CN120513349A

CN120513349A - Non-axial flow pressure exchanger

Info

Publication number: CN120513349A
Application number: CN202480006837.9A
Authority: CN
Inventors: M·J·帕托姆; O·萨姆德瑞拉
Original assignee: Energy Recovery Inc
Current assignee: Energy Recovery Inc
Priority date: 2023-01-06
Filing date: 2024-01-04
Publication date: 2025-08-19
Also published as: EP4646537A1; IL321914A; WO2024148188A1

Abstract

A pressure exchanger includes a rotor configured to receive a first fluid, receive a second fluid, and exchange pressure between the first fluid and the second fluid. The pressure exchanger also includes a sleeve disposed around the rotor, wherein the first fluid radially enters the rotor through the sleeve. The pressure exchanger also includes a column disposed within the rotor.

Description

Non-axial flow pressure exchanger

Technical Field

The present invention relates to pressure exchangers, and more particularly, to non-axial flow pressure exchangers.

Background

The system uses fluids at different pressures. The system uses components to increase the pressure of the fluid.

Drawings

The present disclosure is illustrated by way of example, and not by way of limitation, in the figures of the accompanying drawings.

Fig. 1A-1D illustrate schematic diagrams of fluid treatment systems including hydraulic energy transfer systems, according to certain embodiments.

Fig. 2A-2E are exploded perspective views of a pressure exchanger (PX) according to some embodiments.

Fig. 3A illustrates a perspective view of an assembly of a pressure exchanger, according to some embodiments.

Fig. 3B illustrates a cross-sectional view of an assembly of a pressure exchanger, according to some embodiments.

Fig. 3C illustrates a top or bottom view of a rotor of a pressure exchanger, according to some embodiments.

Fig. 4A illustrates a perspective view of an assembly of a pressure exchanger, according to some embodiments.

Fig. 4B-4C illustrate cross-sectional views of components of a pressure exchanger, according to some embodiments.

Fig. 4D illustrates a perspective view of an assembly of a pressure exchanger, according to some embodiments.

Fig. 4E-4F illustrate cross-sectional views of components of a pressure exchanger, according to some embodiments.

Fig. 4G illustrates a perspective view of an assembly of a pressure exchanger, according to some embodiments.

Fig. 5A-5B illustrate components of a pressure exchanger according to some embodiments.

Fig. 6A-6B illustrate components of a pressure exchanger according to some embodiments.

Fig. 7A-7B illustrate components of a pressure exchanger according to certain embodiments.

Detailed Description

Embodiments described herein relate to non-axial flow pressure exchangers (e.g., pressure exchangers in which fluid enters and/or exits a rotor in a non-axial manner).

The system may use fluids of different pressures. The fluid supplied to the system may be at a lower pressure and one or more portions of the system may be operating at a higher pressure. The system may include a closed circuit in which various fluid pressures are maintained in different portions of the circuit. These systems may include hydraulic fracturing (e.g., hydraulic fracturing (fracturing) or fracturing (fracing)) systems, desalination systems, refrigeration systems, heat pump systems, energy generation systems, mud pumping systems, slurry pumping systems, industrial fluid systems, waste fluid systems, fluid transfer systems, and the like. Pumps or compressors may be used to increase the pressure of the fluid of such systems.

Conventionally, systems (e.g., refrigeration systems, heat pump systems, reversible heat pump systems, water systems, etc.) use pumps or compressors to increase the pressure of a fluid (e.g., a refrigeration fluid such as carbon dioxide (CO ₂), R-744, R-134A, hydrocarbons, hydrofluorocarbons (HFCs), hydrochlorofluorocarbons (HCFCs), ammonia (NH ₃), refrigerant mixtures, R-407A, R-404A, etc.). Conventionally, a separate pump or compressor mechanically coupled to the motor is used to increase the fluid pressure in any portion of the system including the fluid pressure increase. Pumps and compressors, particularly pumps and compressors operating at large pressure differentials (e.g., resulting in a substantial increase in fluid pressure), require a significant amount of energy. Thus, conventional systems consume a significant amount of energy to increase fluid pressure (via a pump or compressor driven by a motor). In addition, conventional heat transfer systems reduce the pressure of the fluid through expansion valves and/or heat exchangers (e.g., condensers and/or evaporators, etc.). Conventional systems are not effective in increasing fluid pressure and decreasing fluid pressure. This is wasteful of energy used to operate conventional systems (e.g., energy used to repeatedly increase the pressure of the refrigeration fluid to raise or lower the temperature of the surrounding environment). Conventional systems have unexpected leaks or mixing in the pressure exchanger.

The systems, devices, and methods of the present disclosure provide solutions to these and other shortcomings of conventional systems. The present disclosure provides a pressure exchanger (pressure exchanger) for use in a system (e.g., a fluid handling system, a heat transfer system, a refrigeration system, a heat pump system, a cooling system, a heating system, etc.). In one system, the pressure exchanger may be configured to exchange pressure between a first fluid (e.g., a high pressure portion of a refrigerant fluid in a refrigeration cycle) and a second fluid (e.g., a low pressure portion of a refrigerant fluid in a refrigeration cycle). The pressure exchanger may receive a first fluid (e.g., a high pressure portion of a refrigeration fluid) via a first inlet (e.g., a high pressure inlet) and a second fluid (e.g., a low pressure portion of the refrigeration fluid) via a second inlet (e.g., a low pressure inlet). When entering the pressure exchanger, the pressure of the first fluid may be higher than the pressure of the second fluid. The pressure exchanger may exchange pressure between the first fluid and the second fluid. The first fluid may exit the pressure exchanger via a first outlet (e.g., a low pressure outlet) and the second fluid may exit the pressure exchanger via a second outlet (e.g., a high pressure outlet). When exiting the pressure exchanger, the second fluid may have a higher pressure than the first fluid (e.g., the pressure has been exchanged between the first fluid and the second fluid).

In some embodiments, the pressure exchanger includes a rotor configured to receive a first fluid, to receive a second fluid, and to exchange pressure between the first fluid and the second fluid. The pressure exchanger may further comprise a sleeve disposed around the rotor, wherein the first fluid enters the rotor radially through the sleeve. The pressure exchanger may further comprise a stationary column provided inside the rotor.

In some embodiments, the second fluid may enter the rotor radially via the post. The column may form a first Low Pressure Input (LPIN) port and a first Low Pressure Output (LPOUT) port, or a first High Pressure Input (HPIN) port and a first High Pressure Output (HPOUT) port. The column may also form a second low pressure input port and a second low pressure output port, or a second high pressure input port and a second high pressure output port. The sleeve may form a first low pressure input port and a first low pressure output port, or a first high pressure input port and a first high pressure output port. The sleeve may also form a second low pressure input port and a second low pressure output port, or a second high pressure input port and a second high pressure output port.

In some embodiments, the rotor may be configured to rotate about an axis of rotation. The sleeve may form an angled port disposed about a port axis, wherein the port axis does not intersect the rotation axis.

In some embodiments, the post may form an angled port disposed about a port axis, wherein the port axis does not intersect the rotation axis.

In some embodiments, the rotor forms a plurality of conduits, wherein at least one of the first fluid or the second fluid is to enter the rotor radially via the plurality of conduits. In some embodiments, the plurality of conduits may be external Zhou Caowen. The outer Zhou Caowen channels may refer to the channels formed by the rotor surface. The surface of the rotor may form substantially parallel grooves or channels (forming the outer Zhou Caowen channels). The outer Zhou Caowen channels may be oriented longitudinally with respect to the length of the rotor. The outer Zhou Caowen channels may have a uniform shape and depth, forming a uniform pattern on the rotor surface. In some embodiments, the outer Zhou Caowen tube may be covered by a sleeve that wraps around the rotor, such that the outer Zhou Caowen tube is closed. In some embodiments, the outer Zhou Caowen channels may be formed by the rotor (e.g., grooves or channels on the outer surface of the rotor). The outer Zhou Caowen channels may vary in depth, width, and shape. The outer Zhou Caowen tubing may be a passageway (conduit) for controlling fluid or gas flow, improving heat transfer, and improving pressure exchange efficiency. The rotor has a flat upper surface, a flat lower surface, a curved inner side surface (in which the posts are disposed) and a curved outer side surface. The curved outer side surface may be formed into a channel of outer Zhou Caowen (fluted). The rotor and sleeve form a passageway and/or conduit between the tube forming the outer Zhou Caowen and the inside surface of the sleeve. In some embodiments, a sleeve (e.g., disposed about the rotor) may seal the outer Zhou Caowen (e.g., to contain the fluid). The sleeve may be a cylindrical housing enclosing the rotor and covering the tubing into an outer Zhou Caowen. Such sealing allows (e.g., ensures) fluid or gas within the outer Zhou Caowen pipe to be contained and directed according to a desired flow pattern, which has less (e.g., prevents) accidental leakage or mixing than conventional systems.

In some embodiments, the pressure exchanger includes a rotor configured to exchange pressure between the first fluid and the second fluid, the rotor forming a rotor cavity. In some embodiments, the rotor includes an outer surface, wherein the first fluid enters the rotor radially via the outer surface. The rotor further includes an inner side surface forming a rotor cavity, wherein the second fluid enters the rotor radially via the inner side surface.

In some embodiments, the pressure exchanger further comprises a column disposed in the rotor cavity, the column having a column cavity, wherein the second fluid enters the column cavity axially and exits the column cavity radially to enter the rotor radially. The rotor may form a conduit, wherein at least one of the first fluid or the second fluid enters the rotor radially into the at least one conduit. The conduit may be external Zhou Caowen. In some embodiments, an outer Zhou Caowen (flight) of the outer Zhou Caowen tube leads to at least one of a sleeve or post disposed about the rotor. The conduit may start near a first distal end of the rotor and end across the rotor near a second distal end of the rotor.

In some embodiments, outer Zhou Caowen, which is the conduit of outer Zhou Caowen, refers to a single groove or channel (e.g., formed by the conduit of outer Zhou Caowen) on the outer surface of the rotor. In some embodiments, the peripheral flutes may be concave features on the rotor surface. The outer Zhou Caowen may vary in depth, width, and shape, and may be a passageway (conduit) for fluid or gas to flow. In some embodiments, outer Zhou Caowen is a channel or groove formed by a pipe that is outer Zhou Caowen.

In some embodiments, the plurality of conduits may be configured to pass through the rotor in a helical trajectory. The helical duct may be external Zhou Caowen and may be formed by the outer or inner surface of the rotor. The helical duct may also be an internal channel within the rotor body (e.g., closed by the rotor rather than by a combination of rotor and sleeve).

In some embodiments, the rotor may be configured to rotate about an axis of rotation. The post may form an angled port disposed about a port axis that does not intersect the rotation axis.

In some embodiments, the pressure exchanger includes a rotor forming a radial conduit. The radial conduits may be conduits arranged in a radial pattern. For example, the radial conduit may extend outwardly from a center point or axis of the rotor. The radial conduit may be configured to extend from a central axis of the cross-sectional circle of the rotor directly towards a circumference of the cross-sectional circle of the rotor. The conduit may be linear, emanating from the geometric center of the cross-sectional circle and reaching the outer surface of the cylindrical rotor.

The rotor may be configured to receive a first fluid, receive a second fluid, and exchange pressure between the first fluid and the second fluid. The pressure exchanger may include a column disposed within a cavity formed by the rotor, wherein the first fluid enters the rotor radially into a radial conduit of the radial conduit via a sleeve or column disposed about the rotor forming a first pair of ports and exits the rotor radially via a second port of the first pair of ports.

In some embodiments, the pressure exchanger includes a second pair of ports formed by a sleeve or column. A sleeve is disposed about the rotor and a post is disposed within the rotor cavity. In some embodiments, the second pair of ports includes a low voltage input (LPIN) port and a high voltage output (HPOUT) port, or a high voltage input (HPIN) port and a low voltage output (LPOUT) port.

In some embodiments, the first pair of ports formed by the sleeve or the column may include a low pressure input port and a high pressure output port, or a high pressure input port and a low pressure output port.

In some embodiments, the rotor may be configured to rotate about an axis of rotation. The post may form an angled port disposed about a port axis, wherein the port axis does not intersect the rotation axis.

In some embodiments, the pressure exchanger includes a third pair of ports formed by a sleeve or column. The third pair of ports may include a low pressure input port and a high pressure output port, or a high pressure input port and a low pressure output port.

In some embodiments, the pressure exchanger includes a fourth pair of ports formed by a sleeve or column. The fourth pair of ports may include a low pressure input port and a high pressure output port, or a high pressure input port and a low pressure output port.

In some embodiments, the pressure exchanger includes one or more features described in one or more of fig. 3A-7B.

The systems, devices, and methods of the present disclosure have advantages over conventional solutions. The system of the present disclosure reduces energy consumption compared to conventional systems. For example, using the pressure exchanger of the present disclosure, energy stored as pressure may be recovered and transferred back to the system, thereby reducing the energy costs of operating the system and improving efficiency. The system of the present disclosure may reduce wear of components (e.g., pump, compressor) compared to conventional systems. The system of the present disclosure prevents accidental leakage or mixing.

Although some embodiments of the present disclosure are described with respect to pressure exchangers, energy recovery devices, and hydraulic energy transfer systems, the present disclosure may be applied to other systems and devices (e.g., non-isobaric pressure exchangers, rotating components of non-pressure exchangers, non-rotating pressure exchangers, systems that do not include a pressure exchanger, etc.).

Although some embodiments of the present disclosure are described with respect to exchanging pressure between fluids used in fracturing systems, desalination systems, heat pump systems, and/or refrigeration systems, the present disclosure may be applied to other types of systems. The fluid may refer to a liquid, a gas, a transcritical fluid, a supercritical fluid, a subcritical fluid, and/or a combination thereof.

Fig. 1A-1D illustrate schematic diagrams of a fluid treatment system 100 including a hydraulic energy transfer system 110, according to certain embodiments.

In some embodiments, hydraulic energy transfer system 110 includes a pressure exchanger (e.g., a pressure exchanger). The pressure exchanger may include one or more features described in one or more of fig. 3A-7B. In some embodiments, the pressure exchanger includes a rotor configured to receive a first fluid, to receive a second fluid, and to exchange pressure between the first fluid and the second fluid. The first fluid and/or the second fluid enters the rotor non-axially and/or exits the rotor non-axially.

The hydraulic energy transfer system 110 (e.g., a pressure exchanger) receives a Low Pressure (LP) fluid input 120 (e.g., a low pressure inlet stream) from a Low Pressure (LP) input system 122. The hydraulic energy transfer system 110 also receives a high pressure fluid input 130 (e.g., a high pressure inlet stream) from a High Pressure (HP) input system 132. The hydraulic energy transfer system 110 (e.g., a pressure exchanger) exchanges pressure between the high pressure fluid input 130 and the low pressure fluid input 120 to provide a low pressure fluid output 140 (e.g., a low pressure outlet flow) to a low pressure fluid output system 142 and a high pressure fluid output 150 (e.g., a high pressure outlet flow) to a high pressure fluid output system 152.

In some embodiments, hydraulic energy transfer system 110 includes a pressure exchanger to exchange pressure between high pressure fluid input 130 and low pressure fluid input 120. The pressure exchanger may be a device that transfers fluid pressure between the high pressure fluid input 130 and the low pressure fluid input 120 with an efficiency of greater than about 50%, 60%, 70%, 80%, 90% or more (e.g., without using centrifugal technology). High pressure (e.g., high pressure fluid input 130, high pressure fluid output 150) refers to a pressure that is higher than low pressure (e.g., low pressure fluid input 120, low pressure fluid output 140). The low pressure fluid input 120 of the pressure exchanger may be pressurized and exit the pressure exchanger at a high pressure (e.g., high pressure fluid output 150 at a pressure greater than the pressure of the low pressure fluid input 120), while the high pressure fluid input 130 may be depressurized and exit the pressure exchanger at a low pressure (e.g., low pressure fluid output 140 at a pressure lower than the pressure of the high pressure fluid input 130). The pressure exchanger may operate with the high pressure fluid input 130 directly applying a force to pressurize the low pressure fluid input 120, with or without a fluid separator between the fluids. Examples of fluid separators that may be used with a pressure exchanger include, but are not limited to, pistons, bladders, diaphragms, and the like. In some embodiments, the pressure exchanger may be a rotating device. A rotary pressure exchanger, such as that manufactured by Energy Recovery company (inc.) of san francisco An Deluo, california, may not have any separate valve because the effective valving action is accomplished inside the device via relative movement of the rotor with respect to the end cap. The rotary pressure exchanger may be designed to operate with an internal piston to isolate the fluid and transfer pressure with relatively little mixing of the inlet fluid streams. The reciprocating pressure exchanger may include pistons reciprocating in the rotor ducts for transmitting pressure between the fluid streams. Any one or more pressure exchangers may be used in the present disclosure, such as, but not limited to, a rotary pressure exchanger, a reciprocating pressure exchanger, or any combination thereof. Furthermore, the pressure exchanger may be provided on a sled (carriage) separate from other components of the fluid treatment system 100 (e.g., where the pressure exchanger is attached to an existing fluid treatment system).

In some embodiments, motor 160 is coupled to hydraulic energy transfer system 110 (e.g., to a pressure exchanger). In some embodiments, motor 160 controls the speed of the rotor of hydraulic energy transfer system 110 (e.g., to increase the pressure of high-pressure fluid output 150, decrease the pressure of high-pressure fluid input 130, etc.). In some embodiments, the motor 160 generates energy (e.g., acts as a motor) based on pressure exchanges in the hydraulic energy transfer system 110.

The hydraulic energy transfer system 110 may be a hydraulic protection system (e.g., hydraulic buffer system, hydraulic isolation system) that may prevent or limit contact between a fluid loaded with solid particles (e.g., fracturing fluid) and various devices (e.g., hydraulic fracturing device, high pressure pump) while exchanging work and/or pressure with another fluid. By preventing or limiting contact between various devices (e.g., fracturing devices) and fluids containing solid particulates, the hydraulic energy transfer system 110 increases the life and performance of the various devices (e.g., fracturing devices, high pressure fluid pumps) while reducing wear and damage. By using equipment (e.g., high pressure fluid pumps) that is not designed for abrasive fluids (e.g., fracturing fluids and/or corrosive fluids), less expensive equipment may be used in the fluid treatment system 100.

The hydraulic energy transfer system 110 may include a hydraulic turbocharger or a hydraulic pressure exchanger system, such as a rotary pressure exchanger. The pressure exchanger may include one or more chambers (e.g., 1 to 100) to facilitate pressure transfer and pressure equalization between volumes of the first fluid and the second fluid (e.g., gas, liquid, multiphase fluid). In some embodiments, the pressure exchanger may transfer pressure between a first fluid (e.g., a pressure exchange fluid, such as a proppant-free or substantially proppant-free fluid) and a second fluid, which may be highly viscous and/or contain solid particles (e.g., fracturing fluid containing sand, proppant, powder, debris, ceramic). The solid particulate fluid may cause wear and/or erosion of pressure exchanger components such as the rotor and end caps of the pressure exchanger. As the rotor rotates relative to the end caps, the fluid (e.g., abrasive particles in the fluid) may cause the interface between the rotor and each end cap to wear. Replacement of the wear parts of the pressure exchanger can be expensive.

The hydraulic energy transfer system 110 may be used in different types of systems, such as fracturing systems, desalination systems, refrigeration systems, and the like.

FIG. 1A illustrates a schematic diagram of a fluid treatment system 100A including a hydraulic energy transfer system 110, according to some embodiments. The fluid treatment system 100A may include a control module 180, the control module 180 including one or more controllers 185.

Fig. 1B illustrates a schematic diagram of a fluid treatment system 100B including a hydraulic energy transfer system 110, according to some embodiments. The fluid treatment system 100B may be a fracturing system. In some embodiments, fluid treatment system 100B includes more components, fewer components, the same wiring, different wiring, and/or the like than shown in fig. 1B.

The low pressure fluid input 120 and the high pressure fluid output 150 may be fracturing fluids (e.g., fluids including solid particles, proppant fluids, etc.). The high pressure fluid input 130 and the low pressure fluid output 140 may be substantially solid particle free fluids (e.g., proppant free fluids, water, filtered fluids, etc.).

The low pressure input system 122 may include one or more low pressure fluid pumps to provide the low pressure fluid input 120 to the hydraulic energy transfer system 110 (e.g., a pressure exchanger). The high pressure input system 132 may include one or more high pressure fluid pumps 134 to provide the high pressure fluid input 130 to the hydraulic energy transfer system 110.

The hydraulic energy transfer system 110 exchanges pressure between a low pressure fluid input 120 (e.g., low pressure fracturing fluid) and a high pressure fluid input 130 (e.g., high pressure water) to provide a high pressure fluid output 150 (e.g., high pressure fracturing fluid) to a high pressure output system 152 and a low pressure fluid output 140 (e.g., low pressure water). High pressure output system 152 may include a formation 154 (e.g., a well), and formation 154 includes a fracture 156. Solid particulates (e.g., proppants) from the high pressure fluid output 150 may be provided into a fracture 156 of the formation.

In some embodiments, the low pressure fluid output 140, the high pressure fluid pump 134, and the high pressure fluid input 130 are part of a first loop (e.g., a proppant-free fluid loop). The low pressure fluid output 140 may be provided to a high pressure fluid pump to create a high pressure fluid input 130 that becomes the low pressure fluid output 140 upon exiting the hydraulic energy transfer system 110.

In some embodiments, the low pressure fluid input 120, the high pressure fluid output 150, and the low pressure fluid pump 124 are part of a second circuit (e.g., a fluid circuit containing proppant). High pressure fluid output 150 may be provided into formation 154 and then pumped from formation 154 by low pressure fluid pump 124 to create low pressure fluid input 120.

In some embodiments, the fluid treatment system 100B is used in completion operations in the oil and gas industry to perform hydraulic fracturing (e.g., hydraulic fracturing, fracturing) to increase the release of oil and gas in the formation 154. The high pressure output system 152 may include a formation 154 (e.g., a well). Hydraulic fracturing may include pumping a high pressure fluid 150 containing a combination of water, chemicals, and solid particulates (e.g., sand, ceramic, proppant) into a well (e.g., formation 154) at high pressure. The low pressure fluid inflow 120 and the high pressure fluid output 150 may include a particle laden fluid that increases the release of oil and gas in the formation 154 by propagating and increasing the size of the fracture 156 in the formation 154. The high pressure of high pressure fluid output 150 initiates and increases the size of fracture 156 and propagates through formation 154 to release more oil and gas, while solid particles (e.g., powders, fragments, etc.) enter fracture 156 to keep fracture 156 open (e.g., prevent fracture 156 from closing once high pressure fluid output 150 decompresses).

To pump such particulate laden fluid into formation 154 (e.g., a well), fluid treatment system 100B may include one or more high pressure fluid pumps 134 and one or more low pressure fluid pumps 124 coupled to hydraulic energy transfer system 110. . For example, the hydraulic energy transfer system 110 may be a hydraulic turbocharger or a pressure exchanger (e.g., a rotary pressure exchanger). In operation, the hydraulic energy transfer system 110 transfers pressure between a first fluid (e.g., high pressure fluid input 130, proppant-free fluid) pumped by the high pressure fluid pump 134 and a second fluid (e.g., low pressure fluid input 120, proppant-containing fluid or fracturing fluid) pumped by the low pressure fluid pump 124 without any substantial mixing therebetween. In this manner, hydraulic energy transfer system 110 prevents or limits wear on high pressure fluid pump 134 while enabling fluid treatment system 100B to pump high pressure fracturing fluid (e.g., high pressure fluid output 150) into formation 154 to release oil and gas. To operate in corrosive and abrasive environments, the hydraulic energy transfer system 110 may be made of a material that is resistant to the corrosive and abrasive substances in the first fluid or the second fluid. For example, the hydraulic energy transfer system 110 may be made of a ceramic (e.g., alumina, a cermet such as a carbide, oxide, nitride, or boride hard phase) in a metal matrix (e.g., co, cr, or Ni, or any combination thereof), such as CoCr, ni, niCr or tungsten carbide in a Co matrix.

In some embodiments, the hydraulic energy transfer system 110 includes a pressure exchanger (e.g., a rotary pressure exchanger), with a high pressure fluid input 130 (e.g., a first fluid, a high pressure solids-free fluid) entering a first side of the pressure exchanger, wherein the high pressure fluid input 130 contacts a low pressure fluid input 120 (e.g., a second fluid, a low pressure fracturing fluid) on a second side of the pressure exchanger. The contact between the fluids enables the high pressure fluid input 130 to increase the pressure of the second fluid (e.g., the low pressure fluid input 120), which outputs the second fluid of the pressure exchanger (e.g., the high pressure fluid output 150) and down the well (e.g., the formation 154) for a fracturing operation. The first fluid (e.g., low pressure fluid output 140) similarly exits the pressure exchanger, but is at a low pressure after exchanging pressure with the second fluid. As described above, the second fluid may be a low pressure fracturing fluid, which may include abrasive particles that may abrade the interface between the rotor and the respective end cap as the rotor rotates relative to the respective end cap.

FIG. 1C illustrates a schematic diagram of a fluid treatment system 100C including a hydraulic energy transfer system 110, according to some embodiments. The fluid treatment system 100C may be a desalination system (e.g., to remove salts and/or other minerals from water). In some embodiments, fluid treatment system 100C includes more components, fewer components, the same route, a different route, etc. than shown in fig. 1C.

The low pressure input system 122 may include a feed pump 126 (e.g., a low pressure fluid pump 124) that receives a seawater input 170 (e.g., feed water from a reservoir or directly from the ocean) and provides a low pressure fluid input 120 (e.g., low pressure seawater, feed water) to the hydraulic energy transfer system 110 (e.g., a pressure exchanger). The high pressure input system 132 may include a membrane 136, the membrane 136 providing a high pressure fluid input 130 (e.g., high pressure brine) to the hydraulic energy transfer system 110 (e.g., a pressure exchanger). The hydraulic energy transfer system 110 exchanges pressure between the high pressure fluid input 130 and the low pressure fluid input 120 to provide a high pressure fluid output 150 (e.g., high pressure seawater) to a high pressure output system 152 and a low pressure fluid output 140 (e.g., low pressure brine) to a low pressure output system 142 (e.g., geologic body, ocean, sea, waste, etc.).

The membrane 136 may be a membrane separation device configured to separate a fluid passing through a membrane, such as a reverse osmosis membrane. The membrane 136 may provide a high pressure fluid input 130 to the hydraulic energy transfer system 110 that is concentrated feed water or concentrate (e.g., brine). The pressure of the high pressure fluid input 130 may be used to compress low pressure feed water (e.g., low pressure fluid input 120) into high pressure feed water (e.g., high pressure fluid output 150). For simplicity and illustration, the term "feed water" is used. However, fluids other than water may be used in the hydraulic energy transfer system 110.

A circulation pump 158 (e.g., a centrifugal pump) provides a high pressure fluid output 150 (e.g., high pressure seawater) to the membrane 136. The membrane 136 filters the high pressure fluid output 150 to provide low pressure potable water 172 and a high pressure fluid input 130 (e.g., high pressure brine). The low pressure output system 142 provides a brine output 174 (e.g., to the geologic volume, ocean, sea, waste, etc.).

In some embodiments, high pressure fluid pump 176 is disposed between feed pump 126 and membrane 136. The high pressure fluid pump 176 increases the pressure of low pressure seawater (e.g., low pressure fluid input 120 providing high pressure feed water) that will mix with the high pressure seawater provided by the circulation pump 158.

In some embodiments, the use of hydraulic energy transfer system 110 reduces the load on high pressure fluid pump 176. In some embodiments, the fluid treatment system 100C provides low pressure potable water 172 without using a high pressure fluid pump 176. In some embodiments, the fluid treatment system 100C provides low pressure potable water 172 by intermittently using a high pressure fluid pump 176.

In some examples, the hydraulic energy transfer system 110 (e.g., a pressure exchanger) receives a low pressure fluid input 120 (e.g., low pressure feed water) of about 30 pounds Per Square Inch (PSI) and receives a high pressure fluid input 130 (e.g., high pressure brine or concentrate) of about 980 pounds per square inch. The hydraulic energy transfer system 110 (e.g., a pressure exchanger) transfers pressure from the high pressure concentrate (e.g., high pressure fluid input 130) to the low pressure feed water (e.g., low pressure fluid input 120). The hydraulic energy transfer system 110 (e.g., pressure exchanger) outputs a high pressure fluid output 150 (e.g., high pressure (compressed) feed water) at about 965 pounds per square inch and a low pressure fluid output 140 (e.g., low pressure concentrate) at about 15 pounds per square inch. Thus, the efficiency of the hydraulic energy transfer system 110 (e.g., pressure exchanger) may be about 97% because the input volume is about equal to the output volume of the hydraulic energy transfer system 110 (e.g., pressure exchanger), and 965 pounds per square inch is about 97% of 980 pounds per square inch.

FIG. 1D illustrates a schematic diagram of a fluid treatment system 100D including a hydraulic energy transfer system 110, according to some embodiments. Fluid treatment system 100D may be a refrigeration system. In some embodiments, fluid treatment system 100D includes more components, fewer components, the same route, a different route, etc. than shown in fig. 1D.

The hydraulic energy transfer system 110 (e.g., a pressure exchanger) may receive a low pressure fluid input 120 from a low pressure input system 122 (e.g., a low pressure lift 128, a low pressure fluid pump, etc.) and a high pressure fluid input 130 from a high pressure input system 132 (e.g., a condenser 138). The hydraulic energy transfer system 110 (e.g., a pressure exchanger) may exchange pressure between the low pressure fluid input 120 and the high pressure fluid input 130 to provide the high pressure fluid output 150 to the high pressure output system 152 (e.g., the high pressure lift 159) and the low pressure fluid output 140 to the low pressure output system 142 (e.g., the evaporator 144). The evaporator 144 may provide fluid to the compressor 178 and the low pressure lift device 128. The condenser 138 may receive fluid from a compressor 178 and a high pressure lift device 159.

The fluid treatment system 100D may be a closed system. The low pressure fluid input 120, the high pressure fluid input 130, the low pressure fluid output 140, and the high pressure fluid output 150 may all be fluids (e.g., refrigerants) circulating in the closed system of the fluid treatment system 100D.

In some embodiments, the fluid of fluid treatment system 100D may include solid particles. For example, pipes, equipment, connections (e.g., pipe welds), etc. may introduce solid particles (e.g., solid particles from welding) into the fluid in the fluid treatment system 100D. Solid particles in the fluid and/or high pressure of the fluid may cause wear and/or erosion of components (e.g., rotor, end caps) of the pressure exchanger of the hydraulic energy transfer system 110.

Fig. 2A-2E are exploded perspective views of a rotary pressure exchanger 40 (e.g., rotary pressure exchanger, rotary Liquid Piston Compressor (LPC)) in accordance with certain embodiments. The pressure exchanger 40 may include a motor 92 and/or a control module 94.

In some embodiments, pressure exchanger 40 includes one or more features described in one or more of fig. 3A-7B. In some embodiments, the pressure exchanger includes a rotor configured to receive a first fluid, to receive a second fluid, and to exchange pressure between the first fluid and the second fluid. The first fluid and/or the second fluid enters the rotor non-axially and/or exits the rotor non-axially.

The pressure exchanger 40 is configured to transfer pressure and/or work between a first fluid (e.g., proppant-free fluid or supercritical carbon dioxide, high pressure fluid input 130) and a second fluid (e.g., fracturing fluid or superheated gaseous carbon dioxide, low pressure fluid input 120) with minimal fluid mixing. The rotary pressure exchanger 40 may include a generally cylindrical body portion 42 including a sleeve 44 (e.g., a rotor sleeve) and a rotor 46. The rotary pressure exchanger 40 may also include two end caps 48 and 50, which include manifolds 52 and 54, respectively. Manifold 52 includes respective inlet and outlet ports 56, 58, while manifold 54 includes respective inlet and outlet ports 60, 62. In operation, these inlet ports 56, 60 enable the first and second fluids to enter the rotary pressure exchanger 40 to exchange pressure, while the outlet ports 58, 62 enable the first and second fluids to subsequently exit the rotary pressure exchanger 40. In operation, the inlet port 56 may receive a high pressure first fluid (e.g., the high pressure fluid input 130) and, after exchanging pressure, the outlet port 58 may be used to direct a low pressure first fluid (e.g., the low pressure fluid output 140) out of the rotary pressure exchanger 40. Similarly, the inlet port 60 may receive a second fluid at a low pressure (low pressure fluid input 120) and the outlet port 62 may be used to direct a second fluid at a high pressure (e.g., high pressure fluid output 150) out of the rotary pressure exchanger 40. The end caps 48, 50 include respective end caps 64, 66 (e.g., end plates) disposed within the respective manifolds 52, 54 that enable fluid-tight contact with the rotor 46.

As described above, one or more components of pressure exchanger 40, such as rotor 46, end cover 64, and/or end cover 66, may be constructed of a wear resistant material (e.g., carbide, cemented carbide, silicon carbide, tungsten carbide, etc.) having a hardness greater than a predetermined threshold (e.g., a vickers hardness value of at least 1000, 1250, 1500, 1750, 2000, 2250, or higher). For example, tungsten carbide may be more durable than other materials such as alumina ceramics, and may provide improved wear resistance to abrasive fluids.

The rotor 46 may be cylindrical and may be disposed within the sleeve 44, which enables the rotor 46 to rotate about the axis 68. The rotor 46 may have a plurality of channels 70 (e.g., tubes, rotor ducts) extending substantially longitudinally through the rotor 46, the plurality of channels having openings 72 and 74 (e.g., rotor ports) at each end symmetrically arranged about the longitudinal axis 68. Openings 72 and 74 of rotor 46 are disposed in hydraulic communication with inlet and outlet ports 76 and 78 (e.g., end cap inlet and outlet ports) and inlet and outlet ports 80 and 82 (e.g., end cap inlet and outlet ports) in end caps 64, 66 such that channel 70 is exposed to fluid under high pressure and fluid under low pressure during rotation. As shown, the inlet and outlet orifices 76, 78 and the inlet and outlet orifices 80, 82 may be designed in the form of circular arcs or segments of circles (e.g., C-shapes).

In some embodiments, a controller using sensor feedback (e.g., revolutions per minute measured by a tachometer or optical encoder or volumetric flow measured by a flow meter) may control the degree of mixing between the first fluid and the second fluid in the rotary pressure exchanger 40, which may be used to improve the operability of a fluid treatment system (e.g., the fluid treatment systems 100A-100D of fig. 1A-1D). For example, varying the volumetric flow rates of the first fluid and the second fluid entering the rotary pressure exchanger 40 allows an equipment operator (e.g., a system operator) to control the amount of fluid mixed within the pressure exchanger 40. In addition, varying the rotational speed of rotor 46 also allows the operator to control the mixing. Three features of the rotary pressure exchanger 40 that affect mixing are (1) the aspect ratio of the rotor channel 70, (2) the duration of exposure between the first fluid and the second fluid, and (3) the formation of a fluid barrier (e.g., interface) between the first fluid and the second fluid within the rotor channel 70. First, the rotor channels 70 (e.g., pipes) are typically long and narrow, which stabilizes the flow within the rotary pressure exchanger 40. Further, the first fluid and the second fluid may move through the channel 70 in a plug flow state with minimal axial mixing. Second, in certain embodiments, the speed of the rotor 46 reduces the contact between the first fluid and the second fluid. For example, the speed of the rotor 46 (e.g., a rotor speed of about 1200 Revolutions Per Minute (RPM)) may reduce the contact time between the first fluid and the second fluid to less than about 0.15 seconds, 0.10 seconds, or 0.05 seconds. Third, a small portion of the rotor channel 70 is used for pressure exchange between the first fluid and the second fluid. Thus, a volume of fluid remains in the channel 70 to act as a barrier between the first fluid and the second fluid. All of these mechanisms may limit mixing within the rotary pressure exchanger 40. Furthermore, in some embodiments, the rotary pressure exchanger 40 may be designed to operate with an internal piston or other barrier that fully or partially isolates the first fluid from the second fluid while achieving pressure transfer.

Fig. 2B-2E are exploded views of an embodiment of the rotary pressure exchanger 40, showing the sequence of positions of the individual rotor channels 70 in the complete cycle rotor 46 as the channels 70 rotate. Note that fig. 2B to 2E are simplified diagrams of the rotary pressure exchanger 40 showing one rotor channel 70, and the channel 70 is shown as having a circular cross-sectional shape. In other embodiments, the rotary pressure exchanger 40 may include multiple channels 70 having the same or different cross-sectional shapes (e.g., circular, oval, square, rectangular, polygonal, etc.). Thus, fig. 2B-2E are simplified for illustrative purposes, and other embodiments of the rotary pressure exchanger 40 may have different configurations than those shown in fig. 2A-2E. As described in detail below, the rotary pressure exchanger 40 facilitates pressure exchange between the first fluid and the second fluid by bringing the first fluid and the second fluid into brief contact with each other within the rotor 46. In certain embodiments, the exchange occurs at a rotational speed that results in limited mixing of the first fluid with the second fluid. The speed of the pressure wave through the rotor channels 70 (once the channels are exposed to the orifices 76), the diffusion speed of the fluid, and/or the rotational speed of the rotor 46 may determine whether any mixing occurs and the degree of mixing.

Fig. 2B is a split view of an embodiment of a rotary pressure exchanger 40 (e.g., a rotary liquid piston compressor) according to some embodiments. In fig. 2B, the channel opening 72 is in a first position. In this first position, the channel opening 72 is in fluid communication with the aperture 78 in the end cap 64, and thus the manifold 52, while the opposite channel opening 74 is in fluid communication with the aperture 82 in the end cap 66, and through the extension, with the manifold 54. As will be discussed below, the rotor 46 may rotate in a clockwise direction indicated by arrow 84. In operation, low pressure second fluid 86 passes through end cap 66 and into channel 70 where low pressure second fluid 86 contacts first fluid 88 at dynamic fluid interface 90. Second fluid 86 then drives first fluid 88 out of channel 70, through end cap 64, and out of rotary pressure exchanger 40. However, due to the short duration of contact, mixing between the second fluid 86 and the first fluid 88 is minimal.

Fig. 2C is an exploded perspective view of an embodiment of a rotary pressure exchanger 40 (e.g., a rotary liquid piston compressor) according to some embodiments. In fig. 2C, the channel 70 has rotated clockwise through an arc of about 90 degrees. In this position, the opening 74 (e.g., outlet) is no longer in fluid communication with the apertures 80 and 82 of the end cap 66, and the opening 72 is no longer in fluid communication with the apertures 76 and 78 of the end cap 64. Thus, the low pressure second fluid 86 is temporarily contained within the channel 70.

Fig. 2D is an exploded perspective view of an embodiment of a rotary pressure exchanger 40 (e.g., a rotary liquid piston compressor) according to some embodiments. In fig. 2D, the channel 70 has been rotated through an arc of about 60 degrees from the position shown in fig. 2B. The opening 74 is now in fluid communication with the aperture 80 in the end cap 66, while the opening 72 of the channel 70 is now in fluid communication with the aperture 76 of the end cap 64. In this position, high pressure first fluid 88 enters and low pressure second fluid 86 is pressurized, driving second fluid 86 out of rotor channel 70 and through orifice 80.

Fig. 2E is an exploded perspective view of an embodiment of a rotary pressure exchanger 40 (e.g., a rotary liquid piston compressor) according to some embodiments. In fig. 2E, the channel 70 has been rotated through an arc of approximately 270 degrees from the position shown in fig. 2B. In this position, opening 74 is no longer in fluid communication with apertures 80 and 82 of end cap 66, and opening 72 is no longer in fluid communication with apertures 76 and 78 of end cap 64. Thus, the first fluid 88 is no longer pressurized and is temporarily contained within the channel 70 until the rotor 46 is rotated approximately 90 degrees again, and the cycle begins again.

When suspended solids are introduced and mixed in the fluid entering the pressure exchanger, wear and/or erosion damage to the pressure exchanger may occur. Wear damage may occur when particles enter the gap in the pressure exchanger (e.g., become trapped between the stationary end cap and the rotor). Erosion damage may occur due to the presence of suspended solids (e.g., aggressive agents) in the high velocity fluid jet (e.g., slurry jet) created by the high pressure differential inside the pressure exchanger. When the high velocity jet impinges on components of the pressure exchanger, the high velocity jet can cause damage to those components. Damage (e.g., erosion damage) may occur when a high pressure rotor port (e.g., rotor tube) opens to a low pressure end cap port (e.g., kidney) or a low pressure rotor port (e.g., rotor tube) opens to a high pressure end cap port (e.g., kidney), resulting in a high pressure differential.

Fig. 3A-7B illustrate components of a pressure exchanger according to some embodiments. The pressure exchanger of the present disclosure may include features of one or more of fig. 3C-7B. The pressure exchanger of the present disclosure may have the characteristic that fluid enters the rotor of the pressure exchanger non-axially and/or fluid exits the rotor of the pressure exchanger non-axially. In some embodiments, the pressure exchanger includes a rotor configured to receive a first fluid, to receive a second fluid, and to exchange pressure between the first fluid and the second fluid. The first fluid and/or the second fluid enters the rotor non-axially and/or exits the rotor non-axially.

The present disclosure may address issues of axial contact (e.g., friction, wear, etc.) between the rotor and the end cover of a pressure exchanger that may occur (e.g., occur primarily) due to an axial gap (e.g., a very tight axial gap, an axial gap of about 10 to 25 microns) between the rotor and the end cover. Closure of the axial gap results in contact that may be attributable to one or both of deformation of the end caps due to pressure, and/or thrust loads (e.g., excessive thrust loads) on the rotor exceeding the capabilities of existing thrust bearings. The axial gap of the loading side may be about 5 to 10 microns. The axial clearance of the unloading side should be kept to a minimum (about 20 microns) to minimize leakage that may be excessive at high pressures.

Fig. 3A-3C illustrate components of a pressure exchanger according to some embodiments. Fig. 3A illustrates a perspective view of an assembly of a pressure exchanger (e.g., a pressure exchanger having a radial inlet, a substantially straight tube, and a post-flow path design), fig. 3B illustrates a cross-sectional view of an assembly of a pressure exchanger (e.g., a pressure exchanger having a radial inlet, a substantially straight tube, and a post-flow path design), and fig. 3C illustrates a top or bottom view of a rotor of a pressure exchanger according to some embodiments. In some embodiments, two or more of fig. 3A-3C illustrate views of components of the same pressure exchanger (e.g., pressure exchanger 300). In some embodiments, two or more of fig. 3A-3C illustrate views of an assembly of different pressure exchangers. In some embodiments, the pressure exchanger of fig. 3A-3C may have two pressure exchange cycles per rotor revolution (e.g., pressurizing and depressurizing each rotor conduit twice per revolution) to balance radial loads (e.g., radial thrust) on rotor 310. 3A-3B may have a single cycle per revolution (e.g., pressurization and depressurization per rotor duct per revolution). For example, each complete revolution (e.g., 360 degree revolution) of the rotor completes one complete pressure exchange cycle. In a single rotation, the rotor may facilitate the process of transferring pressure from the high pressure fluid to the low pressure fluid. This may include drawing high pressure fluid into the rotor, transferring pressure to low pressure fluid, and releasing low pressure fluid, now at a different (higher) pressure.

The single cycle high pressure ports (high pressure input and high pressure output formed by the sleeve) and low pressure ports (low pressure input and low pressure output formed by the center post) may be approximately 180 degrees apart in the clock direction (clocked) (e.g., the high pressure ports are positioned directly opposite each other on the surface of the cylindrical sleeve and the low pressure ports are positioned directly opposite each other on the surface of the cylindrical center post, respectively). To achieve dual cycle operation, two additional ports may be formed in the sleeve substantially 180 degrees apart from each other and substantially 90 degrees apart from the single high and low pressure ports. Further, two additional ports are formed from the center column substantially 180 degrees apart from each other and substantially 90 degrees apart from the single high and low pressure ports.

An advantage of fig. 3A-3B may be that the sealing area between high pressure input port 381 and low pressure output port 371, and between low pressure input port 361 and high pressure output port 391 is larger to provide lower leakage. In some embodiments, the pressure exchanger of fig. 3A-3B may be used for lower pressure applications, such as brackish water desalination, wastewater treatment applications (e.g., municipal water), and the like.

Fig. 3A illustrates a pressure exchanger 300 having radial inlets (e.g., via high pressure input port 381, high pressure output port 391, low pressure input port 361, and/or low pressure output port 371), a substantially straight tube 311, and a post-flow path design (e.g., via column 330) according to some embodiments.

In some embodiments, pressure exchanger 300 may include a rotor 310 configured to receive a first fluid, to receive a second fluid, and to exchange pressure between the first fluid and the second fluid. In some embodiments, pressure exchanger 300 may include a sleeve 320, which may be disposed about rotor 310. In some embodiments, the first fluid enters rotor 310 radially through sleeve 320 (e.g., in the direction of arrow 302, enters the rotor from an outside surface of the rotor via high pressure input port 381, etc.). In some embodiments, the second fluid enters rotor 310 radially (e.g., in the direction of arrow 302, enters the rotor from an inside surface of the rotor via low pressure input port 361, etc.). In some embodiments, the fluid enters the rotor radially rather than axially. In some embodiments, the pressure exchanger 300 may include a post 330 disposed inside the rotor. In some embodiments, the post 330 forms a post cavity 350.

Fig. 3B shows a cross-sectional view of a pressure exchanger 300 having radial rotor inlet and outlet (e.g., via high pressure input port 381, high pressure output port 391, low pressure input port 361, and/or low pressure output port 371), substantially straight tube 311, and a post-flow path (e.g., through column 330) design.

In some embodiments, the pressure exchanger 300 may be substantially cylindrical. In some embodiments, the radial direction may be a direction substantially perpendicular to the central axis 309 of the pressure exchanger 300. For example, arrow 302 shows a radial direction relative to a central axis 309 of the pressure exchanger 300. In some embodiments, the axial direction may be a direction substantially parallel to the central axis 309 of the pressure exchanger 300. For example, arrow 301 shows an axial direction relative to a central axis 309 of the pressure exchanger 300.

In some embodiments, the second fluid enters rotor 310 radially via post 330.

In some embodiments, the post 330 forms a first low pressure input port 361 and a first low pressure output port 371.

In some embodiments, sleeve 320 forms a first high pressure input port 381 and a first high pressure output port 391.

Or in some embodiments, the post 330 may form a first high pressure input port and a first high pressure output port. The sleeve 320 may form a first low pressure input port and a first low pressure output port.

Fig. 3C illustrates rotor 310 of pressure exchanger 300, according to some embodiments.

In some embodiments, the rotor is the same as or substantially similar to rotor 310 of fig. 3A and/or 3B.

In some embodiments, pressure exchanger 300 includes a rotor 310 configured to exchange pressure between a first fluid and a second fluid, the rotor forming a rotor cavity 360.

In some embodiments, the rotor includes an outer surface 322, wherein the first fluid enters the rotor 310 radially via the outer surface 322. In some embodiments, rotor 310 includes an inside surface 324 forming rotor cavity 360, wherein the second fluid radially enters rotor 310 via inside surface 324.

In some embodiments, the pressure exchanger 300 further includes a post 330 (see, e.g., fig. 3A and/or 3B) disposed in the rotor cavity 360, the post 330 forming a post cavity 350. In some embodiments, the second fluid enters column cavity 350 axially and exits column cavity 350 radially to enter rotor 310 radially.

In some embodiments, rotor 310 forms a conduit 311, wherein at least one of the first fluid or the second fluid radially enters rotor 310 into at least one conduit 311. In some embodiments, the conduit 311 may be external Zhou Caowen.

Fig. 4A-4C illustrate components of a pressure exchanger according to some embodiments. In some embodiments, fig. 4A-C illustrate a pressure exchanger having a flow path design with radial inlets (e.g., via high pressure input ports 481 and 482, high pressure output ports 491 and 492, low pressure input ports 461 and 462, and/or low pressure output ports 471 and 472), a substantially straight tube 411, and a central bore (e.g., via central bore 450).

Fig. 4B-4C illustrate cross-sectional views of embodiments of the present disclosure. In some embodiments, the central bore 450 (e.g., formed by a post) serves as a fluid path. This is accomplished by using a center post 430 having a fluid path as shown in fig. 4A-4C. Fluid enters the pressure exchanger 400 radially (through the sleeve 420 outside the cartridge and through the center post 430 inside the rotor 410) and makes a substantially 90 degree turn into the rotor 410. The low pressure fluid is shown in the central bore 450 and the high pressure fluid is external. In some embodiments, the high and low voltage regions may be switched. The high pressure ports (e.g., 481 to 482 and 491 to 492) in the sleeve 420 and the low pressure ports (e.g., 461 to 462 and 471 to 472) in the rotor 410 are substantially 90 degrees apart from each other in the clock direction (e.g., the high pressure ports and the low pressure ports are positioned substantially 90 degrees apart from each other on the surface of the cylindrical sleeve 420 or the center post 430) to seal the high pressure region and the low pressure region and prevent direct communication or excessive leakage between the high pressure ports and the low pressure ports. In some embodiments, the angular spacing of the ports is equal to or greater than the angular spacing of the conduits.

Having two low pressure ports (see, e.g., fig. 4B) approximately 180 degrees apart and two high pressure ports (see, e.g., fig. 4C) approximately 180 degrees apart helps balance the radial load on rotor 410. The use of the center column 430 as a flow path in the radial inlet pressure exchanger 400 has the advantage of simplifying the housing design and maintaining an external design similar to other pressure exchangers.

Fig. 4A illustrates a pressure exchanger 400 having a radial inlet, substantially straight tube, and post-flow path design, according to some embodiments.

In some embodiments, pressure exchanger 400 may include a rotor 410 configured to receive a first fluid, to receive a second fluid, and to exchange pressure between the first fluid and the second fluid. In some embodiments, pressure exchanger 400 may include a sleeve 420, which may be disposed about rotor 410. In some embodiments, the first fluid enters rotor 410 radially (e.g., in the direction of arrow 402) through sleeve 420. In some embodiments, the fluid enters the rotor radially rather than axially. In some embodiments, the pressure exchanger 400 may include a column 430 disposed inside the rotor. In some embodiments, the post 430 fills the rotor central bore.

Fig. 4B-4C show cross-sectional views of a pressure exchanger 400 having a radial inlet, a substantially straight tube, and a post-flow path design. In some embodiments, fig. 4B-4C illustrate the same pressure exchanger 400.

In some embodiments, the pressure exchanger 400 may be substantially cylindrical. In some embodiments, the radial direction may be a direction substantially perpendicular to the central axis 405 of the pressure exchanger 400. For example, arrow 402 illustrates a radial direction relative to a central axis 405 of the pressure exchanger 400. In some embodiments, the axial direction may be a direction substantially parallel to the central axis 405 of the pressure exchanger 400. For example, arrow 401 shows an axial direction relative to a central axis 405 of the pressure exchanger 400.

In some embodiments, the second fluid enters rotor 410 radially via post 430.

In some embodiments, the column 430 forms a first low pressure input port 461 and a first low pressure output port 471. In some embodiments, the column 430 also forms a second low pressure input port 462 and a second low pressure output port 472.

In some embodiments, the sleeve 420 forms a first high pressure input port 481 and a first high pressure output port 491. In some embodiments, sleeve 420 forms a second high pressure input port 482 and a second high pressure output port 492.

Or in some embodiments, the column 430 may form a first high pressure input port and a first high pressure output port. The column 430 may also form a second high pressure input port and a second high pressure output port. The sleeve 420 may form a first low pressure input port and a first low pressure output port. The sleeve 420 may also form a second low pressure input port and a second low pressure output port.

In some embodiments, pressure exchanger 400 may include a rotor 410 (e.g., see fig. 4A-B) forming a radial conduit, wherein rotor 410 is configured to receive a first fluid, to receive a second fluid, and to exchange pressure between the first fluid and the second fluid. In some embodiments, pressure exchanger 400 includes a post 430 disposed in a rotor cavity formed by rotor 410, wherein a first fluid enters rotor 410 radially via a first radial conduit of the radial conduits, enters a second radial conduit of the radial conduits through a post cavity (e.g., central bore 450) formed by post 430, and exits rotor 410 radially via the second radial conduit.

In some embodiments, the pressure exchanger 400 further includes a first pair of ports formed by the sleeve 420 or the post 430. Sleeve 420 is disposed about rotor 410 and post 430 is disposed in the rotor cavity. In some embodiments, the first pair of ports includes a low pressure input port and a low pressure output port. In some embodiments, the first pair of ports may include a high voltage input port and a high voltage output port.

In some embodiments, the pressure exchanger 400 further includes a second pair of ports formed by the sleeve 420 or the post 430. In some embodiments, the second pair of ports includes a high voltage input port and a high voltage output port. In some embodiments, the second pair of ports includes a low pressure input port and a low pressure output port.

In some embodiments, the pressure exchanger 400 may include a third pair of ports formed by the sleeve 420 or the post 430. In some embodiments, the third pair of ports includes a low pressure input port and a low pressure output port. In some embodiments, the third pair of ports includes a high voltage input port and a high voltage output port.

In some embodiments, the pressure exchanger 400 may include a fourth pair of ports formed by the sleeve 420 or the post 430. In some embodiments, the fourth pair of ports includes a low pressure input port and a low pressure output port. In some embodiments, the fourth pair of ports includes a high voltage input port and a high voltage output port.

In some embodiments, the third pair of ports formed by the post 430 is disposed substantially 180 degrees apart from the fourth pair of ports formed by the post 430 and substantially 90 degrees apart from the first and second pairs of ports formed by the sleeve 420. In some embodiments, the first pair of ports formed by the sleeve 420 and the second pair of ports formed by the post 430 are disposed substantially 180 degrees apart from each other on the sleeve 420.

In some embodiments, rotor 410 may be configured to rotate about axis of rotation 405. In some embodiments, the sleeve 420 may form an angled port (e.g., the angled port 615 in fig. 6A-6B) disposed about a port axis. In some embodiments, the port axis does not intersect the rotation axis 405. For a more detailed description, please refer to fig. 6A-6B.

In some embodiments, rotor 410 may be configured to rotate about axis of rotation 405. In some embodiments, the post 430 forms an angled port disposed about a port axis. In some embodiments, the port axis does not intersect the rotation axis 405 (see, e.g., fig. 6A-6B and corresponding description).

Fig. 4D-4F illustrate components of a pressure exchanger according to some embodiments. Fig. 4D-4F illustrate a pressure exchanger 400 having a spiral design with an outer Zhou Caowen (e.g., instead of a 90 degree turn in rotor 410). The helical channels forming the outer Zhou Caowen may refer to the channels formed by the rotor surface. The surface of the rotor may form substantially parallel helical grooves or channels (forming the outer Zhou Caowen channels). The outer Zhou Caowen tube may be helical along the length of the rotor. The outer Zhou Caowen channels may have a uniform shape and depth, forming a uniform pattern on the rotor surface. In some embodiments, the helical tubing in outer Zhou Caowen may be covered by a sleeve that wraps around the rotor, thereby closing the tubing in outer Zhou Caowen. This may increase the fluid path inside the rotor and provide a more streamlined flow compared to a straight tube design. For the same size housing, the solid sections of the rotor may be subjected to higher stresses due to bending loads not present in a straight tube design, and thus the pressure may need to be reduced. One application may be where the pressure is lower but mixing may be a greater problem. In some embodiments, outer Zhou Caowen is any shape that increases the length of the conduit. For example, the peripheral flutes may be partially helical, serpentine (serpentine), partially serpentine, zigzag, partially zigzag, etc. (e.g., based on the application of the pressure exchanger).

Fig. 4D shows a pressure exchanger 400 with radial inlet, external Zhou Caowen tubing and spiral flow path design.

In some embodiments, pressure exchanger 400 may include a rotor 410 configured to receive a first fluid, to receive a second fluid, and to exchange pressure between the first fluid and the second fluid. In some embodiments, pressure exchanger 400 may include a sleeve 420, which may be disposed about rotor 410. In some embodiments, the first fluid enters rotor 410 radially (e.g., in the direction of arrow 402) through sleeve 420. In some embodiments, the fluid enters the rotor radially rather than axially. In some embodiments, the pressure exchanger 400 may include a column 430 disposed inside the rotor. In some embodiments, the post 430 forms a central aperture 450. The central bore 450 may be a hollow channel extending axially within the post 430. In some embodiments, the central bore 450 is a cylindrical bore in the center of the rotor 410 that extends the entire length of the rotor 410. The post 430 is a fixed member disposed in the central hole 450 with a certain gap. The post 430 may form two cavities at either end. For example, in some embodiments, the first chamber forms a low pressure input plenum and the second chamber forms a low pressure output plenum. In some embodiments, the first chamber forms a high pressure input plenum and the second chamber forms a high pressure output plenum.

In some embodiments, rotor 410 of pressure exchanger 400 forms conduit 411, and at least one of the first fluid or the second fluid will enter rotor 410 radially via conduit 411. In some embodiments, conduit 411 is external Zhou Caowen.

In some embodiments, the outer Zhou Caowen channels 411 may be formed by the rotor 410 (e.g., grooves or channels on the outer surface of the rotor). The outer Zhou Caowen channels 411 may vary in depth, width and shape. The outer Zhou Caowen conduit 411 may be a passageway (conduit) for controlling fluid or gas flow, improving heat transfer and improving pressure exchange efficiency. In some embodiments, sleeve 420 (e.g., disposed about rotor 410) may seal outer Zhou Caowen (e.g., to contain fluid). Sleeve 420 may be a cylindrical housing enclosing rotor 410 and covering tubing 411 into outer Zhou Caowen. This seal ensures that the fluid or gas within the outer Zhou Caowen conduit 411 is contained and directed in the desired flow pattern, preventing any accidental leakage or mixing.

In some embodiments, outer Zhou Caowen of outer Zhou Caowen's tubing 411 refers to a single groove or channel (e.g., formed by the tubing of outer Zhou Caowen) on the outer surface of rotor 410. In some embodiments, the peripheral flutes may be concave features on the surface of the rotor 410. The outer Zhou Caowen may vary in depth, width, and shape, and may be a passageway (conduit) for fluid or gas to flow. In some embodiments, outer Zhou Caowen is a channel or groove formed by a pipe that is outer Zhou Caowen (e.g., pipe 411 that is outer Zhou Caowen).

In some embodiments, fig. 4E-4F show cross-sectional views of a pressure exchanger 400 having a radial inlet, an outer Zhou Caowen pipe, and a spiral flow path design.

In some embodiments, the outer Zhou Caowen of the conduit 411 leads to at least one of a sleeve 420 or a post 430 disposed about the rotor 410. In some embodiments, conduit 411 spans rotor 410, beginning at a first distal end 431 proximate rotor 410 and ending at a second distal end 432 proximate rotor 410. In some embodiments, conduit 411 is configured to pass through rotor 410 in a helical trajectory.

Fig. 4G illustrates components of a pressure exchanger 400 according to some embodiments. Fig. 4G shows a pressure exchanger that may not use a central bore for flow. All flow may enter and leave the sleeve 420. Fig. 4G shows a design version of the rotor outer Zhou Caowen. In some embodiments, fig. 4G may use straight tubes in the rotors shown in fig. 4A-4C. Fig. 4G may omit the use of a center post (e.g., as may be desired or needed in certain applications).

In some embodiments, the pressure exchanger of fig. 4A-4C may have straight tubes as slots on the rotor Outer Diameter (OD), leading to the sleeve Inner Diameter (ID). The conduit may also be on the inside diameter of the rotor leading to the outside diameter of the column. A benefit may be that it may be optional to not use end caps on the rotor (see, e.g., fig. 6A-6B). In some embodiments, the conduits are angled rather than vertical.

Fig. 5A-5B illustrate components of a pressure exchanger according to some embodiments. Fig. 5A-5B illustrate a pressure exchanger 500 having a rotor with radial ducts. The low pressure input fluid enters through the (outer diameter) OD sleeve and exits the OD sleeve as a high pressure output. The high pressure input fluid enters the rotor duct through the center post as a high pressure input and exits through the center post as a low pressure output after transmitting its pressure energy. In some embodiments, an advantage of this embodiment is that the high pressure output fluid may attain a pressure boost due to the centrifugal head applied by the rotor. Multiple rows of tubes may be arranged along the axis of the rotor to increase the flow of the pressure exchanger.

In some embodiments, pressure exchanger 500 includes a rotor 510 forming a radial conduit 511, wherein rotor 510 is configured to receive a first fluid, to receive a second fluid, and to exchange pressure between the first fluid and the second fluid. In some embodiments, the pressure exchanger 500 includes a column 530 disposed in a rotor cavity formed by the rotor 510, wherein a first fluid enters the rotor 510 radially via a first port 541 in a first pair of ports formed through a sleeve 520 or column 530 disposed about the rotor 510, enters one of the radial conduits 511, and exits the rotor 510 radially via a second port 552 in the first pair of ports. In some embodiments, the first pair of ports includes a high voltage input port 551 and a low voltage output port 542. In some embodiments, the radial direction is represented by arrow 502. Fluid entering the rotor radially may enter, for example, in the direction of arrow 502.

In some embodiments, pressure exchanger 500 further includes a second pair of ports formed by sleeve 520 or post 530. A sleeve 520 is disposed about the rotor 510 and a post 530 is disposed within the post cavity 550. In some embodiments, the second pair of ports includes a low voltage input port 541 and a high voltage output port 552. In some embodiments, the first pair of ports may include a high pressure input port 551 and a low pressure output port 542.

In some embodiments, pressure exchanger 500 may include a third pair of ports formed by sleeve 520 or post 530. In some embodiments, the third pair of ports includes a low voltage input port 561 and a high voltage output port 572. In some embodiments, the third pair of ports includes a high pressure input port 571 and a low pressure output port 562.

In some embodiments, the pressure exchanger 500 may include a fourth pair of ports formed by the sleeve 520 or the post 530. In some embodiments, the fourth pair of ports includes a high pressure input port 551 and a low pressure output port 562. In some embodiments, the fourth pair of ports includes a low voltage input port 561 and a high voltage output port 572.

In some embodiments, the third pair of ports formed by the post 530 is disposed approximately 180 degrees from the second pair of ports formed by the post 530. The third pair of ports formed by post 530 are disposed approximately 180 degrees from the first pair of ports disposed on the sleeve. The third pair of ports formed by post 530 and the fourth pair of ports formed by sleeve 520 are disposed at substantially 0 degrees to each other on post 530 and sleeve 520, respectively. In some embodiments, the first pair of ports formed by sleeve 520 and the second pair of ports formed by post 530 are disposed substantially 0 degrees from each other on sleeve 520 and post, respectively.

In some embodiments, rotor 510 may be configured to rotate about axis of rotation 505. In some embodiments, sleeve 520 may form an angled port (e.g., angled port 615 in fig. 6A-6B) disposed about a port axis. In some embodiments, the port axis does not intersect the rotation axis 505. For a more detailed description, please refer to fig. 6A-6B.

In some embodiments, rotor 510 may be configured to rotate about axis of rotation 505. In some embodiments, the post 530 forms an angled port disposed about a port axis. In some embodiments, the port axis does not intersect the rotation axis 405 (see, e.g., fig. 6A-6B and corresponding description).

Fig. 6A-6B illustrate components of a pressure exchanger according to some embodiments. Fig. 6A-6B may illustrate components of a pressure exchanger 600 for generating torque on a rotor to begin rotation and maintain that rotation. To generate torque on the rotor to rotate the rotor and exchange pressure (e.g., to act as a pressure exchanger), may include letting fluid in and out at an angle relative to the radial direction. In fig. 6A-6B, there may be a single cycle per revolution of the pressure exchanger (e.g., in fig. 3A-3B), and/or may be applied to other embodiments of the present disclosure. To better control the RPM of the rotor and minimize inlet losses, adjustable vanes may be incorporated on the ports (on the sleeve) through which fluid enters the rotor. In some embodiments, the adjustable vane may be an insert mounted in the port and adjusted based on the flow rate of the application. The adjustable vanes may also be incorporated into the sleeve ports and actuated mechanically, electrically, or hydraulically (e.g., if the flow rate varies substantially over time). The adjustable vane may be part of another component upstream of the sleeve port. The adjustable vane may be included at a high pressure input port within the center post.

In some embodiments, the pressure exchanger 600 may include a rotor 610 configured to receive a first fluid, to receive a second fluid, and to exchange pressure between the first fluid and the second fluid. In some embodiments, the pressure exchanger 600 may include a sleeve 620, which may be disposed about the rotor 610. In some embodiments, the first fluid enters the rotor 610 radially (e.g., in the direction of arrow 602) through the sleeve 620. In some embodiments, the fluid enters the rotor radially rather than axially. In some embodiments, the pressure exchanger 600 may include a post 630 disposed inside the rotor.

In some embodiments, the rotor 610 may be configured to rotate about the axis of rotation 605. In some embodiments, the sleeve 620 may form an angled port 615 disposed about the port axis 606. In some embodiments, the port axis 606 does not intersect the rotation axis 605.

In some embodiments, the rotor 610 may be configured to rotate about the axis of rotation 605. In fig. 6B, the rotation axis 605 is shown as a circle with a point in between. This representation shows that the rotation axis 605 extends in a direction perpendicular to the 2D plane of the drawing. In some embodiments, the post 630 forms an angled port 615 disposed about the port axis 606. In some embodiments, the port axis 606 does not intersect the rotation axis 605. In some embodiments, this configuration allows fluid to enter the rotor 610 at an angle that aids in the rotation of the rotor 610.

Fig. 7A-7B relate to a pressure exchanger, according to some embodiments. Fig. 7A to 7B may illustrate the layout of the pressure exchanger of the cartridge included in the housing 701. In some embodiments, radial bearings 709 may be used to seal the high and low pressure fluids. Providing bearings on the post and sleeve may provide a higher margin in terms of acceptable radial loading. Fig. 7A-7B also illustrate an axial bearing 708. Unlike conventional systems, these axial bearings may not act as seals and may not have as tight tolerances and small clearances as conventional systems. Fig. 7A illustrates the use of a split insert 712 to force fluid flow in a particular direction (e.g., clockwise in fig. 7A) to help provide torque to the rotor.

To achieve high pressure and low leakage, conventional systems may use very small margins of error in manufacturing tolerances and inspection. There is always a risk that at higher pressures, contact between the rotor and the end cap may occur due to high thrust forces and/or end cap deflection, resulting in a stalled rotor. The present disclosure aims to eliminate or alleviate this problem. The radial sealing surfaces of the present disclosure allow for axial clearance (e.g., a larger axial clearance) preventing the end cover and rotor from contacting each other. Any residual thrust load may be borne by the bearing system (e.g., independent of tight clearances). Furthermore, the radial bearing surfaces (male rotor and female sleeve) can better handle unexpected operating loads that a pressure exchanger such as vibration may encounter in the field, as compared to conventional systems.

In some embodiments of the present disclosure (e.g., fig. 4A-4F, 3A-7B), the radial load of the pressure exchanger may be balanced. In some embodiments, the radial load of the present disclosure may be higher compared to conventional systems. In some embodiments, the flow rate may be higher (e.g., for the same rotor and sleeve size envelope) than conventional systems. In some embodiments, one or more components of the pressure exchanger may be produced using complex machining processes (e.g., components comprising the spiral outer Zhou Caowen).

The present disclosure (e.g., one or more embodiments of fig. 3A-7B) may be improved over conventional solutions in terms of pressure range, efficiency, volume, and cost reduction.

The foregoing description sets forth numerous specific details, such as examples of specific systems, components, methods, etc., in order to provide a good understanding of several embodiments of the present disclosure. It will be apparent, however, to one skilled in the art that at least some embodiments of the present disclosure may be practiced without these specific details. In other instances, well-known components or methods have not been described in detail or presented in simple block diagram format in order to avoid unnecessarily obscuring the present disclosure. Therefore, the specific details set forth are merely exemplary. The specific embodiments may vary from these exemplary details and still be contemplated to be within the scope of the present disclosure. The description of the system herein may include a description of one or more optional components. The components may be included in combinations not specifically discussed in the present disclosure and still be within the scope of the present disclosure.

Reference throughout this specification to "one embodiment" or "an embodiment" means that a particular feature, structure, or characteristic described in connection with the embodiment is included in at least one embodiment. Thus, appearances of the phrases "in one embodiment" or "in an embodiment" in various places throughout this specification are not necessarily all referring to the same embodiment. Furthermore, the term "or" is intended to mean an inclusive "or" rather than an exclusive "or". When the terms "about," "substantially," or "approximately" are used herein, this means that the nominal values presented are accurate to within ±10%. Furthermore, the terms "first," "second," "third," "fourth," and the like as used herein mean labels that distinguish between different elements and do not necessarily have an ordinal meaning according to their numerical designation.

The terms "above," "below," "between," "disposed on," "before," "after," and "over" as used herein refer to the relative position of one layer or component of material with respect to another layer or component. For example, one layer disposed on, above, or below another layer may be in direct contact with the other layer, or may have one or more intervening layers. Furthermore, one layer disposed between two layers may be in direct contact with both layers, or may have one or more intermediate layers. Similarly, a feature disposed between two features may be in direct contact with an adjacent feature, or may have one or more intervening layers or components, unless expressly stated otherwise.

It is to be understood that the above description is intended to be illustrative, and not restrictive. Many other embodiments will be apparent to those of skill in the art upon reading and understanding the above description. The scope of the disclosure should, therefore, be determined with reference to the appended claims, along with the full scope of equivalents to which such claims are entitled.

Claims

1. A pressure exchanger comprising:

a rotor configured to receive a first fluid, receive a second fluid, and exchange pressure between the first fluid and the second fluid;

a sleeve disposed around the rotor, wherein the first fluid radially enters the rotor through the sleeve; and

A column is disposed inside the rotor.

2. The pressure exchanger of claim 1 , wherein the second fluid enters the rotor radially via the columns, and wherein the columns form:

a first low-voltage input port and a first low-voltage output port; or

a first high-voltage input port and a first high-voltage output port.

3. The pressure exchanger according to claim 2, wherein the sleeve forms:

a first low-voltage input port and a first low-voltage output port; or

a first high-voltage input port and a first high-voltage output port.

4. The pressure exchanger according to claim 3, characterized in that:

The column also forms:

a second low-voltage input port and a second low-voltage output port; or

a second high voltage input port and a second high voltage output port; and

The sleeve also forms:

a second low-voltage input port and a second low-voltage output port; or

a second high-voltage input port and a second high-voltage output port.

5. The pressure exchanger according to claim 1, characterized in that:

The rotor is configured to rotate about an axis of rotation;

The sleeve forms an angled port disposed about a port axis; and

The port axis does not intersect the rotation axis.

6. The pressure exchanger according to claim 2, characterized in that:

The rotor is configured to rotate about an axis of rotation;

The post forms an angled port disposed about a port axis; and

The port axis does not intersect the rotation axis.

7. The pressure exchanger of claim 1 , wherein the rotor forms a plurality of conduits, wherein at least one of the first fluid or the second fluid radially enters the rotor via the plurality of conduits, and wherein the plurality of conduits are circumferentially fluted.

8. A pressure exchanger comprising:

A rotor configured to exchange pressure between a first fluid and a second fluid, the rotor forming a rotor cavity, the rotor comprising:

An outer side surface, wherein the first fluid radially enters the rotor via the outer side surface.

9. The pressure exchanger of claim 8 , wherein the rotor forms a plurality of peripherally fluted conduits configured to pass through the rotor in a spiral trajectory, the plurality of peripherally fluted conduits spanning the rotor starting near a first distal end of the rotor and ending near a second distal end of the rotor, wherein at least one of the first fluid or the second fluid radially enters the rotor into at least one of the plurality of peripherally fluted conduits, and wherein the plurality of peripheral flutes of the plurality of conduits lead to a sleeve disposed about the rotor.

10. The pressure exchanger according to claim 8 is characterized in that it also includes a column arranged in the rotor cavity, the column forming a column cavity, wherein the second fluid enters the column cavity axially and leaves the column cavity radially to radially enter the rotor, and wherein the rotor also includes an inner surface forming the rotor cavity, wherein the second fluid radially enters the rotor via the inner surface.

11. The pressure exchanger of claim 10, wherein the rotor forms a plurality of conduits, wherein at least one of the first fluid or the second fluid radially enters the rotor into at least one of the plurality of conduits, and wherein the plurality of conduits are circumferentially fluted.

12. The pressure exchanger of claim 11 , wherein the plurality of peripheral flutes of the plurality of tubes lead to at least one of a sleeve disposed about the rotor or the post, and wherein the tubes span the rotor starting near a first distal end of the rotor and ending near a second distal end of the rotor.

13. The pressure exchanger of claim 12, wherein the plurality of tubes are arranged to pass through the rotor in a spiral trajectory.

14. The pressure exchanger according to claim 13, characterized in that:

The rotor is configured to rotate about an axis of rotation;

The sleeve forms an angled port disposed about a port axis; and

The port axis does not intersect the rotation axis.

15. The pressure exchanger according to claim 13, characterized in that:

The rotor is configured to rotate about an axis of rotation;

The post forms an angled port disposed about a port axis; and

The port axis does not intersect the rotation axis.

16. A pressure exchanger comprising:

a rotor forming a plurality of radial conduits, wherein the rotor is configured to receive a first fluid, receive a second fluid, and exchange pressure between the first fluid and the second fluid; and

a column disposed in a rotor cavity formed by the rotor, wherein the first fluid radially enters the rotor into one of the plurality of radial conduits via a first port of a first pair of ports formed by a sleeve disposed around the rotor or the column, and radially exits the rotor via a second port of the first pair of ports.

17. The pressure exchanger of claim 16, further comprising a second pair of ports formed by the sleeve or the post, the second pair of ports comprising:

Low voltage input port and high voltage output port;

or a high pressure input port and a low pressure output port, wherein the first pair of ports formed by the sleeve or the column comprises:

Low voltage input port and high voltage output port;

Or a high voltage input port and a low voltage output port.

18. The pressure exchanger according to claim 17, characterized in that:

The rotor is configured to rotate about an axis of rotation;

The sleeve forms an angled port disposed about a port axis; and

The port axis does not intersect the rotation axis.

19. The pressure exchanger according to claim 17, wherein:

The rotor is configured to rotate about an axis of rotation;

The post forms an angled port disposed about a port axis; and

The port axis does not intersect the rotation axis.

20. The pressure exchanger according to claim 17, comprising:

a third pair of ports formed by the sleeve or the column, the third pair of ports comprising: a low pressure input port and a high pressure output port; or

a high voltage input port and a low voltage output port; and

a fourth pair of ports formed by the sleeve or the column, the fourth pair of ports comprising: a low pressure input port and a high pressure output port; or

High voltage input port and low voltage output port.