in this embodiment; Figure 8 is Figure 7 is a cross-sectional view along B-B.

[0027] Reference signs: 1, outer ring body; 11, first circular part; 12, cylindrical part; 13, second circular part; 2, liquid inlet exchange member; 21, liquid inlet vertical pipe part; 22, liquid inlet horizontal pipe part; 23, first stage nozzle; 3, liquid outlet exchange member; 31, liquid outlet vertical pipe part; 32, liquid outlet horizontal pipe part; 33, final output nozzle; 4, first inner sphere; 41, second stage nozzle; 5, second inner sphere; 51, fourth stage nozzle; 6, exchange cavity; 61, third stage nozzle; 611, speed reduction and pressure increase nozzle; 612, speed increase and pressure reduction nozzle; 7, first ball cavity; 8, second ball cavity. DETAILED DESCRIPTION

[0028] The following will be described in detail in combination with the accompanying Figures 1-8 The present application is further described in detail.

[0029] Example 1 The embodiment of the present application discloses a double-sphere energy exchanger.

[0030] Referring to Figures 1-8 , comprising an outer ring body 1, a liquid inlet exchange element 2, a first inner sphere element 4, a second inner sphere element 5 and a liquid outlet exchange element 3.

[0031] The first inner sphere element 4 and the second inner sphere element 5 are both located in the outer ring body 1, the first inner sphere element 4 is connected with the top end inside the outer ring body 1 and forms a first sphere cavity 7, the second inner sphere element 5 is connected with the bottom end inside the outer ring body 1 and forms a second sphere cavity 8, and the first inner sphere element 4, the second inner sphere element 5 and the outer ring body 1 together form an exchange cavity 6, wherein the liquid inlet exchange element 2 penetrates the top end of the outer ring body 1 and extends into the first sphere cavity 7, the liquid outlet exchange element 3 penetrates the bottom end of the outer ring body 1 and extends into the second sphere cavity 8, and these components are combined into a whole through welding to form a multi-stage acceleration pressure reduction and deceleration pressure increase mixed buffer unit for attenuating the pulsation generated by a reciprocating pump.

[0032] The outer ring body 1 comprises a first circular part 11, a cylindrical part 12 and a second circular part 13 from top to bottom, wherein the first circular part 11 and the second circular part 13 are half-sphere shells and are welded together to form an elliptical closed container, the outer ring body 1 serves as a pressure-bearing shell, and the shape of the outer ring body 1 has an important influence on stress distribution. The elliptical closed container can conveniently form the first sphere cavity 7 and the second sphere cavity 8 together with the first inner sphere element 4 and the second inner sphere element 5, facilitates the collision of fluid in the sphere cavity to reduce pressure pulsation, can further reduce pressure pulsation through the rebound of fluid in the sphere cavity, and makes the overall structure of the double-sphere energy exchanger relatively simple and facilitates production cooperation. In addition, when the elliptical closed container bears high pressure, the stress distribution is more uniform, this characteristic can significantly improve the pressure limit and safety of the equipment, and thus the outer ring body 1 is very suitable for high-pressure water injection working conditions in oil fields.

[0033] The liquid inlet exchange piece 2 comprises a liquid inlet vertical pipe part 21 and a liquid inlet horizontal pipe part 22, the liquid inlet vertical pipe part 21 and the liquid inlet horizontal pipe part 22 are vertically arranged and welded in an inverted "T" shape, the hole inner diameters of the liquid inlet vertical pipe part 21 and the liquid inlet horizontal pipe part 22 are equal, the two ends of the liquid inlet horizontal pipe part 22 are closed, the liquid inlet horizontal pipe part 22 is provided with two first-stage nozzles 23 (A, B) for speed increasing and pressure reducing on the front and back side walls near the two ends respectively, so that the two first-stage nozzles 23 are arranged in a 180° direction, the distance between the two first-stage nozzles 23 is L, and the liquid inlet exchange piece 2 is welded with the outer ring body 1 at a distance of a predetermined size H from the center line of the first ball cavity 7, so that the liquid inlet exchange piece 2 and the first inner ball piece 4 jointly form a mixed buffer zone for speed increasing and pressure reducing and speed reducing and pressure increasing, for consuming pulsating energy, wherein the design of the T-shaped structure and the symmetrical nozzles forces the fluid to collide and mix strongly before entering the core exchange area and finally outputting, which can most effectively consume turbulent kinetic energy, eliminate large-scale vortex flow, lay the foundation for smooth flow, the reaction forces generated by the 180° symmetrical jets can be offset, reducing the vibration of the equipment itself, improving the operation stability and service life.

[0034] The first inner ball piece 4 is in a semi-spherical shell shape, the first inner ball piece 4 is welded with the first circular part 11 of the outer ring body 1 to form a complete ball cavity, that is, the first ball cavity 7, and two groups of second-stage nozzles 41 (C, D and E, F) are positioned and welded on the spherical surface of the first inner ball piece 4 according to the preset theoretical parameters (such as H1, L1, L2), so that each pair of second-stage nozzles 41 is arranged symmetrically with respect to the center of the spherical surface of the first inner ball piece 4, and the inflow directions of each pair of nozzles are also symmetrical in a 180° direction, and the function of the second-stage nozzles 41 is mainly to increase speed and reduce pressure, the fluid is rotated in the first ball cavity 7 of the outer ring body 1 by the 180° opposite injection of the first-stage nozzles 23A, B, and then is injected out of the second-stage nozzles 41C, D, E, F on the first inner ball piece 4, so that the fluid always collides and balances in rotation at different flow rates and pressures to consume and attenuate part of the speed and pressure pulsations, wherein in the first ball cavity 7, after the fluid is injected out of the two first-stage nozzles 23, the fluid is injected into the exchange cavity 6 through the symmetrically arranged second-stage nozzles 41 on the spherical surface after collision and mixing, the spherical surface cooperates with the symmetrical nozzles to guide the fluid to form a rotating flow field in the ball cavity, prolong the residence time of the fluid, promote the full mixing and balance of the fluids with different speeds and pressures, and further dissipate the fatal and directional pulsating energy into harmless heat energy through rotation and collision, thereby enhancing the pulsation attenuation effect, and the two pairs of symmetrically arranged second-stage nozzles 41 ensure that the flow field covers the entire ball cavity space, avoids the fluid stagnation area, and improves the volume utilization rate and the exchange efficiency.

[0035] The inner wall surface of the exchange cavity 6 is provided with six third-stage nozzles 61 (G, H, I, J, K, O), which can be divided into two categories: two of them (G, H) are located at the outer edge of the first inner spherical member 4, allowing fluid to flow from the first spherical cavity 7 into the exchange cavity 6; the middle two (I, J) are located at the inner edge of the first inner spherical member 4, and two (K, O) are located at the input end of the second inner spherical member 5, wherein G, H, I, J are deceleration and pressure-increasing nozzles 611, through which the fluid entering the exchange cavity 6 is decelerated and pressurized, realizing the conversion of kinetic energy into pressure energy; then the fluid is rotated and mixed in the exchange cavity 6, enters the second inner spherical member 5 through nozzles K, O (deceleration and pressure reduction), and further consumes pulsating energy.

[0036] The second inner spherical member 5 is also a hemispherical shell, and the second inner spherical member 5 is symmetrically arranged with the first inner spherical member 4, and the second inner spherical member 5 is welded with the second circular part 13 of the outer ring body 1 to form a complete spherical cavity, that is, the second spherical cavity 8. On the spherical surface of the second inner spherical member 5, a pair of fourth-stage nozzles 51 (P, Q) are provided, the centers of the two nozzles are apart by L3, and the inflow direction is 180°, which is used to receive the fluid treated by the exchange cavity 6. Among them, in the second spherical cavity 8, the fluid is shot to the liquid discharge exchange member 3 through the symmetrical fourth-stage nozzles 51, and the conversion of kinetic energy and pressure energy is actively and repeatedly carried out. At the peak of pulsating high pressure, the fluid is accelerated to consume energy; at the low pressure valley, the kinetic energy of the fluid is recovered and converted into pressure energy, thereby greatly smoothing the pressure fluctuation. The exchange cavity 6 and the nozzles with different functions on both sides jointly constitute a complete "deceleration and pressure increase + buffer + acceleration and pressure reduction" unit, which is the core of realizing multi-stage attenuation.

[0037] The liquid discharge exchange member 3 partially extends into the second inner spherical member 5, and includes a liquid discharge vertical pipe portion 31 and a liquid discharge horizontal pipe portion 32. The liquid discharge vertical pipe portion 31 is inserted into the inner hole of the bottom end of the outer ring body 1, and is positioned and welded with the second inner spherical member 5 according to parameters H2 and L4. The liquid discharge horizontal pipe portion 32 is closed at both ends, and a pair of 180° directionally symmetrical nozzles (W, S) are arranged on the outer circle as final output nozzles 33. The center lines of the nozzles W, S are arranged at 90° with the center lines of the nozzles P, Q of the second inner spherical member 5, for collecting fluid and performing the last collision mixing. Similarly, the T-shaped structure and the symmetrical nozzle design force the fluid to collide and mix strongly before entering the core exchange area and before the final output, can most effectively consume the turbulent flow kinetic energy, eliminate large-scale vortexes, lay the foundation for smooth flow, the reaction force generated by the 180° symmetrical jet can be offset, reducing the vibration of the equipment itself, improving the operation stability and service life, and the fluid ejected from the fourth stage nozzle 51 in the second spherical cavity 8 is at 90° with the inflow direction of the final output nozzle 33 of the liquid discharge exchange member 3. This means that the fluid is not directly collided, but is impacted, sheared and mixed at a certain angle, the 90° staggered arrangement produces more complex turbulent shear action, which can more effectively break and dissipate the remaining small-scale vortexes and secondary pulsations, to achieve the final "refinement" smoothing. This arrangement can avoid the vibration and energy loss caused by the fluid directly colliding with the liquid discharge pipe wall, and make the flow more smooth.

[0038] The liquid discharge exchange member 3 has the same structure as the liquid inlet exchange member 2, and also has a reverse "T" shape, for collecting the fluid after multi-stage processing and smoothly outputting.

[0039] Specifically, in operation, the exchange member is installed in series at the discharge outlet of the reciprocating pump. The high-pressure medium with strong pulsation first enters the liquid inlet exchange member 2.

[0040] First stage energy exchange: the fluid is divided in the horizontal pipe portion of the liquid inlet exchange member 2, and is accelerated and decompressed through the nozzles A, B at both ends, and is then injected at high speed into the spherical cavity of the first inner spherical member 4. The fluid rotates, collides and mixes in the spherical cavity, and preliminarily consumes part of the pulsation energy.

[0041] Second stage energy exchange: the fluid then passes through the second stage nozzles 41 (C, D, E, F) on the first inner spherical member 4 to be accelerated and decompressed again, and then enters the central exchange cavity 6 through the deceleration and pressure-increasing nozzles 61 G, H, I, J after further energy consumption.

[0042] Third stage energy exchange: in the exchange cavity 6, the fluid impacts the spherical surface, and the change in flow area causes it to be decelerated and pressurized, realizing the conversion of kinetic energy and pressure energy. Subsequently, the fluid enters the second inner spherical member 5 after being accelerated and decompressed through the nozzles K, O.

[0043] Fourth stage energy exchange and final output: in the second inner sphere 5, the fluid is subjected to the last speed reduction and pressure increase through the nozzles P, Q, the high-speed kinetic energy is converted into stable pressure energy. Finally, the fluid is collected in the T-shaped pipe of the liquid discharge exchange member 3, collides and mixes through the nozzles W, S, the turbulent kinetic energy is further consumed, and the stable pressure and flow are output to the downhole. This scheme is based on the principle of fluid dynamics, has a solid structure, does not need to be inflated and maintained like a bladder accumulator, and is especially suitable for high-pressure and high-temperature working conditions.

[0044] The core of the working principle of the present application is to attenuate the fluid pulsation through multiple stages of "speed reduction and pressure increase" and "speed increase and pressure reduction" units. The high-pressure peak fluid of the pulsation consumes energy in the "speed reduction and pressure increase" link, and the remaining kinetic energy is gently recovered as pressure energy in the "speed increase and pressure reduction" link. The combination of nozzles of different sizes effectively broadens the attenuation frequency band. Finally, after four stages of energy exchange, the strong pressure / flow pulsation is converted into stable flow that meets the downhole water injection requirements.

[0045] Further, in the embodiment, the cross-sectional shape of the first-stage nozzle 23 and the final output nozzle 33 can be not only circular but also elliptical. The elliptical jet has a larger contact area with the surrounding fluid, stronger entrainment and mixing ability, and can consume pulsation energy faster.

[0046] Further, the four-stage energy exchange structure shown in the embodiment is a specific implementation of the present application. The core of the present application is the multiple-stage energy exchange unit arranged on the flow path, and the number of stages can be configured according to the actual pulsation attenuation requirements. As long as it contains at least two energy exchange units that realize speed reduction and pressure increase and speed increase and pressure reduction conversion through cross-sectional area change of the flow passage, the purpose of the present application can be achieved.

[0047] Further, in the embodiment, the C, D, E, and F nozzles in the second-stage nozzle are in communication with and positionally corresponding to the speed reduction and pressure increase nozzles G, H, I, and J of the third-stage nozzle, respectively; and the speed increase and pressure reduction nozzles K and O of the third-stage nozzle are in communication with and positionally corresponding to the fourth-stage nozzles P and Q, respectively.

[0048] It should be noted that the embodiments of the present application can be arbitrarily combined into new embodiments as long as the schemes do not conflict and the technical schemes can coexist.

[0049] The above are the preferred embodiments of the present application, which do not limit the protection scope of the present application. Therefore, equivalent changes made on the basis of the structure, shape, and principle of the present application should be covered within the protection scope of the present application.

Claims

1. A double-sphere energy exchanger, characterized by: The utility model relates to a kind of fluid energy exchange devices, including Outer ring body (1); Liquid inlet exchange piece (2), through and being arranged at the top of the outer ring body (1); Liquid outlet exchange piece (3), through and being arranged at the bottom of the outer ring body (1); First inner sphere piece (4), arranged in the upper portion of the outer ring body (1), with the inner wall of the outer ring body (1) jointly formed with first ball cavity (7), and the outlet end of the liquid inlet exchange piece (2) is inserted into the first ball cavity (7); Second inner sphere piece (5), arranged in the lower portion of the outer ring body (1), with the inner wall of the outer ring body (1) jointly formed with second ball cavity (8), and the inlet end of the liquid outlet exchange piece (3) is inserted into the second ball cavity (8); Wherein, the inner wall of the outer ring body (1), the first inner sphere piece (4) and the second inner sphere piece (5) jointly form exchange cavity (6); The liquid inlet exchange piece (2), the first ball cavity (7), the exchange cavity (6), the second ball cavity (8) and the liquid outlet exchange piece (3) are sequentially communicated, to constitute the flow path of fluid;And, at least two energy exchange units for reducing pressure pulsation are arranged on the flow path, and the energy exchange unit is converted by the change of flow passage section to realize fluid acceleration pressure reduction and deceleration pressure increase.

2. The dual-sphere energy exchanger of claim 1, wherein: The liquid inlet exchange piece (2) includes liquid inlet vertical pipe part (21) and liquid inlet horizontal pipe part (22) communicated with each other, the both ends of the liquid inlet horizontal pipe part (22) are closed, and two first-stage nozzles (23) are arranged on the side wall of the liquid inlet horizontal pipe part (22), and the two first-stage nozzles (23) are symmetrically arranged along the direction of 180°.

3. The dual-sphere energy exchanger of claim 1, wherein: Two pairs of second-stage nozzles (41) are arranged on the spherical surface of the first inner sphere piece (4), and each pair of second-stage nozzles (41) is symmetrically arranged with respect to the center of the first inner sphere piece (4).

4. The dual-sphere energy exchanger of claim 1, wherein: The inner wall of the exchange cavity (6) is provided with a plurality of third-stage nozzles (61), including deceleration pressure-increasing nozzle (611) located on the first inner sphere piece (4) and acceleration pressure-decreasing nozzle (612) located at the input end of the second inner sphere piece (5).

5. The double-sphere energy exchanger of claim 1, wherein: A pair of fourth-stage nozzles (51) are arranged on the spherical surface of the second inner sphere piece (5), and the pair of fourth-stage nozzles (51) are symmetrically arranged along the direction of 180°.

6. The double-sphere energy exchanger of claim 2, wherein: The liquid outlet exchange piece (3) includes liquid outlet vertical pipe part (31) and liquid outlet horizontal pipe part (32), the both ends of the liquid outlet horizontal pipe part (32) are closed, and two final output nozzles (33) are arranged on the side wall thereof, and the two final output nozzles (33) are symmetrically arranged along the direction of 180°.

7. The double-sphere energy exchanger of claim 6, wherein: The center line of the final output nozzle (33) and the center line of the fourth-stage nozzle (51) on the second inner sphere piece (5) are arranged in a staggered manner at 90°.

8. The dual-sphere energy exchanger of claim 1, wherein: The outer ring body (1) is composed of two hemispherical shells and a cylindrical part (12) to form an elliptical closed container.

9. The double-sphere energy exchanger of claim 1, wherein: The liquid inlet exchange piece (2) and the liquid outlet exchange piece (3) are both inverted T-shaped structures, and the inner diameters of the vertical pipe parts and the horizontal pipe parts of the two are equal.

10. The double-sphere energy exchanger of claim 6, wherein: The cross-sectional shape of the first-stage nozzle (23) and the final output nozzle (33) is elliptical.

Images