Pressure exchanger

Abstract

A pressure exchanger includes a rotor configured to exchange pressure between a first fluid at a first pressure and a second fluid at a second pressure. The rotor forms a conduit from a first distal end to a second distal end. The pressure exchanger also includes a first end cap forming a high pressure input (HPIN) port configured to provide a first fluid into the conduit in a substantially axial direction at a first pressure. The first end cap forms a low pressure output (LPOUT) port configured to receive the first fluid from the conduit at a third pressure. The pressure exchanger also includes a second end cap forming a low pressure input (LPIN) port configured to provide a second fluid at a second pressure into the conduit and also forming a high pressure output (HPOUT) port configured to receive the second fluid from the conduit at a fourth pressure.

Description

This application is a divisional application of Chinese invention patent application No. 202380029556.0, which is a Chinese national phase application of international application No. PCT / US2023 / 016310 filed on September 23, 2024 and named “Pressure Exchanger”. Technical Field

[0001] The present disclosure relates to pressure exchangers. Background Art

[0002] Pressure exchangers exchange pressure between fluids. Mixing of fluids may occur. BRIEF DESCRIPTION OF THE DRAWINGS

[0003] The present disclosure is illustrated by way of example and not by way of limitation in the figures of the accompanying drawings.

[0004] Figures 1A to 1D A schematic diagram of a fluid handling system including a hydraulic energy transfer system is shown, according to certain embodiments.

[0005] FIG. 2A to FIG. 2E is an exploded perspective view of a pressure exchanger according to some embodiments.

[0006] Figures 3A to 3P Components of a pressure exchanger according to certain embodiments are shown.

[0007] Figures 4A to 4K Components of a pressure exchanger according to certain embodiments are shown.

[0008] FIG. 5A to FIG. 5J Components of a pressure exchanger according to certain embodiments are shown. DETAILED DESCRIPTION

[0009] Embodiments described herein relate to optimizing a pressure exchanger by one or more of minimizing mixing, improving efficiency, cavitation control, noise control, and / or vibration control.

[0010] High pressure fluid can be used in systems such as hydraulic fracturing (such as franking or fracing) systems, desalination systems, refrigeration systems, mud pumping systems, etc. Pumps can be used to provide high pressure fluids. Some fluids (e.g., salt water, viscous fluids, sand, powders, fragments, ceramics, etc.) may damage the pump and reduce its efficiency. Pressure exchangers can be used to exchange pressure between two fluids. Pumps can be used to increase the pressure of a first fluid (e.g., substantially free of solid particles, low viscosity, water, etc.). Pressure exchangers can receive a high pressure first fluid (e.g., water) and a low pressure second fluid (e.g., a fluid containing solid particles, a more viscous fluid, salt water), and can transfer pressure from the high pressure first fluid to the low pressure second liquid.

[0011] In a pressure exchanger, liquid-to-liquid pressure exchange is performed via an oscillating "fluid plug" in a rotor conduit. The "fluid plug" is not impermeable, and mixing may occur between the two fluids that exchange pressure energy. Mixing may depend on a variety of factors, such as the travel distance of the "fluid plug" (e.g., the portion of the rotor conduit traversed by the "fluid plug", the distance traveled by the "fluid plug" in the rotor conduit within a standardized rotor rotation length cycle), turbulence, diffusion, jetting, rotor inlet and outlet losses, etc. The efficiency of the pressure exchanger may be proportional to the travel distance of the "fluid plug", while the mixing of the pressure exchanger may be inversely proportional to the travel distance. Traditional attempts to increase the efficiency of pressure exchangers by increasing the travel distance will also increase mixing within the pressure exchanger. Less efficient pressure exchangers consume more energy and cause other components (such as pumps) to be used and worn more. Pressure exchangers for mixed fluids can result in increased specific energy consumption (for example, in seawater reverse osmosis (SWRO) devices), fluid contamination (for example, when performing pressure exchange with toxic fluids, solid particle fluids, highly viscous fluids, etc.), component wear (for example, pump wear due to solid particles being introduced into the water), etc.

[0012] In a pressure exchanger (e.g., a rotary isobaric pressure exchanger), a rotating pipe transports a high-pressure (HP) fluid from a high-pressure port (e.g., a kidney-shaped portion) to a low-pressure (LP) port, and also transports a low-pressure fluid from a low-pressure port to a high-pressure port. When the pipe fluid approaches a set of ports, the pipe fluid undergoes rapid pressurization or depressurization. The frequency and rate of pressurization or depressurization depends on the rotor revolutions per minute (RPM), the number of pressure exchange cycles per revolution, and the pressure difference between the high-pressure and low-pressure ports. Rapid pressurization and depressurization cause high-speed fluid jets to generate noise and produce flow and pressure pulsations, thereby increasing vibration levels. If the local fluid pressure (e.g., due to high speed) drops below the vapor pressure at that temperature, this can also produce vapor bubbles. When the vapor bubble travels to a higher pressure area, the bubble collapses, resulting in the formation of a void, which causes the surrounding fluid to rush in, producing extremely high local pressure spikes. When it occurs near a solid wall, pitting damage (e.g., cavitation) is generated and accumulates over time. This cavitation further amplifies the noise and vibration levels.

[0013] The devices, systems and methods of the present disclosure provide optimization of efficiency, mixing, cavitation, sound and vibration of a pressure exchanger.

[0014] A pressure exchanger includes a rotor configured to exchange pressure between a first fluid at a first pressure and a second fluid at a second pressure. The rotor forms a pipeline from a first distal end to a second distal end. The pressure exchanger also includes a first end cap, which forms a high pressure input (HPIN) port, which is configured to provide a first fluid to the pipeline at a first pressure. The first end cap forms a low pressure output (LPOUT) port, which is configured to receive the first fluid from the pipeline at a third pressure. The pressure exchanger also includes a second end cap, which forms a low pressure input (LPIN) port, which is configured to provide a second fluid to the pipeline at a second pressure, and also forms a high pressure output (HPOUT) port, which is configured to receive the second fluid from the pipeline at a fourth pressure.

[0015] In some embodiments, the HPIN port is configured to provide a first fluid to the conduit at a first pressure in a substantially axial direction. The first end cap may include one or more radial sidewalls that are closer to each other than the radial sidewalls of the high pressure output port, fillets between the radial sidewalls and the inner sidewall, radial sidewalls that are both sloped, non-planar three-dimensional slopes, inserts, etc.

[0016] In some embodiments, one or more side walls (e.g., radial side walls) of the first end cap that form the high pressure input port or the low pressure output port are substantially planar (e.g., non-curved). In some embodiments, the rotor forms at least three concentric rows of tubes. In some embodiments, the pressure exchanger includes a spacer disposed in the first end cap, wherein the spacer is disposed between an interconnect (e.g., a metal interconnect) and the first end cap (e.g., a ceramic end cap).

[0017] In some embodiments, the second end cap forms a first facet near the low pressure input port and a second facet near the high pressure output port. In some embodiments, the first end cap does not include facets 340 near the low pressure output port and the high pressure input port. In some embodiments, one or more of the first facet and the second facet have chamfers, include a radial extent shorter than the radial extent of the corresponding pipe formed by the rotor, include different grooves for different concentric rows of pipes, staggered arrangements, etc. In some embodiments, the second end cap forms a pre-pressurized hole near the first facet.

[0018] The present disclosure has advantages over traditional solutions. In some embodiments, the pressure exchanger of the present disclosure exchanges pressure with higher efficiency compared to traditional systems. This results in less energy usage and less use and wear of other components (e.g., pumps). In some embodiments, the pressure exchanger of the present disclosure exchanges pressure with less fluid mixing compared to traditional systems. This results in lower specific energy consumption of the device, less fluid contamination, less wear of components (e.g., pumps), etc. In some embodiments, the pressure exchanger of the present disclosure produces less noise, less vibration, and less damage (e.g., pitting damage, cavitation) than traditional systems. This results in less wear, less maintenance, less parts replacement, less downtime, etc.

[0019] Although some embodiments of the present disclosure are described with respect to rotors and end caps of a pressure exchanger, embodiments of the present disclosure may also be applied to other components and other devices (eg, adapter plates, etc.).

[0020] Although some embodiments of the present disclosure are described with respect to isobaric pressure exchangers, pressure exchangers, and hydraulic energy transfer systems, the present disclosure can be applied to other systems and devices (e.g., non-isobaric pressure exchangers, rotating parts of non-pressure exchangers, non-rotating pressure exchangers, etc.).

[0021] Although some embodiments of the present disclosure are described with respect to exchanging pressure between fluids used in fracturing systems, desalination systems, and / or refrigeration systems, the present disclosure can be applied to other types of systems. Fluids can refer to liquids, gases, transcritical fluids, supercritical fluids, subcritical fluids, and / or combinations thereof.

[0022] Although some embodiments of the present disclosure are described with respect to a pressure exchanger having a sleeve, in some embodiments, the pressure exchanger of the present disclosure has a sleeve (e.g., has a sleeve), and in some embodiments, the pressure exchanger of the present disclosure does not have a sleeve (e.g., does not have a sleeve but has a center column).

[0023] Although some embodiments of the present disclosure are described with respect to a pressure exchanger having a single cycle, in some embodiments, the pressure exchanger of the present disclosure is a multi-cycle pressure exchanger.

[0024] Figures 1A to 1D Schematic diagrams of fluid handling systems 100A- 100D including a hydraulic energy transfer system 110 (eg, a pressure exchanger) are shown, according to certain embodiments.

[0025] Figures 1A to 1DEach hydraulic energy transfer system 110 may include a pressure exchanger including a rotor configured to exchange pressure between a first fluid at a first pressure and a second fluid at a second pressure. The rotor forms a pipeline from the first distal end to the second distal end. The pressure exchanger also includes a first end cap, which forms a high pressure input (HPIN) port, which is configured to provide the first fluid to the pipeline at a first pressure. The first end cap forms a low pressure output (LPOUT) port, which is configured to receive the first fluid from the pipeline at a third pressure. The pressure exchanger also includes a second end cap, which forms a low pressure input (LPIN) port, which is configured to provide the second fluid to the pipeline at a second pressure, and also forms a high pressure output (HPOUT) port, which is configured to receive the second fluid from the pipeline at a fourth pressure.

[0026] In some embodiments, Figures 1A to 1D The hydraulic energy transfer system 110 has a high pressure input port configured to provide a first fluid at a first pressure to a conduit of a rotor of the hydraulic energy transfer system 110 in a substantially axial direction. In some embodiments, one or more side walls (e.g., radial side walls) of the end cap forming the high pressure input port or the low pressure output port are substantially planar (e.g., non-curved). In some embodiments, the second end cap forms a first point face near the low pressure input port and a second point face near the high pressure output port.

[0027] Figure 1A A schematic diagram of a fluid handling system 100A including a hydraulic energy transfer system 110 is shown, according to certain embodiments.

[0028] In some embodiments, the hydraulic energy transfer system 110 includes a pressure exchanger (PX). The hydraulic energy transfer system 110 (e.g., PX) receives a low pressure (LP) fluid input 120 (e.g., a low pressure inlet flow, a low pressure input (LPIN)) 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 flow, a high pressure input (HPIN)) from a high pressure (HP) input system 132. The hydraulic energy transfer system 110 (e.g., PX) 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, a low pressure output (LPOUT)) to a low pressure fluid output system 142, and provides a high pressure fluid output 150 (e.g., a high pressure outlet flow, a high pressure output (HPOUT)) to a high pressure fluid output system 152.

[0029] In some embodiments, the hydraulic energy transfer system 110 includes a PX to exchange pressure between a high pressure fluid input 130 and a low pressure fluid input 120. The PX may be referred to as an isobaric pressure exchanger (IPX). The PX (e.g., IPX) may be a device that transfers fluid pressure between a high pressure fluid input 130 and a low pressure fluid input 120 with an efficiency of more than about 50%, 60%, 70%, 80%, 90% or more (e.g., substantially isobaric pressure exchange without using centrifugal techniques). High pressure (e.g., high pressure fluid input 130, high pressure fluid output 150) refers to a pressure that is higher than a low pressure (e.g., low pressure fluid input 120, low pressure fluid output 140). The low pressure fluid input 120 of the PX may be pressurized and leave the PX at a high pressure (e.g., high pressure fluid output 150, whose pressure is greater than the pressure of the low pressure fluid input 120), while the high pressure fluid input 130 may be depressurized and leave the PX at a low pressure (e.g., low pressure fluid output 140, whose pressure is lower than the high pressure fluid input 130). The PX can operate with a high pressure fluid input 130 directly applying force to pressurize a low pressure fluid input 120, with or without a fluid separator between the fluids. Examples of fluid separators that can be used with the PX include, but are not limited to, pistons, capsules, diaphragms, and the like. In some embodiments, the PX can be a rotary device. A rotary PX, such as that manufactured by Energy Recovery, Inc. of San Leandro, California, may not have any separate valves because the effective valve adjustment action is accomplished inside the device via the relative movement of the rotor relative to the end cap. A rotary PX can be designed to operate with an internal piston to isolate the fluid and transfer pressure with relatively little mixing of the inlet fluid streams. A reciprocating PX may include a piston that reciprocates in a cylinder for transferring pressure between the fluid streams. Any or more PXs may be used in the present disclosure, such as, but not limited to, a rotary PX, a reciprocating PX, or any combination thereof. Additionally, the PX may be provided on a skid that is separate from the other components of the fluid treatment system 100 (eg, where the PX is added to an existing fluid treatment system).

[0030] In some embodiments, the motor 160 is coupled to the hydraulic energy transfer system 110 (e.g., coupled to the PX). In some embodiments, the motor 160 controls the speed (e.g., RPM) of the rotor of the hydraulic energy transfer system 110 (e.g., to increase the pressure of the high pressure fluid output 150, decrease the pressure of the low pressure fluid output 140, etc.). In some embodiments, the motor 160 generates energy based on the pressure exchange in the hydraulic energy transfer system 110 (e.g., acts as a generator).

[0031] The hydraulic energy transfer system 110 can be a hydraulic protection system (e.g., a hydraulic buffer system, a hydraulic isolation system) that can prevent or limit contact between a fluid (e.g., a fluid loaded with solid particles, a fracturing fluid, a viscous fluid, a toxic fluid, etc.) and various equipment (e.g., a hydraulic fracturing equipment, a high-pressure pump) while exchanging work and / or pressure with another fluid. By preventing or limiting contact between various equipment (e.g., fracturing equipment, pumps, etc.) and specific fluids (e.g., fluids containing solid particles), the hydraulic energy transfer system 110 increases the life and performance of various equipment (e.g., fracturing equipment, high-pressure fluid pumps) while reducing wear and damage. By using equipment (e.g., a high-pressure fluid pump) that is not designed for abrasive fluids (e.g., fracturing fluids and / or corrosive fluids), less expensive equipment can be used in the fluid treatment system 100.

[0032] The hydraulic energy transfer system 110 may include a hydraulic turbocharger or a hydraulic pressure exchange system, such as a rotary PX. The PX may include one or more chambers (e.g., 1 to 100) to facilitate pressure transfer and pressure balancing between volumes of a first fluid and a second fluid (e.g., a gas, a liquid, a multiphase fluid). In some embodiments, the PX 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., a fracturing fluid containing sand, proppant, powder, debris, ceramics). Solid particle fluids may cause wear and / or erosion of PX components such as the rotor and end caps of the PX. As the rotor rotates relative to the end caps, the fluid (e.g., abrasive particles in the fluid) may cause wear at the interface between the rotor and each end cap. Replacing worn parts of the PX may be expensive.

[0033] 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.

[0034] Figure 1B A schematic diagram of a fluid handling system 100B including a hydraulic energy transfer system 110 is shown, according to certain embodiments. Figure 1B in Figure 1A Features with the same or similar reference numerals may have the same or similar reference numerals as those in Figure 1A Same or similar parts, features, etc.

[0035] The fluid treatment system 100B may be a fracturing system (e.g., a hydraulic fracturing system). In some embodiments, the fluid treatment system 100B includes: Figure 1B More components, fewer components, same routes, different routes, etc. shown.

[0036] 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 fluids substantially free of solid particles (e.g., fluids free of proppant, water, filtered fluids, etc.).

[0037] 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 (eg, PX). 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.

[0038] The hydraulic energy transfer system 110 exchanges pressure between a low pressure fluid input 120 (e.g., a 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., a high pressure fracturing fluid) to a high pressure output system 152 and to provide a low pressure fluid output 140 (e.g., low pressure water). The high pressure output system 152 may include a formation 154 (e.g., a well) that includes fractures 156. Solid particles (e.g., proppant) from the high pressure fluid output 150 may be provided into the fractures 156 of the formation.

[0039] 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 can be provided to the high pressure fluid pump to generate the high pressure fluid input 130, which becomes the low pressure fluid output 140 when leaving the hydraulic energy transfer system 110.

[0040] 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). The high pressure fluid output 150 may be provided into the formation 154 and then pumped from the formation 154 by the low pressure fluid pump 124 to generate the low pressure fluid input 120.

[0041] In some embodiments, the fluid handling system 100B is used in a well completion operation in the oil and gas industry to perform hydraulic fracturing (e.g., hydraulic fracturing, fracking) to increase the release of oil and gas in a rock formation 154. A high pressure output system 152 may include a rock formation 154 (e.g., a well). Hydraulic fracturing may include pumping a high pressure fluid 150 containing a combination of water, chemicals, and solid particles (e.g., sand, ceramics, proppants) into the well (e.g., rock formation 154) under 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 rock formation 154 by propagating and increasing the size of fractures 156 in the rock formation 154. The high pressure of the high pressure fluid output 150 initiates and increases the size of the fractures 156 and propagates through the rock formation 154 to release more oil and gas, while solid particles (e.g., powders, chips, etc.) enter the fractures 156 to keep the fractures 156 open (e.g., to prevent the fractures 156 from closing once the high pressure fluid output 150 is depressurized).

[0042] To pump such particle-laden fluid into the formation 154 (e.g., a well), the fluid handling system 100B may include one or more high-pressure fluid pumps 134 and one or more low-pressure fluid pumps 124 coupled to a hydraulic energy transfer system 110. For example, the hydraulic energy transfer system 110 may be a hydraulic turbocharger or a PX (e.g., a rotary PX). In operation, the hydraulic energy transfer system 110 transfers pressure between a first fluid (e.g., high-pressure fluid input 130, a fluid without proppant) pumped by the high-pressure fluid pump 134 and a second fluid (e.g., low-pressure fluid input 120, a fluid containing proppant or a fracturing fluid) pumped by the low-pressure fluid pump 124 without any substantial mixing between the two. In this way, the hydraulic energy transfer system 110 prevents or limits wear on the high-pressure fluid pump 134 while enabling the fluid handling system 100B to pump a high-pressure fracturing fluid (e.g., high-pressure fluid output 150) into the formation 154 to release oil and gas. To operate in corrosive and abrasive environments, the hydraulic energy transfer system 110 can be made of a material that is resistant to the corrosive and abrasive substances in the first fluid and the second fluid. For example, the hydraulic energy transfer system 110 can be made of a ceramic (e.g., aluminum oxide, 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 tungsten carbide in a CoCr, Ni, NiCr, or Co matrix.

[0043] In some embodiments, the hydraulic energy transfer system 110 includes a PX (e.g., a rotary PX) with a high pressure fluid input 130 (e.g., a first fluid, a high pressure solids-free fluid) entering a first side of the PX, wherein the high pressure fluid input 130 contacts a low pressure fluid input 120 (e.g., a second fluid, a low pressure fracturing fluid) entering the PX on a second side. 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 directs the second fluid output of the PX (e.g., the high pressure fluid output 150) down into the well (e.g., the formation 154) for fracturing operations. The first fluid (e.g., the low pressure fluid output 140) similarly exits the PX, but 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 wear the interface between the rotor and the respective end cap as the rotor rotates relative to the respective end cap.

[0044] Figure 1C 1 shows a schematic diagram of a fluid processing system 100C including a hydraulic energy transfer system 110 according to some embodiments. The fluid processing system 100C may be a desalination system (e.g., removing salt and / or other minerals from water). In some embodiments, the fluid processing system 100C includes a Figure 1C More components, fewer components, same routes, different routes, etc. shown.

[0045] 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 the low pressure fluid input 120 (e.g., low pressure seawater, feed water) to the hydraulic energy transfer system 110 (e.g., PX). The high pressure input system 132 may include a membrane 136 that provides the high pressure fluid input 130 (e.g., high pressure salt water) to the hydraulic energy transfer system 110 (e.g., PX). 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 salt water) to a low pressure output system 142 (e.g., a geological body, ocean, sea, waste, etc.).

[0046] The membrane 136 can be a membrane separation device configured to separate fluids passing through a membrane such as a reverse osmosis membrane. The membrane 136 can provide a high pressure fluid input 130 to the hydraulic energy transfer system 110, which is a concentrated feed water or concentrate (e.g., brine). The pressure of the high pressure fluid input 130 can 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 purposes, the term "feed water" is used. However, fluids other than water can be used in the hydraulic energy transfer system 110. The hydraulic energy transfer system 110 can also be used for other applications, such as industrial wastewater.

[0047] 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 drinking water 172 and high pressure fluid input 130 (e.g., high pressure salt water). The low pressure output system 142 provides a salt water output 174 (e.g., to a geological body, ocean, sea, waste, etc.).

[0048] In some embodiments, a high pressure fluid pump 176 is disposed between the feed pump 126 and the 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 mixes with the high pressure seawater provided by the circulation pump 158.

[0049] In some embodiments, the use of the hydraulic energy transfer system 110 reduces the load on the high pressure fluid pump 176. In some embodiments, the fluid treatment system 100C provides low pressure drinking water 172 without using the high pressure fluid pump 176. In some embodiments, the fluid treatment system 100C provides low pressure drinking water 172 by intermittently using the high pressure fluid pump 176.

[0050] In some examples, the hydraulic energy transfer system 110 (e.g., PX) receives a low pressure fluid input 120 (e.g., low pressure feed water) at approximately 30 pounds per square inch (PSI), and receives a high pressure fluid input 130 (e.g., high pressure brine or concentrate) at approximately 980 PSI. The hydraulic energy transfer system 110 (e.g., PX) 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., PX) outputs a high pressure fluid output 150 (e.g., high pressure (compressed) feed water) at approximately 965 PSI, and outputs a low pressure fluid output 140 (e.g., low pressure concentrate) at approximately 15 PSI. Thus, the efficiency of the hydraulic energy transfer system 110 (e.g., PX) may be approximately 97% because the input volume is approximately equal to the output volume of the hydraulic energy transfer system 110 (e.g., PX), and 965 PSI is approximately 97% of 980 PSI.

[0051] Figure 1D FIG. shows a schematic diagram of a fluid processing system 100D including a hydraulic energy transfer system 110 according to certain embodiments. The fluid processing system 100D can be a refrigeration system. In some embodiments, the fluid processing system 100D includes more components, fewer components, the same routes, different routes, etc. than those shown. Figure 1D than those shown.

[0052] The hydraulic energy transfer system 110 (e.g., PX) can receive a low-pressure fluid input 120 from a low-pressure input system 122 (e.g., a low-pressure lift device 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., PX) can exchange pressure between the low-pressure fluid input 120 and the high-pressure fluid input 130 to provide a high-pressure fluid output 150 to a high-pressure output system 152 (e.g., a high-pressure lift device 159) and a low-pressure fluid output 140 to a low-pressure output system 142 (e.g., an evaporator 144). The evaporator 144 can provide fluid to a compressor 178 and a low-pressure lift device 128. The condenser 138 can receive fluid from the compressor 178 and the high-pressure lift device 159.

[0053] The fluid processing system 100D can 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 can all be fluids (e.g., refrigerants) circulating in the closed system of the fluid processing system 100D.

[0054] In some embodiments, the fluid of the fluid processing system 100D can include solid particles. For example, pipes, equipment, connections (e.g., pipe welding, pipe brazing), etc. may introduce solid particles (e.g., solid particles from welding) into the fluid in the fluid processing system 100D. The solid particles in the fluid and / or the high pressure of the fluid may cause wear and / or erosion of the components (e.g., rotors, end caps) of the PX of the hydraulic energy transfer system 110.

[0055] FIG. 2A to FIG. 2E is an exploded perspective view of a rotary PX 40 (e.g., a rotary pressure exchanger, a rotary liquid piston compressor (LPC)) according to certain embodiments.

[0056] The PX 40 includes a rotor 46 configured to exchange pressure between a first fluid at a first pressure and a second fluid at a second pressure. The rotor 46 forms a channel 70 (e.g., a conduit) leading from a first distal end (e.g., an opening 72) to a second distal end (e.g., an opening 74). The PX 40 also includes an end cap 64 forming a high pressure input port (e.g., an outlet orifice 76) configured to provide the first fluid into the channel 70 at a first pressure. The end cap 64 forms a low pressure output port (e.g., an outlet orifice 78) configured to receive the first fluid from the channel 70 at a third pressure. The PX 40 also includes an end cap 66 forming a low pressure input port (e.g., an outlet orifice 80) configured to provide the second fluid into the channel 70 at a second pressure, and a high pressure output port (e.g., an outlet orifice 82) configured to receive the second fluid from the channel 70 at a fourth pressure.

[0057] In some embodiments, FIG. 2A to FIG. 2E The PX 40 of the embodiment of the present invention has a high pressure input port (e.g., outlet orifice 76) configured to provide a first fluid at a first pressure to the passage 70 of the rotor 46 of the PX 40 in a substantially axial direction. In some embodiments, one or more side walls (e.g., radial side walls) of the end cap 64 forming the high pressure input port (e.g., outlet orifice 76) or the low pressure output port are substantially planar (e.g., non-curved). In some embodiments, the end cap 66 forms a first point face near the high pressure output port (e.g., outlet orifice 82) and a second point face near the high pressure output port (e.g., outlet orifice 82).

[0058] The PX 40 is configured to transfer pressure and / or work between a first fluid (e.g., a proppant-free fluid or supercritical carbon dioxide, a high pressure fluid input 130) and a second fluid (e.g., a fracturing fluid or superheated gaseous carbon dioxide, a low pressure fluid input 120) with minimal mixing of the fluids. The rotary PX 40 may include a generally cylindrical body portion 42 including a sleeve 44 (e.g., a rotor sleeve) and a rotor 46. The rotary PX 40 may also include two end caps 48 and 50, which include manifolds 52 and 54, respectively. The manifold 52 includes respective inlet ports 56 and outlet ports 58, while the manifold 54 includes respective inlet ports 60 and outlet ports 62. In operation, these inlet ports 56, 60 enable the first and second fluids to enter the rotary PX 40 to exchange pressures, while the outlet ports 58, 62 enable the first and second fluids to subsequently exit the rotary PX 40. In operation, inlet port 56 can receive a high pressure first fluid (e.g., high pressure fluid input 130), and after exchanging pressures, outlet port 58 can be used to direct a low pressure first fluid (e.g., low pressure fluid output 140) out of the rotary PX 40. Similarly, inlet port 60 can receive a low pressure second fluid (low pressure fluid input 120), and outlet port 62 can be used to direct a high pressure second fluid (e.g., high pressure fluid output 150) out of the rotary PX 40. End caps 48, 50 include respective end caps 64, 66 (e.g., end plates) disposed within respective manifolds 52, 54 that enable fluid-tight contact with rotor 46.

[0059] As described above, one or more components of the PX 40, such as the rotor 46, the end cap 64, and / or the end cap 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 more). For example, tungsten carbide may be more durable and may provide improved wear resistance to abrasive fluids compared to other materials such as alumina ceramics.

[0060] 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 passages 70 (e.g., ducts, rotor ducts) extending substantially longitudinally through the rotor 46, with openings 72 and 74 (e.g., rotor ports) at each end symmetrically arranged about the longitudinal axis 68. The openings 72 and 74 of the rotor 46 are arranged to be hydraulically connected to inlet apertures 76 and outlet apertures 78 (e.g., end cap inlet ports and end cap outlet ports) and inlet apertures 80 and outlet apertures 82 (e.g., end cap inlet ports and end cap outlet ports) in the end caps 64, 66, so that the passages 70 are exposed to fluids at high pressure and fluids at low pressure during rotation. As shown, the inlet apertures 76 and outlet apertures 78 and the inlet apertures 80 and outlet apertures 82 may be designed in the form of arcs or segments of a circle (e.g., C-shaped).

[0061] In some embodiments, a controller using sensor feedback (e.g., revolutions per minute measured by a tachometer or optical encoder or volume flow measured by a flow meter) can control the degree of mixing between the first and second fluids in the rotary PX 40, which can be used to improve fluid handling systems (e.g., Figures 1A to 1DThe invention also provides an embodiment of the present invention and is a method of controlling the operability of a fluid handling system 100A to 100D of the present invention. For example, varying the volumetric flow rate of the first and second fluids entering the rotary PX 40 allows an equipment operator (e.g., a system operator) to control the amount of fluids that mix within the PX 40. In addition, varying the rotational speed of the rotor 46 also allows the operator to control mixing. Three features of the rotary PX 40 that affect mixing are: (1) the aspect ratio of the rotor channel 70; (2) the duration of exposure between the first and second fluids; and (3) the formation of a fluid barrier (e.g., an interface) between the first and second fluids within the rotor channel 70. First, the rotor channel 70 (e.g., a pipe) is typically long and narrow, which stabilizes the flow within the rotary PX 40. In addition, the first and second fluids can move through the channel 70 in a piston flow state with minimal axial mixing. Second, in some embodiments, the speed of the rotor 46 reduces the contact between the first and second fluids. For example, the speed of the rotor 46 (e.g., a rotor speed of about 1200 RPM (revolutions per minute)) can 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. Therefore, a certain volume of fluid is retained in the channel 70 to act as a barrier between the first fluid and the second fluid. All of these mechanisms can limit mixing within the rotary PX 40. In addition, in some embodiments, the rotary PX 40 can be designed to operate with an internal piston or other barrier that completely or partially isolates the first fluid from the second fluid while enabling pressure transfer.

[0062] FIG. 2B to FIG. 2E is an exploded view of an embodiment of a rotary PX 40 showing the sequence of positions of a single rotor channel 70 in the rotor 46 as the channel 70 rotates through a complete cycle. Note that FIG. 2B to FIG. 2E is a simplified diagram of a rotary PX 40 showing one rotor channel 70, and the channel 70 is shown as having a circular cross-sectional shape. In other embodiments, the rotary PX 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 to FIG. 2E is a simplification for illustrative purposes, and other embodiments of the rotary PX 40 may have the same FIG. 2A to FIG. 2E46. ​​As described in detail below, the rotary PX 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 and the second fluid. The speed of the pressure wave passing through the rotor channel 70 (once the channel is exposed to the orifice 76), the diffusion rate of the fluid, and / or the rotational speed of the rotor 46 may determine whether any mixing occurs and the extent of mixing.

[0063] Figure 2B is an exploded perspective view of an embodiment of a rotary PX 40 (eg, a rotary LPC) according to certain embodiments. Figure 2B 64 and the manifold 52, while the opposing channel opening 74 is in fluid communication with the orifice 82 in the end cap 66 and, by extension, the manifold 54. As will be discussed below, the rotor 46 may rotate in a clockwise direction indicated by arrow 84. In operation, a low pressure second fluid 86 passes through the end cap 66 and enters the channel 70 where it contacts the first fluid 88 at the dynamic fluid interface 90. The second fluid 86 then drives the first fluid 88 out of the channel 70, through the end cap 64, and out of the rotary PX 40. However, due to the short duration of contact, mixing between the second fluid 86 and the first fluid 88 is minimal.

[0064] Figure 2C is an exploded perspective view of an embodiment of a rotary PX 40 (eg, a rotary LPC) according to certain embodiments. Figure 2C , the passage 70 has been rotated clockwise through an arc of approximately 90 degrees. In this position, the opening 74 (e.g., outlet) is no longer in fluid communication with the orifices 80 and 82 of the end cap 66, and the opening 72 is no longer in fluid communication with the orifices 76 and 78 of the end cap 64. Thus, the low pressure second fluid 86 is temporarily contained within the passage 70.

[0065] Figure 2D is an exploded perspective view of an embodiment of a rotary PX 40 (eg, a rotary LPC) according to certain embodiments. Figure 2D In the channel 70, Figure 2B The position shown is rotated through an arc of approximately 60 degrees. The opening 74 is now in fluid communication with the orifice 80 in the end cap 66, and the opening 72 of the passage 70 is now in fluid communication with the orifice 76 of the end cap 64. In this position, the high pressure first fluid 88 enters and pressurizes the low pressure second fluid 86, thereby driving the second fluid 86 out of the rotor passage 70 and through the orifice 80.

[0066] Figure 2E is an exploded perspective view of an embodiment of a rotary PX 40 (eg, a rotary LPC) according to certain embodiments. Figure 2E In the channel 70, Figure 2B The position shown is rotated through an arc of approximately 270 degrees. In this position, opening 74 is no longer in fluid communication with orifices 80 and 82 of end cap 66, and opening 72 is no longer in fluid communication with orifices 76 and 78 of end cap 64. Thus, first fluid 88 is no longer pressurized and is temporarily contained within passage 70 until rotor 46 rotates another 90 degrees to begin the cycle again.

[0067] Figures 3A to 3P Components of a pressure exchanger 300 according to certain embodiments are shown (e.g., FIG. 2A to FIG. 2E PX 40). Figures 3A to 3P With Figures 1A to 2E Features with similar names and / or reference numerals to features in one or more of the figures may include Figures 1A to 2E The same or similar structure, material, function, etc. as one or more of the features in FIG. Figures 3A to 3P One or more features of the PX 300 reduce mixing of fluids in the PX 300 .

[0068] Figure 3A An end cap 310 (eg, FIG. 2A to FIG. 2E A stereoscopic view of one or more end caps 64 and / or 66). Figure 3B An end cap 310 (eg, Figure 3A The end cap, FIG. 2A to FIG. 2E A three-dimensional cutaway view of the end caps 64 and / or 66 of one or more of the figures. Figure 3C A cross-sectional view of components of the pressure exchanger 300 is shown (eg, Figure 3A and / or Figure 3B Parts FIG. 2A to FIG. 2E The end caps 64 and / or 66 of one or more of the Figures, FIG. 2A to FIG. 2E 46 in one of the figures).

[0069] In some embodiments, PX 300 includes a rotor 320 and an end cap 310. Rotor 320 is configured to exchange pressure between a first fluid at a first pressure and a second fluid at a second pressure. Rotor 320 forms a conduit 322 (e.g., FIG. 2A to FIG. 2E of channel 70).

[0070] The PX 300 may include a first end cap and a second end cap 310. The first end cap 310 is disposed at a first distal end of the rotor 320, and the second end cap 310 is disposed at a second distal end of the rotor 320.

[0071] The end cap 310 is disposed at the distal end of the rotor 320. The end cap 310 forms a port 312 (e.g., FIG. 2A to FIG. 2E The orifices 76 and 78, FIG. 2A to FIG. 2E The orifices 80 and 82, inlet, outlet, high pressure input port, high pressure output port, low pressure input port, low pressure output port)

[0072] In some embodiments, the end cap 310 (e.g., disposed at a first distal end of the rotor 320) forms a high-pressure input port and a low-pressure output port, wherein the high-pressure input port is configured to provide a first fluid to the pipe 322 at a first pressure in a substantially axial direction, and the low-pressure output port is configured to receive the first fluid from the pipe 322 at a third pressure lower than the first pressure.

[0073] In some embodiments, the end cap 310 (e.g., disposed at the second distal end of the rotor 320) forms a low-pressure input port and a high-pressure output port, wherein the low-pressure input port is configured to provide the second fluid to the pipeline 322 at a second pressure, and the high-pressure output port is configured to receive the second fluid from the pipeline 322 at a fourth pressure higher than the second pressure.

[0074] In some embodiments, the PX 300 may include two ramps to reduce rotor incidence losses and prevent interface deflection.

[0075] In some embodiments, an end cap insert 330 (eg, made of polycarbonate, fiber-reinforced polytetrafluoroethylene (PTFE), and / or polyetheretherketone (PEEK)) is used to direct flow.

[0076] In some embodiments, end cap 310 has a 3D slope.

[0077] In some embodiments, the end cap 310 has a kidney-shaped closure of the low pressure input at least 2 degrees earlier than the high pressure output to avoid flow acceleration when the conduit is closed.

[0078] In some embodiments, the end cap 310 has rounded corners (eg, heavily rounded corners) at the high pressure input kidney-shaped outlet diameter corners (eg, to reduce mixing through the inner row of conduits).

[0079] In some embodiments, the high pressure input kidney opening of the PX 300 is later than the high pressure output to help move the interface away from the high pressure output and reduce mixing at the high pressure output.

[0080] In some embodiments, the dot surface is located at the high voltage output opening (rather than at the high voltage input opening) to reduce mixing at the high voltage output and avoid interfering with interfaces near the high voltage input opening.

[0081] In some embodiments, the high pressure output fluid is used as the bearing fluid and the center bore fluid (eg, to reduce mixing of the high pressure input with the high pressure output by leakage in the axial gap).

[0082] In some embodiments, the length-to-depth (L / D) ratio and roundness of conduit 322 are maximized.

[0083] In some embodiments, a honeycomb rectifier is used as an insert in the duct 322 to reduce mixing.

[0084] In some embodiments, the end cap 310 includes radial sidewalls 314 (e.g., radial front sidewall 314A, radial rear sidewall 314B), inner sidewall 316, and outer sidewall 318 that form ports 312 (e.g., high pressure input port, high pressure output port, low pressure input port, low pressure output). The front radial sidewall 314A is the first radial sidewall seen by the conduit 322 as it rotates. The rear radial sidewall 314B is the sidewall of the same port seen by the rotor conduit 322 after the front radial sidewall. In some embodiments, the ports 312 have similar dimensions. In some embodiments, the radial sidewalls 314 of the high pressure input port are at least two degrees (e.g., four degrees, six degrees, eight degrees, ten degrees, etc.) closer to each other than the radial sidewalls 314 of the high pressure output port (e.g., see Figure 3G to Figure 3H ).For example, Figure 3G Can be a high voltage output port, Figure 3H Can be a high voltage input port.

[0085] In some embodiments, at least one of the radial side walls 314 (e.g., the rear radial side wall) forming the high pressure input port is configured to close relative to the duct 322 formed by the rotor 320 at least two degrees (e.g., four degrees, six degrees, eight degrees, ten degrees, etc.) before one of the second radial side walls (e.g., the rear radial side wall, etc.) forming the high pressure output port closes relative to the duct 322 (e.g., to reduce mixing of corresponding fluids between the high pressure input and the high pressure output, to reduce mixing of the high pressure input into the high pressure output).

[0086] In some embodiments, at least one of the radial side walls 314 (e.g., the rear radial side wall) forming the low pressure input port is configured to close relative to the duct 322 formed by the rotor 320 at least two degrees (e.g., four degrees, six degrees, eight degrees, ten degrees, etc.) before one of the second radial side walls (e.g., the rear radial side wall, etc.) forming the low pressure output port closes relative to the duct 322 (e.g., to reduce mixing of corresponding fluids between the low pressure input and the low pressure output, to reduce mixing of the low pressure input into the low pressure output).

[0087] In some embodiments, one or more radial sidewalls of the low pressure output port are offset to reduce mixing at the low pressure output port.

[0088] In some embodiments, each radial sidewall 314 forming a high pressure input port has a substantially straight edge that substantially matches a corresponding substantially straight edge of a conduit 322 formed by rotor 320 (e.g., to maximize the time that conduit 322 is exposed to the port to improve efficiency).

[0089] In some embodiments, the first end cap 310 forms a first port and a second port, wherein a first substantially flat diametrical edge of the first port and a second substantially flat diametrical edge of the second port substantially match corresponding substantially straight edges of the conduit 322 of the rotor 320. In some embodiments, the second end cap 310 forms a third port and a fourth port, wherein a third substantially flat diametrical edge of the third port and a fourth substantially flat diametrical edge of the fourth port substantially match corresponding substantially straight edges of the conduit 322 of the rotor 320.

[0090] In some embodiments, at least one of the radial side walls 314 (e.g., the front radial side wall) forming the high pressure input port is configured to open relative to the duct 322 formed by the rotor 320 at least two degrees (e.g., four degrees, six degrees, eight degrees, ten degrees, etc.) after one of the second radial side walls (e.g., the front radial side wall, etc.) forming the high pressure output port opens relative to the duct 322.

[0091] In some embodiments, the end cap 310 (e.g., forming the high pressure input port) forms a fillet (or filet) (e.g., a concave strip of material having a generally triangular cross-section that rounds the inner angle between the two surfaces) between at least one radial sidewall 314 and the inner sidewall 316. In some embodiments, the end cap 310 forming the high pressure output port may form the high pressure output port without a fillet between the radial sidewall 314 and the inner sidewall 316. The fillet of the end cap 310 (e.g., forming the high pressure input port) is configured to close the high pressure input port relative to the conduit 322 of the rotor 320 before the high pressure output port of the end cap forming the high pressure output port is closed relative to the conduit 322.

[0092] The fillet may be located at the inner diameter corner of the high pressure input port outlet. The rotor 320 may form multiple rows of circular conduits 322, wherein the outer row is approximately trapezoidal in shape and the inner row is triangular in shape. Since the roundness decreases from the outer conduits to the inner conduits, the innermost row of triangular conduits may contribute more to the mixing at the high pressure output (per unit flow area) than the outer row of conduits. By increasing the fillet radius at the inner diameter outlet corner of the high pressure output port, the mixing contribution of the inner conduits may be reduced. The fillet at the bottom corner of the high pressure input port reduces the fluid (e.g., brine concentration, fluid exchanged with pressure) flowing out of the inner row of conduits 322 out of the high pressure output row.

[0093] In some embodiments, the radial sidewalls 314 of the end cap 310 (for example, forming the low pressure input port and the high pressure output port) are all formed into a slope (for example, an inclined sidewall, a sidewall that is not perpendicular to the end cap surface) (for example, see FIG. 3A to FIG. 3E ), while the radial side wall 314 of the other end cover forming the high pressure input port (eg, and the low pressure output port) does not form a slope.

[0094] In some embodiments, the radial sidewalls 314 of the end cap 310 (for example, forming the low pressure input port and the high pressure output port) are all formed into a slope (for example, an inclined sidewall, a sidewall that is not perpendicular to the end cap surface) (for example, see FIG. 3A to FIG. 3E ), while the radial side walls 314 of the other end cover forming the high-pressure input port (eg, and the low-pressure output port) are all formed with slopes.

[0095] The first radial sidewalls include a front sidewall and a rear sidewall on the high pressure input port, each sidewall having a corresponding slope angle ranging from about 30 degrees to about 70 degrees measured relative to the face of the rotor 320 .

[0096] In some embodiments, the front radial sidewall and the rear radial sidewall on the low pressure input port form a slope in the rotation direction, and the slope has a slope angle ranging from about 30 degrees to about 70 degrees measured relative to the face of the rotor 320 .

[0097] In some embodiments, the radial sidewall 314 of the end cap 310 (eg, forming the low pressure input port and the high pressure output port) forms a non-planar three-dimensional slope (eg, see Figure 3E In some embodiments, the first radial sidewall forms a non-planar three-dimensional slope defined by at least two spirals at the innermost radius and the outermost radius of the port. In some embodiments, the corresponding slope of the non-planar three-dimensional slope is defined by a spiral, and the pitch of the spiral is proportional to the radius at which the corresponding slope is located to reduce the incidence (e.g., reduce the incidence and make the absolute velocity (c) similar at any radius of the port).

[0098] Ramp 317 may be associated with velocity triangle 319. Velocity triangle 319 may include the following:

[0099] c ID =(u ID )*tan(α ID )

[0100] c OD =(u OD )*tan(α OD )

[0101] α ID = kidney slope angle at the inside diameter (ID) of the kidney (port 312 of end cap 310)

[0102] α OD = kidney slope angle at the outside diameter (OD) of the kidney (port 312 of end cap 310)

[0103] u ID = Tangential velocity at the inner diameter of the port

[0104] u OD = Tangential velocity at the outer diameter of the port

[0105] c ID = Absolute velocity at the inner diameter of the port

[0106] c OD = Absolute velocity at the outer diameter of the port

[0107] The flow exiting the rotor 320 of the PX 300 may have a combination of an axial component and a tangential component of the flow velocity. The axial component varies according to the flow velocity, and the tangential component varies according to the rotor speed and the radial position of the duct 322. In some embodiments, the outlet kidney (e.g., the port 312 of the end cap 310) is shaped to allow the three-dimensional (3D) velocity field to smoothly transition from the rotor 320 to the one-dimensional (1D) velocity field on the stator duct (e.g., the port 312 of the end cap 310). Otherwise, shock losses may result due to flow separation and vortex formation in the outlet kidney (e.g., the port 312 of the end cap 310). The outlet ramp may have a single ramp angle based on the design flow rate, target RPM, the intermediate radial position of the duct 322, etc. For similar considerations, the outlet kidney (e.g., the port 312 of the end cap 310) may also have a dual ramp at the beginning and end of the outlet kidney. In some embodiments, the 3D-shaped outlet kidney (e.g., port 312 of end cap 310) can have a slope angle that continuously changes with radial position. To overcome the manufacturing difficulties of the 3D slope, an injection molded plastic insert with a specific shape can be embedded into the outlet kidney (e.g., port 312 of end cap 310).

[0108] In some embodiments, the end cap 310 includes an insert 330 disposed in the high pressure input port, wherein the insert is configured to direct the flow and reduce the flow incidence at the rotor 320 (see, e.g., Figure 3F ).

[0109] In some embodiments, the end cap 310 forms a first point surface 340 near the high pressure input port (for example, no point surface is formed at the high pressure input port to reduce mixing of corresponding fluids between the high pressure input port and the high pressure output port), and forms a second point surface 340 near the low pressure output port (for example, see Figure 3L to Figure 3O In some embodiments, the first end cap 310 forms a second point surface near the low pressure output port, but does not form a point surface at the low pressure input port, so as to reduce mixing of corresponding fluids between the low pressure input port and the low pressure output port.

[0110] In some embodiments, the pressure exchanger 300 (e.g., PX 40) is configured to use a second fluid provided via the low pressure input port and / or the high pressure output port as a bearing fluid and / or a center bore fluid (e.g., see FIG. 3I to FIG. 3K ).

[0111] Figure 3P PX 300 is shown according to some embodiments. Rotor 320 may include insert 330 disposed in pipe 322. The insert may provide a length to diameter ratio of about 5 to about 10. The insert may be a honeycomb insert. The insert may be a honeycomb rectifier that is press-fit or shrink-fit into the pipe. Insert 330 may maximize the length to diameter ratio (L / D) and roundness of pipe 322. Insert 330 may be a honeycomb rectifier in pipe 322 to reduce fluid mixing.

[0112] The turbulence of the unstable fluid flow in the pipe 322 may cause (e.g., may mainly cause) mixing within the pipe. This causes the "mixing zone" between the two fluids in the pipe 322 to be skewed and stretched. In some embodiments, to alleviate this situation, the aspect ratio (e.g., length to diameter - L / D) of the pipe geometry is increased by inserting an insert 330 (e.g., a honeycomb rectifier) ​​into the pipe 322. The rectifier can be press-fit or shrink-fit into the pipe 322, or mechanically or adhesively (e.g., glued) attached to the pipe wall. The insert 330 (e.g., the rectifier) ​​can have a shape other than a honeycomb, and the insert 330 can divide a pipe with a certain L / D ratio into multiple pipes with a larger L / D ratio. Dividing the pipe into multiple small pipes can also reduce cavitation and noise by temporarily dispersing pressurization and decompression events at the kidney-shaped opening (e.g., the opening of the port 312 of the end cap 310).

[0113] In some embodiments, the pressure exchanger 300 is used to minimize the mixing of two fluids within the pressure exchanger 300. In the pressure exchanger 300, liquid-to-liquid pressure exchange can be performed by an oscillating "liquid plug" in the rotor conduit. The "liquid plug" may not be impenetrable, and a small amount of mixing may generally occur between the two fluids that exchange pressure energy. Mixing may depend on one or more factors, such as the travel distance of the "liquid plug" (e.g., the portion of the conduit 322 of the rotor 320 that is passed through), turbulence, diffusion, jetting, inlet and / or outlet losses of the rotor 320, etc. The efficiency of the pressure exchanger 300 may be proportional to the travel distance of the "liquid plug". The mixing of the first fluid and the second fluid in the pressure exchanger 300 may be inversely proportional to the travel distance (and the efficiency within the pressure exchanger 300). In some examples, the shorter the travel distance, the less mixing and the lower the efficiency. In some examples, a greater travel distance causes more mixing and higher efficiency (e.g., features that attempt to increase efficiency by increasing the travel distance will generally also increase mixing within the pressure exchanger). In some applications (eg, a seawater reverse osmosis (SWRO) plant), the efficiency of the pressure exchanger 300 will be maximized and mixing within the pressure exchanger 300 will be minimized to reduce the specific energy consumption (eg, of the SWRO plant).

[0114] The pressure exchanger 300 may include one or more features configured to reduce mixing within the pressure exchanger 300 without negatively impacting the efficiency of the pressure exchanger 300 (e.g., minimizing a reduction in efficiency, maintaining efficiency, increasing efficiency compared to a pressure exchanger without these features).

[0115] Features of the pressure exchanger 300 (see, for example, 3A to 3H The end cap 310 can reduce the rotor incidence loss (for example, two slopes at the entrance of port 312 to reduce incidence). The incidence can be the angle between the ideal C velocity vector and the actual C velocity vector.

[0116] The flow in the duct 322 of the rotor 320 has an axial velocity component (eg, c(m)= Figure 3C The w velocity component of the two slopes) and the tangential velocity component (e.g., Figure 3Cu velocity component in the rotor 320). The axial component can remain constant at any axial plane of the rotor 320, while the tangential component varies linearly with the radial coordinate. When the fluid enters the rotor 320 through the high pressure input port and the low pressure input port (e.g., the high pressure input and low pressure input kidney-shaped portions), the fluid can be accelerated to a velocity having a combination of the axial velocity component and the tangential velocity component at all radii immediately before the fluid enters the pipe 322 of the rotor 320. Traditionally, impact losses due to oblique incidence may occur, resulting in flow separation and mixing due to enhanced vortex formation. The end cap 310 forms a port 312, which is configured to guide the flow at a given nominal flow rate and a target RPM of the rotor 320, which results in a significant reduction in mixing and a reduction in pressure losses due to a sudden change in flow direction.

[0117] In some embodiments, the end cap 310 includes two slopes (e.g., a slope at each radial sidewall 314) to provide a substantial tangential velocity component in addition to the axial velocity component. In some embodiments, the end cap 310 has a 3D slope (e.g., further kidney-shaped geometry optimization) to allow fluid to smoothly enter the conduit 322 from the port 312 (e.g., see Figure 3C on the right side of the screen).

[0118] In some embodiments, an insert 330 (eg, made of one or more components) can be inserted into the port 312 (eg, see Figure 3F ). The insert 330 may be made of alumina ceramic, plastic such as polycarbonate, fiber reinforced polytetrafluoroethylene (PTFE) and / or polyetheretherketone (PEEK), and / or the like.

[0119] Figure 3H The end cap 310 may reduce the effective width of the port 312 (eg, kidney) by opening the high pressure input port 312 a few degrees later than the baseline, thereby reducing efficiency.

[0120] The high pressure input port may be closed earlier than the high pressure output port (e.g., the radial sidewalls 314 of the high pressure input port are closer to each other than the radial sidewalls 314 of the high pressure output). This may reduce mixing at the high pressure output port caused by fluid inertia. When the pressure exchanger is used for energy recovery in a specific application (e.g., in a seawater reverse osmosis device), mixing at the high pressure output port is undesirable. When the conduit 322 crosses the high pressure port, the flow in the conduit 322 of the rotor 320 is accelerated. When the conduit 322 opens to the high pressure port, the average conduit flow rate starts from near zero and reaches a maximum value when it begins to leave the port (e.g., kidney-shaped portion).

[0121] Conventionally, the high pressure input port and the high pressure output port are closed at the same time (e.g., the same size, with the radial sidewalls at the same distance from each other). This may cause the pipeline flow to suddenly stop within a short period of time after the fluid in the pipeline 322 leaves the port 312. Since the pipeline flow rate changes rapidly from a maximum value to near zero in a very short time, the inertia of the pipeline fluid may cause a substantial surge in the local pipeline pressure. This may cause a fluid jet to be ejected to the high pressure output port through the rapidly closed opening between the pipeline 322 and the high pressure output port. At this point, the mixing zone (e.g., a "liquid plug") may have traveled through the pipeline to the maximum extent and may be close to (e.g., very close to) the position of the high pressure output port. The jet ejected to the high pressure output port may transport fluid from the mixing zone and some of the high pressure input fluid behind the mixing zone to the high pressure output port, thereby increasing undesirable mixing at the high pressure output port.

[0122] The present invention can alleviate this increase in mixing by closing the high pressure input port several degrees before the high pressure output port. This will result in peak velocity before the high pressure input and output ports are closed by the pipeline 322. When the fluid in the pipeline 322 leaves the high pressure output port, the pipeline flow slows down, resulting in a significant reduction in the pressure spike caused by the fluid inertia. This greatly reduces the mixing zone fluid injection to the high pressure output port, resulting in reduced mixing at the high pressure output port.

[0123] The high pressure input port can be opened later than the high pressure output port. Delaying the opening of the high pressure input port after the high pressure output port causes the average position of the two fluid interfaces to be closer to the high pressure input port than the low pressure input port. This helps to move the interface away from the high pressure output and reduce mixing of the low pressure input at the high pressure output. This feature can be selectively utilized when reducing mixing is a higher priority and a slight tradeoff in efficiency is acceptable. Delaying the opening of the high pressure input by a few degrees relative to the high pressure output can move the interface away from the high pressure output, which can reduce mixing at the high pressure output.

[0124] The kidney-shaped outlet ramp (eg, radial sidewall 314 ) of end cap 310 may be configured to direct fluid into the high and low pressure output ports while minimizing shock losses at the outlet (eg, shock losses due to flow separation).

[0125] The flow of the duct 322 leaving the rotor 320 and entering the outlet port (e.g., the outlet port, the high pressure output port, and the low pressure output port) has an axial component and a tangential component of velocity. The axial velocity component may not vary much with the radius, but the tangential velocity component varies linearly with the radius. The outlet port wall may be configured to provide a smooth exit of the duct flow through the port without any separation. The sidewalls of the end cap 310 forming the port 312 may be configured to accommodate the ratio of the change of the tangential component and the axial component of velocity with the radius. By preventing flow separation at the outlet, differential pressure (DP) losses and mixing losses are reduced (e.g., the mixing zone may be closest to the duct outlet at the outlet).

[0126] The point surface 340 may be positioned to reduce mixing (see, for example, Figure 3L to Figure 3O ). The point face 340 can be used on the port 312 to gradually pressurize or depressurize the conduit 322 of the rotor 320 (for example, rather than suddenly achieving pressure equalization by high-speed injection into or out of the rotor conduit). Due to the pressure difference between the conduit 322 and the port 312, the point face 340 reduces the injection velocity by increasing the flow resistance through the narrow gap. In some embodiments, the point face 340 is located at the high-pressure output port, but not in the high-pressure input port. This can compensate for the depth of the point face 340, and pressure equalization can be achieved by the jet of high-pressure output fluid rather than high-pressure input fluid entering the low-pressure rotor conduit. When pressure equalization occurs and mixing is reduced, the "liquid plug" may be farthest from the high-pressure output port.

[0127] In some embodiments, the second fluid (e.g., the high pressure output fluid exiting the high pressure output port) can be used as a bearing fluid and / or a center bore fluid. In a pressure exchanger 300 (e.g., a rotary pressure exchanger), the first fluid (e.g., the high pressure input fluid) or the second fluid (e.g., the high pressure output fluid) can be used as a bearing fluid for radial bearings (load bearing) and axial bearings (load bearing). If the pressure difference between the high pressure input fluid and the high pressure output fluid reaches a threshold amount (e.g., very small), the bearing performance (e.g., stiffness and load capacity) may not change significantly due to the selection of either fluid. If the pressure difference between the high pressure input fluid and the high pressure output fluid reaches a threshold amount (e.g., very small), the high pressure output fluid can be used as a bearing fluid and mixing at the high pressure output port can be reduced. By supplying HPOUT fluid to the radial and axial bearings, the HPIN fluid can be isolated to prevent leakage through the bearing gaps from increasing the chance of mixing. By supplying high pressure output fluid to the radial and axial bearings, the high pressure input fluid can be isolated to prevent leakage from the bearing gaps from increasing the chance of mixing.

[0128] The high pressure output fluid can be used to feed the pressure exchanger radial bearings and fill the center bore of the rotor (e.g., FIG. 3I to FIG. 3J ).

[0129] refer to Fig. 3I According to certain embodiments, the PX 300 can include a fluid bypass 350 (e.g., a high pressure output fluid bypass). Fluid can enter between the housing 352 and the end cap 310 (e.g., a low pressure input end cap) and flow between the housing 352 and the sleeve 301 and through the openings in the sleeve 301 (e.g., to feed the pressure exchanger radial bearings and / or fill the center hole). In some embodiments, the fluid bypass 350 (e.g., a high pressure output fluid bypass) can bypass a gasket (e.g., an O-ring) between the housing 352 and the end cap 310 to feed the PX radial bearing through the hole in the sleeve.

[0130] refer to Figure 3J According to certain embodiments, PX 300 can include a fluid bypass 350 (e.g., a high pressure output fluid bypass) and / or a groove 354. Fluid bypass 350 can be a high pressure output fluid bypass of a gasket (e.g., an O-ring) and can feed the PX radial bearing through a hole in a sleeve. Groove 354 in end cap 310 (e.g., a high pressure output end cap) can be used to connect the high pressure output fluid to a central bore 356 (e.g., a central portion of rotor 320 between rotor 320 and the shaft).

[0131] In some embodiments, the length-to-depth (L / D) ratio and roundness of the conduits 322 are maximized. Mixing in the rotor conduits can be strongly related to turbulence, and the effects of turbulence can be significantly reduced by controlling the L / D ratio and the roundness of the conduits. Inserts can be added to the rotor 320 to achieve the desired conduit shape, achieve flow close to a "liquid plug," and reduce mixing in the rotor conduits.

[0132] The present invention can be used in a rotary pressure exchanger to reduce mixing of two fluids exchanging pressure energy.

[0133] The present disclosure may include features such as slopes (eg, kidney-shaped slopes), point faces 340, rounded corners, etc. (eg, to reduce blending).

[0134] The present invention reduces fluid mixing in pressure exchangers and improves overall energy consumption per unit volume (e.g., drinking water produced in a seawater reverse osmosis (SWRO) plant). The present disclosure is applicable to different pressure exchanger (e.g., isobaric pressure exchanger) applications, such as SWRO, sCO2, industrial wastewater, etc. The present disclosure may also be applicable to pressure exchanger architectures, such as pressure exchangers with rotor sleeves or sleeveless pressure exchangers (e.g., rotors with center posts) and electric or non-electric PXs. The present disclosure may be appropriately applied to different applications to reduce mixing of low pressure input with low pressure output.

[0135] Figures 4A to 4KComponents of a pressure exchanger 300 according to certain embodiments are shown (e.g., FIG. 2A to FIG. 2E PX 40, Figures 3A to 3P One or more of the pressure exchangers 300 in FIG. 1 ). Figures 4A to 4K Zhongyu Figures 1A to 2E and / or Figures 3A to 3P Features with similar names and / or reference numerals may include features similar to those in one or more of the figures. Figures 1A to 2E and / or Figures 3A to 3P The same or similar structure, material, function, etc. as shown in one or more figures. In some embodiments, Figures 4A to 4K One or more features of the PX 300 increase the efficiency of the PX 300.

[0136] In some embodiments, the pressure exchanger 300 includes a rotor 320 and an end cap 310. The rotor 320 is configured to exchange pressure between a first fluid at a first pressure and a second fluid at a second pressure. The rotor 320 forms a conduit 322 leading from a first distal end of the rotor 320 to a second distal end of the rotor 320.

[0137] In some embodiments, the radial edges of the kidney-shaped inlet and outlet of the end cap 310 may mate with the radial edges of the rotor 320 .

[0138] In some embodiments, the PX 300 uses streamlined (attic-style) spacers in the end caps 310 .

[0139] In some embodiments, non-metallic PVC spacers are used in PX 300 to handle axial thrust and avoid fretting corrosion between the ceramic end caps 310 and the metal interconnects.

[0140] In some embodiments, radial bearing clearance and axial bearing clearance are optimized for a target circumferential groove pressure.

[0141] In some embodiments, the ports of the end cap 310 are maximized to be substantially the same size as one conduit 322 plus one wall sealing area of ​​the rotor 320 to reduce differential pressure (DP) losses.

[0142] In some embodiments, the pressure load is substantially balanced on both rotor faces of the rotor 320 .

[0143] In some embodiments, the conduit shape of conduit 322 substantially matches the port (eg, kidney-shaped portion) of end cap 310 (eg, trapezoidal or triangular instead of circular).

[0144] In some embodiments, the end cap 310 (e.g., the first end cap) is disposed at a distal end (e.g., the first distal end) of the rotor 320, and the end cap 310 forms a high-pressure input port configured to provide a first fluid to the pipe 322 at a first pressure, and forms a low-pressure output port configured to receive the first fluid from the pipe 322 at a third pressure lower than the first pressure. One or more side walls (e.g., the radial side wall 314) of the end cap forming the high-pressure input port and / or the low-pressure output port are substantially planar (e.g., straight edge 401, not curved edge 402) (e.g., see Figure 4B In some embodiments, one or more side walls of the first end cap 310 forming the high pressure input port have a substantially straight edge 401 that substantially matches a corresponding substantially straight edge of the conduit 322 formed by the rotor 320 .

[0145] In some embodiments, the end cap 310 at the distal end (e.g., the second distal end) of the rotor 320 forms a low-pressure input port and a high-pressure output port, wherein the low-pressure input port is configured to provide the second fluid into the pipeline 322 at a second pressure, and the high-pressure output port is configured to receive the second fluid from the pipeline 322 at a fourth pressure higher than the second pressure.

[0146] In some embodiments, the end cap 310 (e.g., forming a high pressure input port and a low pressure output port, forming a low pressure input port and a high pressure output port) includes a substantially flat radial sidewall 314 (e.g., a non-curved radial sidewall 314), an inner sidewall 316 forming a port 312 (e.g., a high pressure input port, a high pressure output port), and an outer sidewall 318. The first substantially radial sidewall 314 may be disposed between the center of the end cap 310 and the periphery of the end cap 310. The inner sidewall 316 may be close to the center of the end cap 310, and the outer sidewall 318 may be close to the periphery of the end cap 310.

[0147] The rotor 320 may form concentric rows of tubes 322 (see, e.g., FIG. 4C to FIG. 4D ). The ratio of the number of concentric rows to the diameter of the rotor 320 in inches may be about 0.3 to about 0.45 (eg, about 0.375 to about 0.42). The rotor 320 may form at least three concentric rows of conduits 322 .

[0148] The pressure exchanger 300 may include a first interconnect 420 configured to provide a first fluid to a high pressure input port of the end cap 310, and a first interconnect 420 disposed in the end cap 310 and between the first interconnect and the high pressure input port (e.g., see Figure 4F ) of the first spacer 410 (see, for example, Figure 4EThe pressure exchanger 300 may include a second interconnect 420 configured to receive the first fluid from the low pressure output port of the end cap 310 and a second spacer 410, the second interconnect 420 being configured to receive the first fluid from the low pressure output port of the end cap 310, the second spacer 410 being disposed in the first end cap and between the low pressure output port and the second interconnect (e.g., see Figure 4F ). In some embodiments, the first spacer and / or the second spacer is a thermoplastic material. In some embodiments, the first spacer and / or the second spacer is polyvinyl chloride (PVC).

[0149] Figures 4G to 4H A PX 300 is shown according to certain embodiments. In some embodiments, the bearing stiffness of the PX 300 can be adjusted to center the rotor 320 and reduce leakage by optimizing the diametrical clearance 303 (e.g., radial clearance) and axial clearance 304 (e.g., axial bearing clearance, height difference between the sleeve and the rotor or between the center post and the rotor) to achieve a target circumferential groove pressure.

[0150] In the PX 300 (e.g., a rotary pressure exchanger), the rotor 320 is separated from the stator (e.g., end cap 310, sleeve 301) by a small clearance in the radial direction (e.g., diametrical clearance 303 between sleeve 301 and rotor 320 or between center post 302 and rotor 320) and in the axial direction (e.g., axial clearance 304 between end cap 310 and rotor 320). During operation, the rotor 320 is suspended in the clearance by the stiffness of the fluid films in the radial bearing and the axial bearing, which are generated by fluid dynamic and hydrostatic effects, respectively. For minimum bearing flow (leakage losses), the rotor 320 should have a minimum clearance, and the rotor 320 should be axially centered (e.g., with a minimum axial eccentricity). The minimum clearance is set by manufacturing and material stiffness limitations. Minimum eccentricity can be achieved by keeping the ratio between diametrical clearance 303 and axial clearance 304 within a narrow range of about 1 to about 3.5. This arrangement may provide an intermediate boost pressure (eg, an optimum intermediate boost pressure) between the two bearings (eg, in the circumferential boost chamber 305), thereby providing a low axial rotor eccentricity (eg, a minimum axial rotor eccentricity) and thereby minimizing leakage losses.

[0151] In some embodiments, the ratio of the diametric gap 303 (e.g., diametric gap, diametric gap, radial gap, etc.) to the axial gap 304 is about 1 to about 3.5. The diametric gap 303 is located between the rotor 320 and the sleeve 301 or between the rotor 320 and the center column 302. The axial gap 304 is located between the rotor 320 and the end cover 310.

[0152] Fig. 4I A rotor 320 is shown in accordance with certain embodiments. Figure 4JAn end cap 310 is shown in accordance with certain embodiments. Figure 4K FIG. 3 shows a PX 300 according to certain embodiments, wherein a rotor 320 is stacked on an end cap 310. Figures 4I to 4K As shown, the sealing angle 313 between the ports 312 of the end cover 310 may be at least the same as the sum of the conduit angle 323 and the conduit wall angle 324 of the rotor 320 .

[0153] In some embodiments, the angular spacing between the high pressure input port and the low pressure output port of the first end cover 310 substantially matches the corresponding angular spacing between the first front radial sidewall of the first conduit 322 of the rotor 320 and the second front radial sidewall of the second conduit 322 adjacent to the first conduit 322 .

[0154] The fluid flow in the pipeline of the rotary pressure exchanger may be unstable, and each rotation will accelerate and decelerate rapidly in both directions. This results in the need to cross the rotor loss pressure to overcome the fluid inertia. In addition to reducing the rotor speed (which may cause increased mixing), this inertial pressure loss can also be minimized by maximizing the flow area of ​​the kidney-shaped portion (e.g., the port 312 of the end cap 310). This results in lower acceleration under the same flow rate, thereby reducing inertial pressure loss. In order to prevent direct communication from one kidney-shaped portion to the next kidney-shaped portion (e.g., between ports 312), the minimum sealing angle of the end cap 310 can be kept substantially equal (e.g., equal) to the angular spacing (pipeline angle 323 plus pipeline wall angle 324) between the pipeline 322.

[0155] The present invention may optimize efficiency, mixing, cavitation, sound, and cost of a pressure exchanger 300 (eg, an isobaric pressure exchanger).

[0156] Traditionally, features that attempt to increase efficiency by increasing travel distance ultimately increase mixing within the pressure exchanger. The present invention can maximize efficiency over a similar travel distance as a conventional pressure exchanger without negatively impacting mixing performance (e.g., by maintaining the same amount of mixing, reducing mixing, etc.).

[0157] The present invention can be used in different pressure exchanger (e.g., isobaric pressure exchanger) applications (e.g., using pressure exchangers for energy recovery), such as SWRO, sCO2, industrial wastewater, etc. The present invention can be used in different pressure exchanger architectures, such as pressure exchangers with rotor sleeves or sleeveless pressure exchangers (e.g., rotors with a center post) and electric or non-electric pressure exchangers.

[0158] The present disclosure can be used to reduce fluid inertial pressure losses using the radial edges of the inlet and outlet of the port 312 (e.g., kidney-shaped portion). Conventionally, a large amount of pressure loss in the rotor 320 occurs due to the sudden acceleration and deceleration of the flow within the rotor 320. The pressure difference of the flow within the duct 322 that accelerates the rotor 320 (e.g., the pressure lost when accelerating the flow within the rotor duct expressed as dQ / dt) can be given as shown in Equation 1.

[0159] Equation 1: ΔP fluid_inertia =(ρ fluid *L duct / A duct )*(dQ duct / dt)

[0160] Q duct is the flow rate passing through each pipe 322.

[0161] dQ duct / dt is the change in flow rate in conduit 322 (eg, acceleration, deceleration).

[0162] L duct is the length of pipeline 322.

[0163] A duct is the area of ​​the pipe 322.

[0164] dt is the time at which the conduit 322 opens to the port 312 (eg, kidney).

[0165] dP fluid_inertia (For example, ΔP fluid_inertia ) is the fluid pressure loss due to acceleration and / or deceleration.

[0166] Since dt=ω*dθ, Equation 1 can be rewritten as Equation 2 (eg, pressure loss during accelerated flow in the rotor duct represented by dQ / dθ).

[0167] Equation 2: ΔP fluid_inertia =(ρ fluid *L duct / A duct / ω)*(dQ duct / dθ)

[0168] According to Equation 2, d can be reduced by reducing the dQ / dθ term. Pfluid_inertia (For example, ΔP fluid_inertia ).

[0169] Conventional end caps may have curved edge sidewalls that form ports. In some embodiments, the end cap 310 of the present disclosure includes a substantially flat radial sidewall 314 (e.g., a radial edge end cap 310). Using radial edge ports can increase the effective kidney angle of the middle and outermost conduits compared to curved edge ports (e.g., an increase of about 26% for the outermost conduits). The radial edge of the port 312 can match the trapezoidal shape of the port 312 to the trapezoidal shape of the conduits 322 of the rotor 320.

[0170] In some embodiments, fluid inertial pressure losses can be reduced by selecting the number and shape of rotor ducts to maximize rotor flow. In rotor 320, duct passages help transport fluid from inlet to outlet. Most of the pressure loss may occur in rotor 320. Increasing the rotor duct flow area can reduce pressure losses without negatively affecting mixing. The constraint can be that the stress should be lower than the material strength of rotor 320.

[0171] In some embodiments, the rotor 320 has a trapezoidal duct 322 with heavily rounded corners to utilize the available area by maximizing the duct flow area and preventing high stress concentrations (see, e.g., Figure 4D ).

[0172] In some embodiments, the number of concentric rows is selected to maximize the total conduit flow area while minimizing the maximum conduit area and meeting material strength criteria. This also helps achieve an effective hydraulic diameter similar to an equivalent circle (e.g., preventing high aspect ratio conduits).

[0173] In some embodiments, the rotor 320 has an odd number of conduits 322 (eg, an even number of conduits). This prevents the conduits 322 from opening to symmetrically opposite ports 312 at the same time, thereby reducing noise and vibration of the pressure exchanger 300.

[0174] In some embodiments, rotor 320 has staggered conduits, which reduces the total amount of conduit volume that is pressurized and / or depressurized while reducing noise and vibration in the pressure exchanger.

[0175] In some embodiments, the rotor 320 has at least two concentric rows of tubes 322. In some embodiments, the rotor 320 has at least three concentric rows of tubes 322.

[0176] In some embodiments, spacers (eg, loft-style spacers, streamlined spacers) are used to provide flow into the high-pressure output port and direct the low-pressure output port to minimize exit shock losses due to flow separation.

[0177] The flow leaving the rotor conduit and entering the outlet has axial and tangential velocity components. The axial velocity component may not change too much with the radius of the rotor 320. The tangential component scales linearly with the radius. The outlet port (e.g., low pressure output port, high pressure output port) wall can be designed so that the pipeline flow leaves smoothly through the port 312 without separation. The port sidewall (e.g., kidney-shaped wall) can be configured to adapt to the different ratios of the tangential and axial components of the speed and the radius. By preventing the flow separation at the outlet, the pressure difference loss and mixing loss are reduced. The mixing zone can be the pipeline outlet at the outlet (e.g., outlet kidney-shaped portion) closest to the end cap 310.

[0178] Spacers 410 (e.g., streamlined spacers, streamlined loft-style spacers) can be used to reduce pressure losses. In some embodiments, spacers can be used to eliminate the use of thrust rings and / or reduce pressure losses due to abrupt changes in area between the low pressure port and the interconnect. Spacers 419 (e.g., loft-style spacers) can be used to simplify flow and avoid pressure losses due to abrupt changes in area. In some embodiments, PX 300 can include spacers 410 having a loft shape that transitions from a circular shape of the interconnect to a non-circular shape of a corresponding port of first end cap 310.

[0179] A non-metallic spacer 410 (e.g., a non-metallic streamlined spacer) can be used to handle axial thrust and avoid fretting corrosion between the ceramic end cap 310 and the metal interconnect (e.g., an end cap 310 used with an interconnect without the spacer 410 may have fretting corrosion issues). The spacer 410 (e.g., a streamlined spacer) can be made of polyvinyl chloride (PVC) (e.g., to eliminate the need for a thrust ring used in a conventional pressure exchanger). The thrust ring transfers the axial force from the ceramic barrel to the housing through a sealing plate and a bearing plate. A spacer 419 made of PVC (e.g., injection molded to reduce cost) is used as a buffer material between the metal low pressure interconnect and the ceramic end cap 310. This allows the low pressure interconnect material to be freely selected as any material that is compatible with the fluid of the application (e.g., a seawater application) (e.g., 2507 Super Duplex, AL6XN, etc.) and is suitable for the rated pressure.

[0180] In some embodiments, the front radial sidewalls and rear radial sidewalls of the low pressure output port and the high pressure output port are not axial. The front radial sidewalls and rear radial sidewalls of the low pressure output port and the high pressure output port can be inclined at an angle substantially proportional to the number of revolutions per minute of the rotor. The angle can be about 30 degrees to about 70 degrees.

[0181] Fluid acceleration and deceleration (e.g., fluid inertia) losses can be reduced by increasing the effective angular range of the port by making the port edges radial (e.g., substantially flat radial sidewalls 314), thereby increasing the time to fill the rotor duct; and minimizing the peak fluid velocity (e.g., V_max) within the rotor 320 by maximizing the rotor flow area while satisfying stress and manufacturing constraints.

[0182] In some embodiments, the spacers 410 (eg, loft-style spacers) help reduce the amount of super duplex or stainless steel metal and aluminum oxide (Al 2 O 3 ) and can simplify the flow in and out of the port, thereby reducing frictional fluid losses. This can avoid the use of more exotic materials for the interconnect 420, such as titanium. The spacer (e.g., a loft-style spacer) can combine the three functions of simplifying flow and reducing fluid losses due to sudden changes in area, acting as a flexible material between the metal interconnect 420 and the brittle ceramic, and can also handle the net thrust of the barrel due to pressure imbalance. This may prevent the use of a separate thrust ring.

[0183] Features such as trapezoidal shaped conduits 322, an odd number of conduits 322, at least three concentric rows of conduits 322 while keeping individual conduit volume to a minimum, and / or the like may be used to maximize rotor efficiency.

[0184] FIG. 5A to FIG. 5J Components of a pressure exchanger 300 according to certain embodiments are shown (e.g., FIG. 2A to FIG. 2E PX 40, Figures 3A to 4K One or more of the pressure exchangers 300 in FIG. 1 ). FIG. 5A to FIG. 5J Zhongyu Figures 1A to 2E and / or Figures 3A to 4K Features with similar names and / or reference numerals may include features similar to those in one or more of the figures. Figures 1A to 2E and / or Figures 3A to 4K The same or similar structure, material, function, etc. as shown in one or more figures. In some embodiments, FIG. 5A to FIG. 5J One or more features of the PX 300 reduce mixing of fluids within the PX 300 .

[0185] The pressure exchanger includes a rotor 320 and an end cap 310. The rotor 320 is configured to exchange pressure between a first fluid at a first pressure and a second fluid at a second pressure. The rotor 320 forms a conduit 322 leading from a first distal end of the rotor 320 to a second distal end of the rotor 320.

[0186] The end cap 310 (e.g., disposed at the distal end of the rotor 320) forms a high-pressure input port and a low-pressure output port, wherein the high-pressure input port is configured to provide a first fluid into the pipeline 322 at a first pressure, and the low-pressure output port is configured to receive the first fluid from the pipeline 322 at a third pressure lower than the first pressure.

[0187] In some embodiments, the PX 300 includes a point surface at the low pressure input opening instead of the low pressure output opening (eg, so that the high pressure conduit is depressurized at the low pressure input, where the pressure is higher than the low pressure output).

[0188] In some embodiments, the conduit is opened to the spot face at the conduit ID rather than the conduit OD (eg, the angle of the spot face edge is adjusted or the spot face wall is curved toward or away from the conduit).

[0189] In some embodiments, the radial extent is shorter than the point surface of the conduit 322 (eg, reducing the diameter of the conduit into the kidney, reducing tangential velocity and cavitation potential).

[0190] In some embodiments, the PX 300 includes a split point face (e.g., at one or more end caps 310). There may be one split point face per row of pipes or split points face may be combined for a group of pipes. This may adjust the point face for each row of pipes 322 separately.

[0191] In some embodiments, the PX 300 has optimized tube volumes and staggered tubes in adjacent rows.

[0192] In some embodiments, the spot geometry can have: (a) a substantially constant depth spot; (b) a substantially linear depth spot; (c) an outgoing EC (end cap); and / or (d) a pre-pressurized hole.

[0193] In some embodiments, the spot angle range, radial range, and slope angle may be optimized for different fluid and operating conditions.

[0194] In some embodiments, rotor 320 may include a chamfer on the trailing edge of the rotor duct wall to increase the discharge coefficient (Cd).

[0195] The end cap 310 (e.g., disposed at the distal end of the rotor 320) forms a low-pressure input port configured to provide the second fluid to the conduit 322 at a second pressure and a high-pressure output port configured to receive the second fluid from the conduit 322 at a fourth pressure higher than the second pressure (e.g., Figure 5B The end cover 310 forms a first point surface 340 near the low-pressure input port and a second point surface 340 near the high-pressure output port.

[0196] In some embodiments, the end cap 310 forms a low-pressure output port but does not form a point surface 340 near the low-pressure output port, and forms a high-pressure input port but does not form a point surface 340 near the high-pressure input port (e.g., Figure 5A ).

[0197] In some embodiments, for SWRO, a point surface 340 is formed near the low pressure input port and a point surface 340 is formed near the high pressure output port to minimize mixing at the high pressure output port (e.g., a point surface is not formed at the low pressure output because the low pressure output pressure is below the threshold pressure, which may cause cavitation).

[0198] In some embodiments, for refrigeration, a point surface 340 is formed near the low pressure output port and a point surface 340 is formed near the high pressure output port to reduce mixing at the low pressure output port and the high pressure output port (e.g., the low pressure output pressure is higher than the threshold pressure, so the risk of cavitation is lower).

[0199] In some embodiments, the end cover 310 forms a chamfer 311 at the low pressure input port, and the chamfer 311 is configured to change the corresponding angle of the first point surface 340 of each row of concentric pipes of the rotor 320 (for example, see Figure 5C The chamfer 311 at the low-pressure input port is configured to change the corresponding angle of each pipe exposed to the point surface to change the pressurization amount (eg, pressurization and / or decompression) of different rows of pipes.

[0200] In some embodiments, the radial extent of the first point surface 340 is shorter than the radial extent of the corresponding conduit 322 formed by the rotor 320 (e.g., see FIG. 5D to FIG. 5F ).

[0201] In some embodiments, the first point surface 340 (eg, a split point surface) includes a first recess associated with the first concentric row of pipes 322 and a second recess associated with the second concentric row of pipes 332 (eg, see Figure 5G ).

[0202] In some embodiments, rotor 320 forms staggered concentric rows of tubes 322 (see, e.g., FIG. 5H to FIG. 5I ).

[0203] In some embodiments, the duct opening of the rotor 320 to the corresponding end cap duct is within the inner duct diameter by adjusting the angle of the duct edge or the curved duct wall relative to the duct opening.

[0204] In some embodiments, the end cap 310 (e.g., forming a low-pressure input port and a high-pressure output port) forms a pre-pressurization hole near the first point surface 340. The pre-pressurization hole is configured to perform one or more of pressurization or depressurization on at least a portion of the pressure exchanger near the end cap 310 (e.g., forming a low-pressure input port and a high-pressure output port).

[0205] Figure 5J A rotor according to some embodiments is shown. In some embodiments, the rotor 320 forms a chamfer on the trailing edge rotor duct wall. The chamfer of the trailing edge of the rotor duct wall may increase the discharge coefficient (Cd) of the rotor 320.

[0206] Adding chamfers or fillets at the trailing edge of the rotor conduit wall can increase the effective area (discharge coefficient) of the depressurized jet from the high pressure conduit to the low pressure kidney-shaped portion. The increase in effective area reduces the jet velocity, thereby reducing the local fluid static pressure, which may reduce the possibility of cavitation. Similarly, chamfers or fillets can be adopted on the leading edge of the rotor conduit wall to increase the effective area (discharge coefficient) of the pressurized jet from the kidney-shaped piece to the pipeline 322. In certain embodiments, these features also reduce noise and vibration by reducing the peak jet velocity.

[0207] The present invention may provide cavitation, noise, and vibration control in a pressure exchanger 300 (eg, a rotary isobaric pressure exchanger).

[0208] In a pressure exchanger (e.g., a rotary isobaric pressure exchanger), a rotating conduit carries a high-pressure fluid from a high-pressure kidney-shaped portion (port) to a low-pressure kidney-shaped portion, and also carries a low-pressure fluid from a low-pressure kidney-shaped portion to a high-pressure kidney-shaped portion. Whenever the conduit fluid approaches a group of kidney-shaped portions, the conduit fluid is rapidly pressurized or depressurized. The frequency and rate of pressurization and / or depressurization depend on the rotor revolutions per minute (RPM), the number of pressure exchange cycles per revolution, and the pressure difference between the high-pressure kidney-shaped portion and the low-pressure kidney-shaped portion. Rapid pressurization and / or depressurization cause high-speed fluid jets to produce noise, and produce flow and pressure pulsations, thereby increasing vibration levels. If the local fluid pressure (e.g., due to the high speed of the local fluid pressure) drops below the vapor pressure at the temperature, this will also produce vapor bubbles. When vapor bubbles travel to higher pressure regions, these vapor bubbles break, causing gaps to form, thereby causing surrounding fluids to surge in, producing extremely high local pressure spikes. If these situations occur next to a solid wall, they will produce pitting damage, and accumulate over time. This can cause cavitation, which amplifies noise and vibration levels.

[0209] The point surface 340 (e.g., channel, notch, recess) can be used to control the rate of pressurization or depressurization of the rotor conduit 322, thereby reducing noise, vibration and the risk of cavitation damage. Including the point surface 340 in the present disclosure improves efficiency without adversely affecting other performance parameters of the pressure exchanger such as mixing or efficiency.

[0210] In some embodiments, the pressure exchanger 300 may have a point face 340 at the low pressure input port and no point face 340 at the low pressure output port.

[0211] When the pipeline 322 carrying high pressure fluid approaches the low pressure input port and the low pressure output port, the pressure reduction rate of the pipeline fluid can be controlled by combining the point surface 340 at the inlet of the low pressure input port or the inlet of the low pressure output port or both inlets. Due to the viscosity and inertial losses in the pipeline 322 of the rotor 320, the low pressure output port pressure is lower than the low pressure input port pressure. In some embodiments (e.g., a typical SWRO device), when the pressure exchanger 300 is used as an energy recovery device, the low pressure output pressure can be about half of the low pressure input pressure. Therefore, by positioning the point surface 340 of a given geometry at the low pressure input inlet rather than the low pressure output inlet, the pipeline pressure reduction occurs with a lower pressure gradient (e.g., a lower injection velocity), and the cavitation possibility, noise and vibration levels can be lower.

[0212] In some embodiments, the pressure exchanger 300 includes a point surface 340 at a low pressure input port (eg, in place of a low pressure output port) and / or a high pressure output port (eg, in place of a high pressure input port).

[0213] When the pipeline 322 carrying low pressure fluid approaches high pressure, the rate of depressurization of the pipeline fluid can be controlled by incorporating a point surface 340 at the inlet of the high pressure input port, at the inlet of the high pressure output port, or at both inlets. Due to viscosity and inertial losses in the rotor pipeline, the high pressure output port pressure is lower than the high pressure input port pressure. Therefore, by positioning the point surface 340 of a given geometry at the high pressure output inlet rather than the high pressure input inlet, pipeline depressurization occurs at a lower pressure gradient (e.g., lower injection velocity) and can result in lower cavitation potential, noise and vibration levels.

[0214] In some embodiments, pipeline 322 is opened to point face 340 at pipeline inner diameter (ID) rather than pipeline outer diameter (OD). Fluid in pipeline 322 experiences rotational motion, therefore, the tangential component of fluid velocity increases linearly with radius. In addition, due to the centrifugal head caused by fluid centripetal acceleration, the fluid pressure in pipeline increases from pipeline inner diameter to outer diameter. When the pipeline carrying high pressure fluid approaches the point face 340 at the entrance of low pressure kidney-shaped portion, depressurization is carried out by spraying along point face 340 from pipeline inner diameter rather than pipeline outer diameter. This can be realized by adjusting the relative angle of point face 340 and pipeline 322 when approaching. This can also be realized by bending pipeline wall and / or point face 340 wall when approaching or away from pipeline 322.

[0215] In some embodiments, the chamfer at the low pressure input port (e.g., the low pressure input opening) can change the angle of the point surface 340 of different rows of pipes 322. In some embodiments, the point surface 340 can be conformal to the pipe 322. In some embodiments, the radial extent of the point surface 340 can be shorter than the radial extent of the pipe 322. Both the tangential velocity and pressure of the fluid in the rotor pipe can increase with increasing radial coordinates. One way to prevent injection and pressure drop at the highest radius is to shorten the radial extent of the point surface 340 (e.g., the point surface 340 has a lower radial extent that is shorter than the radial extent of the pipe 322).

[0216] In some embodiments, the end cap 310 forms split point faces 340 (eg, one for each row of tubes or one for each group of rows).

[0217] The pressure exchanger 300 may include multiple rows of pipes 322 formed by the rotor 320. Each row may have different pipe geometries, resulting in different volumes of fluid that need to be pressurized and / or depressurized. The fluid tangential velocity and pressure may vary from one row to another. Compared with a single point surface 340 covering all rows, the point surface 340 adjusted for each row of pipes 322 may be more effective in reducing noise, vibration, and cavitation. In some embodiments, a single point surface 340 with different geometries (e.g., for ramp angles) along the radius is used.

[0218] In some embodiments, the tube volume can be optimized (eg, one or more rows of trapezoidal tubes). In some embodiments, the tubes in adjacent concentric rows can be staggered.

[0219] Dividing the rotor ducts into multiple rows rather than a single row, while keeping the total rotor duct volume essentially the same, may result in smaller duct sizes. By staggering the duct rows so that each row of ducts approaches the kidney at a different time, individual ducts in a row of ducts can be depressurized and / or pressurized at a time. This allows for a shallower slope at the point face 340 and a reduced pressure gradient across the duct wall.

[0220] Staggering the rows of pipes can make flow and pressure more uniform (eg, minimizing the volume of a single pipe), thereby reducing vibration levels.

[0221] In some embodiments, various point surface 340 geometries may be used and may be combined with one or more pre-pressurization or depressurization holes.

[0222] In some embodiments, one or more of the angular extent, radial extent, and / or slope of the spot face 340 may be optimized for different fluids.

[0223] The depth, radial, and angular extent of the spot face 340 may depend on the geometry of the pressure exchanger (e.g., pipe size, pipe wall thickness, etc.), pressure exchanger flow rate, high pressure / low pressure ratio, rotor RPM, fluid type, etc. In some embodiments, the higher the compressibility of the fluid, the larger the volume of the spot face 340 to provide pressurization and / or depressurization of the rotor pipe.

[0224] The present invention can be used to reduce cavitation potential, noise and / or vibration levels. In addition to reducing RPM, reducing the number of pressure exchange cycles (including pre-pressurization and / or depressurization holes, etc.), the present disclosure can also use point surface 340.

[0225] The present invention can reduce noise generation, vibration levels and cavitation potential in energy recovery applications using pressure exchangers.

[0226] The present invention can be used in pressure exchangers for energy recovery, such as seawater reverse osmosis, transcritical carbon dioxide refrigeration / heat pumps, industrial wastewater, etc.

[0227] The foregoing description presents many 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. However, it will be apparent to those skilled in the art that at least some embodiments of the present disclosure may be implemented without these specific details. In other cases, well-known components or methods are not described in detail, or are presented in a simple block diagram format to avoid unnecessary confusion of the present disclosure. Therefore, the specific details set forth are merely exemplary. Specific embodiments may differ from these exemplary details and may still be expected to be within the scope of the present disclosure.

[0228] References throughout this specification to "one embodiment" or "an embodiment" mean that the specific features, structures or characteristics associated with the description of the embodiment are included in at least one embodiment. Therefore, phrases appearing in various places throughout this specification in "one embodiment" or "in an embodiment" do not necessarily all refer to the same embodiment. In addition, the term "or" is intended to represent an inclusive "or" rather than an exclusive "or". When the terms "approximately", "substantially" or "roughly" are used herein, this means that the nominal values ​​presented are accurate to within ±10%. In addition, the terms "first", "second", "third", "fourth", etc. used herein are meant to be labels that distinguish between different elements and do not necessarily have ordinal meanings according to their numerical names.

[0229] As used herein, the terms "above," "below," "between," "disposed on," and "on" refer to the relative position of one material layer or component with respect to other layers or components. For example, a layer disposed on, over, or below another layer may be in direct contact with the other layer, or may have one or more intervening layers. Additionally, a layer disposed between two layers may be in direct contact with the two layers, or may have one or more intervening layers. Similarly, unless expressly stated otherwise, a feature disposed between two features may be in direct contact with the adjacent feature, or may have one or more intervening layers.

[0230] Although the operations of the methods herein are shown and described in a particular order, the order of operations of each method can be changed so that certain operations can be performed in reverse order, or so that certain operations can be performed at least partially simultaneously with other operations. In another embodiment, instructions or sub-operations of different operations can be performed in an intermittent and / or alternating manner. In one embodiment, multiple metal bonding operations are performed as a single step.

[0231] It should be understood that the above description is intended to illustrate rather than to limit. After reading and understanding the above description, many other embodiments will be apparent to those skilled in the art. Therefore, the scope of the present disclosure should be determined with reference to the attached claims and the full range of equivalents covered by each claim.

Claims

1. A pressure exchanger, include: a rotor configured to rotate to exchange pressure between a first fluid at a first pressure and a second fluid at a second pressure, wherein the rotor forms a conduit leading from a first distal end of the rotor to a second distal end of the rotor, wherein the rotor forms a chamfer on a wall of the trailing edge rotor conduit; a first end cap disposed at a first distal end of the rotor, wherein the first end cap forms a high pressure input port configured to provide a first fluid into the conduit at a first pressure, and wherein the first end cap forms a low pressure output port configured to receive the first fluid from the conduit at a third pressure lower than the first pressure; and a second end cap disposed at a second distal end of the rotor, wherein the second end cap forms a low-pressure input port configured to provide a second fluid into the conduit at a second pressure and a high-pressure output port configured to receive the second fluid from the conduit at a fourth pressure higher than the second pressure.

2. The pressure exchanger according to claim 1, It is characterized in that The second end cover forms a first point surface close to the high-voltage output port.

3. The pressure exchanger according to claim 2, It is characterized in that The pressure exchanger forms a second point surface near the low-pressure input port of the second end cover, but does not form a point surface near the low-pressure output port of the first end cover, so as to reduce the pressure of the high-pressure pipeline of the rotor at the low-pressure input port.

4. The pressure exchanger according to claim 1, It is characterized in that The first end cover forms the high-pressure input port, but does not form a point surface close to the high-pressure input port.

5. The pressure exchanger according to claim 2, It is characterized in that The second end cover forms a chamfer at the low-pressure input port, and the chamfer is configured to change a corresponding angle of the first point surface for each concentric row of pipes of the rotor.

6. The pressure exchanger according to claim 5, It is characterized in that The chamfer at the low-pressure input port is configured to change the angle at which each pipe is exposed to the first point surface to change the pressurization amount of different rows of pipes.

7. The pressure exchanger according to claim 2, It is characterized in that The radial extent of the first point surface is smaller than the radial extent of the corresponding duct formed by the rotor to reduce the diameter of the rotor duct opening to the end cover port, thereby reducing the tangential velocity and the possibility of cavitation.

8. The pressure exchanger according to claim 2, It is characterized in that The first point surface includes a first recess associated with a first concentric row of tubes and a second recess associated with a second concentric row of tubes.

9. The pressure exchanger according to claim 1, It is characterized in that The rotor forms staggered concentric rows of tubes.

10. The pressure exchanger according to claim 1, It is characterized in that By adjusting the angle of the point surface edge or the curved point surface wall relative to the pipeline opening, the pipeline opening of the rotor to the corresponding end cover point surface is within the inner pipeline diameter.

11. A pressure exchanger, include: a rotor configured to rotate to exchange pressure between a first fluid at a first pressure and a second fluid at a second pressure, wherein the rotor forms a conduit leading from a first distal end of the rotor to a second distal end of the rotor, wherein the rotor forms at least two concentric rows of conduits, including a first concentric row of conduits and a second concentric row of conduits; and A first end cover is disposed at the first distal end of the rotor, wherein the first end cover forms a first port, a second port, and a split point surface proximate the first port, wherein the split point surface includes a first recess associated with the first concentric row of pipes and a second recess associated with the second concentric row of pipes.

12. The pressure exchanger according to claim 11, It is characterized in that Corresponding tubes in the first concentric row and the second concentric row are staggered.

13. The pressure exchanger according to claim 11, It is characterized in that The radial extent of the split point surface is smaller than the radial extent of the corresponding pipeline formed by the rotor.

14. The pressure exchanger according to claim 11, It is characterized in that The pressure exchanger forms a split point surface near the low-pressure input port, but does not form a point surface near the low-pressure output port, so as to reduce the pressure of the high-pressure pipeline of the rotor at the low-pressure input port.

15. The pressure exchanger according to claim 11, It is characterized in that The rotor forms a chamfer on the rear edge rotor duct wall.

16. The pressure exchanger according to claim 11, It is characterized in that The rotor forms at least three concentric rows of pipes, including the first concentric row of pipes, the second concentric row of pipes, and a third concentric row of pipes.

17. A pressure exchanger, include: a rotor configured to rotate to exchange pressure between a first fluid at a first pressure and a second fluid at a second pressure, wherein the rotor forms a conduit leading from a first distal end of the rotor to a second distal end of the rotor, wherein the rotor forms at least two concentric rows of conduits, including a first concentric row of conduits and a second concentric row of conduits; and A first end cap is disposed at a first distal end of the rotor, wherein the first end cap forms a first port, a second port, and a point face, wherein the first end cap forms a chamfer at the first port, the chamfer is configured to change a corresponding angle of the point face of each concentric row of pipes of the rotor, and wherein the chamfer at the first port is configured to change an angle at which each pipe is exposed to the point face to change the pressurization amount of pipes in different rows.

18. The pressure exchanger according to claim 17, It is characterized in that The rotors form staggered concentric rows of tubes.

19. The pressure exchanger according to claim 17, It is characterized in that The pressure exchanger forms a point surface near the low-pressure input port, but does not form a point surface near the low-pressure output port, so as to reduce the pressure of the high-pressure pipeline of the rotor at the low-pressure input port.

20. The pressure exchanger according to claim 17, It is characterized in that The rotor forms a chamfer on the rear edge rotor duct wall.

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