Sealing and Aligning Cartridges in Pressure Exchangers

Abstract

The pressure exchanger includes a rotor configured to exchange pressure between a first fluid and a second fluid, a sleeve disposed about the rotor, and a first end cover disposed at a first distal end of the rotor, and further includes one or more first sealing elements configured to prevent leakage between the sleeve and the first end cover.

Description

[Technical field]

[0001] FIELD OF THE DISCLOSURE The present disclosure relates to pressure exchangers, and more particularly to sealing and alignment of cartridges in pressure exchangers. [Background technology]

[0002] Some systems use fluids at various pressures. Some systems use components to increase the pressure of the fluid.

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

[0004] [Figure 1A] 1 is a schematic diagram of a fluid processing system including a hydraulic energy transfer system, in accordance with certain embodiments. [Figure 1B] 1 is a schematic diagram of a fluid processing system including a hydraulic energy transfer system, in accordance with certain embodiments. [Figure 1C] 1 is a schematic diagram of a fluid processing system including a hydraulic energy transfer system, in accordance with certain embodiments. [Figure 1D] 1 is a schematic diagram of a fluid processing system including a hydraulic energy transfer system, in accordance with certain embodiments. [Figure 2A] FIG. 2 is an exploded perspective view of a pressure exchanger (PX) according to a particular embodiment. [Figure 2B] FIG. 2 is an exploded perspective view of a pressure exchanger (PX) according to a particular embodiment. [Figure 2C] FIG. 2 is an exploded perspective view of a pressure exchanger (PX) according to a particular embodiment. [Figure 2D] FIG. 2 is an exploded perspective view of a pressure exchanger (PX) according to a particular embodiment. [Figure 2E] FIG. 2 is an exploded perspective view of a pressure exchanger (PX) according to a particular embodiment. [Figure 3A] 1 illustrates a PX according to a specific embodiment. [Figure 3B] 1 illustrates a PX according to a specific embodiment. [Figure 3C] 1 illustrates a PX according to a specific embodiment. [Figure 3D] 1 illustrates a PX according to a specific embodiment. [Figure 3E] 1 illustrates a PX according to a specific embodiment. [Figure 3F] 1 illustrates a PX according to a specific embodiment. [Figure 3G] 1 illustrates a PX according to a specific embodiment. [Figure 3H] 1 illustrates a PX according to a specific embodiment. [Figure 3I] 1 illustrates a PX according to a specific embodiment. [Figure 3J] 1 illustrates a PX according to a specific embodiment. [Figure 3K] 1 illustrates a PX according to a specific embodiment. [Figure 3L] 1 illustrates a PX according to a specific embodiment. [Figure 3M] 1 illustrates a PX according to a specific embodiment. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0005] The embodiments described herein relate to sealing and alignment of a cartridge at the PX.

[0006] A system may use fluids at different pressures. A fluid may be supplied to a system at a lower pressure and one or more portions of the system may operate at a higher pressure. A system may include a closed loop where different fluid pressures are maintained in different portions of the loop. Such systems may include hydraulic fracturing (e.g., fracking or fracing) systems, desalination systems, refrigeration systems, heat pump systems, energy generation systems, mud pump systems, slurry pump systems, industrial fluid systems, wastewater systems, fluid transport systems, etc. Pumps or compressors may be used to increase the pressure of the fluids in such systems.

[0007] Traditionally, systems (e.g., refrigeration systems, heat pump systems, reversible heat pump systems, water systems, etc.) use pumps or compressors to increase the pressure of a fluid (e.g., refrigeration fluids such as carbon dioxide (CO2), R-744, R-134a, hydrocarbons, hydrofluorocarbons (HFCs), hydrochlorofluorocarbons (HCFCs), ammonia (NH3), refrigerant mixtures, R-407A, R-404A, etc.). Traditionally, separate pumps or compressors mechanically coupled to a motor are used to increase the pressure of the fluid in any part of the system, including increasing the fluid pressure. Pumps and compressors, especially those that operate with large pressure differentials (e.g., causing large pressure increases in the fluid), require large amounts of energy. Thus, traditional systems consume large amounts of energy to increase the pressure of the fluid (through the pump or compressor driven by the motor). Additionally, traditional fluid transfer systems reduce the pressure of the fluid through an expansion valve. Traditional systems inefficiently increase the pressure of the fluid and reduce the pressure of the fluid when operating in a loop. This is wasteful in terms of the energy used to run conventional systems (e.g., the energy used to repeatedly increase the pressure of a refrigerated fluid to raise or lower the temperature of the surrounding environment).

[0008] Traditionally, systems (e.g., refrigeration systems, heat pump systems, reversible heat pump systems, water systems, etc.) have components that may be misaligned and / or unsealed. Misalignment can cause the system to operate inefficiently. Unsealing can allow system fluids to leak into the environment or allow surrounding fluids to enter the system. This can be harmful to the health of people around the system, can lead to waste of system fluids, can cause inefficient operation of the system, and / or can allow foreign objects to enter the system and damage system components.

[0009] The systems, apparatus, and methods of the present disclosure provide solutions to these and other shortcomings of conventional systems. The present disclosure provides a PX for use in a system (e.g., a fluid processing system, a heat transfer system, a refrigeration system, a heat pump system, a cooling system, a heating system, etc.). In the system, the PX may be configured to exchange pressure between a first fluid (e.g., a high-pressure portion of the refrigeration fluid in a refrigeration cycle) and a second fluid (e.g., a low-pressure portion of the refrigeration fluid in a refrigeration cycle). The PX receives the first fluid (e.g., a portion of the high-pressure refrigeration fluid) via a first inlet (e.g., a high-pressure inlet) and receives the second fluid (e.g., a portion of the low-pressure refrigeration fluid) via a second inlet (e.g., a low-pressure inlet). The first fluid may be at a higher pressure than the second fluid when it enters the PX. The PX exchanges pressure between the first fluid and the second fluid. The first fluid exits the PX via a first outlet (e.g., a low-pressure outlet) and the second fluid exits the PX via a second outlet (e.g., a high-pressure outlet). The second fluid may be at a higher pressure than the first fluid when it exits the PX (eg, pressure has been exchanged between the first and second fluids).

[0010] In some embodiments, the PX comprises a sleeve disposed about the rotor, a first end cover disposed at a first distal end of the rotor, and a second end cover disposed at a second distal end of the rotor, the PX further comprising one or more first sealing elements configured to prevent leakage between the sleeve and the first end cover, and one or more second sealing elements configured to prevent leakage between the sleeve and the second end cover.

[0011] In some embodiments, the PX comprises alignment elements configured to align the first end cover and the second end cover, the alignment elements may comprise a first alignment element radially inserted into the first end cover and a second alignment element radially inserted into the second end cover.

[0012] In some embodiments, the PX comprises a pressure exchanger seal ring assembly disposed about an interface between an end cover of the pressure exchanger and a sleeve of the pressure exchanger to prevent leakage between the sleeve and the end cover. The pressure exchanger seal ring assembly may comprise a seal ring, a first gasket, a second gasket, a first pin and / or a second pin. The seal ring may comprise an inner surface forming a first groove and a second groove. The first gasket is configured to be disposed in the first groove and the second gasket is configured to be disposed in the second groove. The first gasket will interface with an end cover outer surface of the end cover and the second gasket will interface with a sleeve outer surface of the sleeve.

[0013] The first pin has a first distal end configured to be disposed in an upper seal ring recess defined by an upper surface of the seal ring and a second distal end configured to be radially inserted into an end cover recess defined by an end cover outer surface of the end cover, and the second pin has a first distal end configured to be disposed in a lower seal ring recess defined by a lower surface of the seal ring and a second distal end configured to be radially inserted into a sleeve recess defined by a sleeve outer surface of the sleeve.

[0014] The disclosed systems, devices, and methods provide advantages over conventional solutions. The disclosed systems reduce energy consumption compared to conventional systems. For example, the disclosed PX can be used to recover energy stored as pressure and return that energy to the system, reducing the energy costs of operating the system. The disclosed systems can reduce wear on components (e.g., pumps, compressors) compared to conventional systems. The disclosed PX can be better aligned and better sealed than conventional system components. This provides a healthier environment, less system fluid waste, improved system efficiency, and less debris in the system compared to conventional systems.

[0015] Although some embodiments of the present disclosure are described in relation to pressure exchangers, energy recovery devices, and hydraulic energy transmission systems, the present disclosure may be applied to other systems and devices (e.g., non-isobaric pressure exchangers, rotating components that are not pressure exchangers, non-rotary pressure exchangers, systems that do not include a pressure exchanger, etc.).

[0016] Although some embodiments of the present disclosure are described in the context of pressure exchange between fluids used in fracking, desalination, heat pump and / or refrigeration systems, the present disclosure may also be applied to other types of systems. Fluids may refer to liquids, gases, transcritical fluids, supercritical fluids, subcritical fluids and / or combinations thereof.

[0017] 1A-1D show schematic diagrams of a fluid treatment system 100 including a hydraulic energy transfer system 110, according to certain embodiments.

[0018] In some embodiments, the hydraulic energy transfer system 110 includes a pressure exchanger (e.g., PX). The PX may include one or more of the features described in one or more of Figures 3A-3M (e.g., sealing rings, gaskets, pins, etc.) to provide alignment and / or prevent fluid leakage.

[0019] The hydraulic energy transfer system 110 (e.g., PX) receives a low pressure (LP) in fluid 120 (e.g., a low pressure inlet flow) from an LPin system 122. The hydraulic energy transfer system 110 also receives a high pressure (HP) in fluid 130 (e.g., a high pressure inlet flow) from an HPin system 132. The hydraulic energy transfer system 110 (e.g., PX) exchanges pressure between the HPin fluid 130 and the LPin fluid 120 to provide an LPout fluid 140 (e.g., a low pressure outlet flow) to an LPout fluid system 142 and an HPout fluid 150 (e.g., a high pressure outlet flow) to an HPout fluid system 152.

[0020] In some embodiments, the hydraulic energy transfer system 110 includes a PX that exchanges pressure between the HPin fluid 130 and the LPin fluid 120. The PX may be a device that transfers fluid pressure between the HPin fluid 130 and the LPin fluid 120 with an efficiency of about 50%, 60%, 70%, 80%, 90% or more (e.g., without using centrifugal techniques). High pressure (e.g., HPin fluid 130, HPout fluid 150) refers to a pressure higher than low pressure (e.g., LPin fluid 120, LPout fluid 140). The LPin fluid 120 in the PX is pressurized and discharged from the PX at high pressure (e.g., HPout fluid 150 at a pressure higher than the pressure of the LPin fluid 120), and the HPin fluid 130 is depressurized and discharged from the PX at low pressure (e.g., LPout fluid 140 at a pressure lower than the pressure of the HPin fluid 130). The PX may operate with the HPin fluid 130 exerting a direct force to pressurize the LPin fluid 120, with or without a fluid separator between the fluids. Examples of fluid separators that may be used in the PX may include, but are not limited to, pistons, bladders, diaphragms, and the like. In some embodiments, the PX may be a rotary device. Rotary PXs, such as those manufactured by Energy Recovery, Inc. of San Leandro, California, may not have any separate valves, as the relative motion of the rotor to the end cover achieves effective valving within the device. Rotary PXs may be designed to operate with internal pistons to separate the fluids and transfer pressure with relatively little mixing of the inlet fluid streams. Reciprocating PXs may have pistons that move back and forth within a cylinder to transfer pressure between the fluid streams. The present disclosure may use any PX or multiple PXs, such as, but not limited to, rotary PXs, reciprocating PXs, or any combination thereof. Additionally, the PX may be located on a separate skid from other components of fluid treatment system 100 (eg, if the PX is being added to an existing fluid treatment system).

[0021] In some embodiments, the motor 160 is coupled to the hydraulic energy transmission system 110 (e.g., PX). In some embodiments, the motor 160 controls the speed of a rotor of the hydraulic energy transmission system 110 (e.g., to increase the pressure of the HPout fluid 150 or decrease the pressure of the LPout fluid 140). In some embodiments, the motor 160 generates energy (e.g., functions as a generator) based on pressure exchanges in the hydraulic energy transmission system 110.

[0022] The hydraulic energy transfer system 110 may be a hydraulic protection system (e.g., hydraulic buffer system, hydraulic isolation system) that exchanges work and / or pressure with another fluid while blocking or limiting contact between the fluid containing solid particles (e.g., fracking fluid) and various equipment (e.g., hydraulic fracturing equipment, high pressure pumps). By blocking or limiting contact between the fluid containing solid particles and various equipment (e.g., fracturing equipment) the hydraulic energy transfer system 110 increases the life and performance of the various equipment (e.g., fracturing equipment, high pressure fluid pumps) while reducing wear and tear. The use of equipment (e.g., high pressure fluid pumps) that is not designed for abrasive fluids (e.g., fracking fluids and / or corrosive fluids) may reduce the cost of equipment that may be used in the fluid treatment system 100.

[0023] The hydraulic energy transfer system 110 may include a hydraulic turbocharger or hydraulic pressure exchange system, such as a rotary PX. The PX may include one or more chambers (e.g., 1-100) that facilitate pressure transfer and pressure equalization between volumes of a first fluid and a second fluid (e.g., gas, liquid, 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 that may be highly viscous and / or contain solid particles (e.g., fracking fluids containing sand, proppant, powder, debris, ceramic). The solid particle fluid causes wear and / or erosion of parts of the PX, such as the rotor and end covers of the PX. The fluid (e.g., abrasive particles within the fluid) may cause wear at the interface between the rotor and each end cover as the rotor rotates relative to the end cover. Replacement of worn parts of the PX may be costly.

[0024] The hydraulic energy transfer system 110 may be used in various types of systems, such as fracking systems, desalination systems, and refrigeration systems.

[0025] 1A shows a schematic diagram of a fluid treatment system 100A including a hydraulic energy transfer system 110, according to certain embodiments. The fluid treatment system 100A may include a control module 180 including one or more controllers 185.

[0026] 1B shows a schematic diagram of a fluid treatment system 100B including a hydraulic energy transfer system 110, according to certain embodiments. Fluid treatment system 100B may be a fracking system. In some embodiments, fluid treatment system 100B includes more components, fewer components, the same routing, different routing, etc. than those shown in FIG. 1B.

[0027] The LPin fluid 120 and the HPout fluid 150 may be fracking fluids (e.g., fluids containing solid particles, proppant-containing fluids, etc.). The HPin fluid 130 and the LPout fluid 140 may be fluids that are substantially free of solid particles (e.g., proppant-free fluids, water, filtered fluids, etc.).

[0028] The LPin system 122 may include one or more low pressure fluid pumps for supplying the LPin fluid 120 to the hydraulic energy transmission system 110 (e.g., PX). The HPin system 132 may include one or more high pressure fluid pumps 134 for supplying the HPin fluid 130 to the hydraulic energy transmission system 110.

[0029] A hydraulic energy transfer system 110 exchanges pressure between LPin fluid 120 (e.g., low pressure fracking fluid) and HPin fluid 130 (e.g., high pressure water) to provide HPout fluid 150 (e.g., high pressure fracking fluid) to an HPout system 152, which provides LPout fluid 140 (e.g., low pressure water). The HPout system 152 may include a rock formation 154 (e.g., a well) that includes cracks 156. Solid particles (e.g., proppant) from the HPout fluid 150 may be provided into the cracks 156 in the rock formation.

[0030] In some embodiments, the LPout fluid 140, the high pressure fluid pump 134, and the HPin fluid 130 are part of a first loop (e.g., a fluid loop that does not include a proppant). The LPout fluid 140 may be fed to the high pressure fluid pump to produce the HPin fluid 130, which becomes the LPout fluid 140 upon exiting the hydraulic energy transfer system 110.

[0031] In some embodiments, the LPin fluid 120, the HPout fluid 150, and the low pressure fluid pump 124 are part of a second loop (e.g., a proppant-containing fluid loop). The HPout fluid 150 may be fed into the rock formation 154 and then pumped out of the rock formation 154 by the low pressure fluid pump 124 to produce the LPin fluid 120.

[0032] In some embodiments, the fluid treatment system 100B is used in well completion operations in the oil and gas industry to perform hydraulic fracturing (e.g., fracking, fracing) to increase the release of oil and gas in a rock formation 154. The HPout system 152 may include a rock formation 154 (e.g., a well). Hydraulic fracturing may include pumping an HPout fluid 150, including a combination of water, chemicals, and solid particles (e.g., sand, ceramic, proppant), at high pressure into the well (e.g., rock formation 154). The LPin fluid 120 and the HPout fluid 150 may include fluids containing particles that increase the release of oil and gas in the rock formation 154 by propagating and increasing the size of cracks 156 in the rock formation 154. The high pressure of the HPout fluid 150 causes cracks 156 to initiate, expand in size, and propagate through the rock formations 154, releasing more oil and gas, while solid particles (e.g., powder, debris, etc.) enter the cracks 156 and keep them open (e.g., preventing the cracks 156 from closing once the HPout fluid 150 is depressurized).

[0033] To pump the particle-laden fluid into the rock formation 154 (e.g., a well), the fluid treatment system 100B may include one or more high pressure fluid pumps 134 and one or more low pressure fluid pumps 124 coupled to a hydraulic energy transfer system 110. For example, the hydraulic energy transfer system 110 may be a hydraulic turbocharger or PX (e.g., a rotary PX). In operation, the hydraulic energy transfer system 110 transfers pressure without implementing any substantial mixing between a first fluid (e.g., HPin fluid 130, a proppant-free fluid) pumped by the high pressure fluid pump 134 and a second fluid (e.g., LPin fluid 120, a proppant-containing fluid, a fracking fluid) pumped by the low pressure fluid pump 124. In this manner, the hydraulic energy transfer system 110 prevents or limits wear on the high pressure fluid pump 134 while simultaneously enabling the fluid treatment system 100B to pump the high pressure fracking fluid (e.g., HPout fluid 150) into the rock formation 154 to release oil and gas. To operate in corrosive and abrasive environments, the hydraulic energy transmission system 110 may be made from materials that are resistant to the corrosive and abrasive substances contained in either the first fluid or the second fluid. For example, the hydraulic energy transmission system 110 may be made from a ceramic (e.g., a cermet such as alumina, 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 matrix of CoCr, Ni, NiCr, or Co.

[0034] In some embodiments, the hydraulic energy transfer system 110 comprises a PX (e.g., a rotary PX) where an HPin fluid 130 (e.g., a first fluid, a fluid that does not contain solid particles at high pressure) flows into a first side of the PX. Here, the HPin fluid 130 contacts an LPin fluid 120 (e.g., a second fluid, a low-pressure fracking fluid) that flows into the PX on a second side. The contact between the fluids allows the HPin fluid 130 to increase the pressure of the second fluid (e.g., the LPin fluid 120), which then pushes a second out fluid (e.g., the HPout fluid 150) of the PX into the well (e.g., the rock formation 154) for fracturing operations. The first fluid (e.g., the LPout fluid 140) also exits the PX, but at a lower pressure after exchanging pressure with the second fluid. As previously mentioned, the second fluid may be a low-pressure fracking fluid that may contain abrasive particles that may wear down the interface between the rotor and each end cover as the rotor rotates against each end cover.

[0035] 1C shows a schematic diagram of a fluid treatment system 100C including a hydraulic energy transfer system 110, according to certain embodiments. Fluid treatment system 100C may be a desalination system (e.g., removing salt and / or other minerals from water). In some embodiments, fluid treatment system 100C includes more components, fewer components, the same routing, different routing, etc. than those shown in FIG. 1C.

[0036] The LPin system 122 may include a feed pump 126 (e.g., low pressure fluid pump 124) that receives in seawater 170 (e.g., a reservoir feed or a direct ocean feed) and supplies the LPin fluid 120 (e.g., low pressure seawater, feed) to the hydraulic energy transfer system 110 (e.g., PX). The HPin system 132 may include a membrane 136 that supplies the HPin fluid 130 (e.g., high pressure brine) to the hydraulic energy transfer system 110 (e.g., PX). The hydraulic energy transfer system 110 exchanges pressure between the HPin fluid 130 and the LPin fluid 120 to supply the HPout fluid 150 (e.g., high pressure seawater) to the HPout system 152 and the LPout fluid 140 (e.g., low pressure brine) to the LPout system 142 (e.g., a geological mass, ocean, sea, wastewater, etc.).

[0037] The membrane 136 may be a membrane separator configured to separate fluids passing through the membrane, such as a reverse osmosis membrane. The membrane 136 may provide a concentrated feedwater or concentrate (e.g., brine) HPin fluid 130 to the hydraulic energy transfer system 110. The pressure of the HPin fluid 130 may be used to compress a low pressure feedwater (e.g., LPin fluid 120) to a high pressure feedwater (e.g., HPout fluid 150). For simplicity and explanation, the term feedwater is used. However, fluids other than water may be used in the hydraulic energy transfer system 110.

[0038] A circulation pump 158 (e.g., a centrifugal pump) delivers HPout fluid 150 (e.g., high pressure seawater) to the membrane 136. The membrane 136 filters the HPout fluid 150 to deliver LP drinking water 172 and HPin fluid 130 (e.g., high pressure brine). The LPout system 142 delivers out brine 174 (e.g., to a geological body, ocean, sea, wastewater, etc.).

[0039] In some embodiments, a high pressure fluid pump 176 is disposed between the feedwater pump 126 and the membrane 136. The high pressure fluid pump 176 increases the pressure of the low pressure seawater (e.g., LPin fluid 120, providing the high pressure feedwater) that is mixed with the high pressure seawater provided by the circulation pump 158.

[0040] In some embodiments, 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 the LP potable water 172 without the use of the high pressure fluid pump 176. In some embodiments, the fluid treatment system 100C provides the LP potable water 172 using the high pressure fluid pump 176 intermittently.

[0041] In some examples, a hydraulic energy transfer system 110 (e.g., PX) receives an LPin fluid 120 (e.g., low pressure feedwater) at about 30 pounds per square inch (PSI) (about 207 kPa) and an HPin fluid 130 (e.g., high pressure brine or concentrate) at about 980 PSI (about 6757 kPa). The hydraulic energy transfer system 110 (e.g., PX) transfers pressure from the high pressure concentrate (e.g., HPin fluid 130) to the low pressure feedwater (e.g., LPin fluid 120). The hydraulic energy transfer system 110 (e.g., PX) outputs an HPout fluid 150 (e.g., high pressure (compressed) feedwater) at about 965 PSI (about 6653 kPa) and outputs an LPout fluid 140 (e.g., low pressure concentrate) at about 15 PSI (about 103 kPa). Because of this, the hydraulic energy transmission system 110 (e.g., PX) can be approximately 97% efficient because the input volume is approximately equal to the output volume of the hydraulic energy transmission system 110 (e.g., PX) and 965 PSI (approximately 6653 kPa) is approximately 97% of 980 PSI (approximately 6757 kPa).

[0042] 1D shows a schematic diagram of a fluid treatment system 100D including a hydraulic energy transfer system 110, according to certain embodiments. Fluid treatment system 100D may be a refrigeration system. In some embodiments, fluid treatment system 100D includes more components, fewer components, the same routing, different routing, etc. than those shown in FIG. 1D.

[0043] A hydraulic energy transfer system 110 (e.g., PX) receives LPin fluid 120 from an LPin system 122 (e.g., low pressure lift device 128, low pressure fluid pump, etc.) and receives HPin fluid 130 from an HPin system 132 (e.g., condenser 138). The hydraulic energy transfer system 110 (e.g., PX) may exchange pressure between the LPin fluid 120 and the HPin fluid 130 to provide HPout fluid 150 to the HPout system 152 (e.g., high pressure lift device 159) and provide LPout fluid 140 to the LPout system 142 (e.g., evaporator 144). The evaporator 144 may provide fluid to the compressor 178 and the low pressure lift device 128. The condenser 138 may receive fluid from the compressor 178 and the high pressure lift device 159.

[0044] Fluid treatment system 100D may be a closed system. LPin fluid 120, HPin fluid 130, LPout fluid 140 and HPout fluid 150 may all be fluids (eg, refrigerants) that circulate in the closed system of fluid treatment system 100D.

[0045] In some embodiments, the fluid of the fluid treatment system 100D may include solid particles. For example, solid particles (e.g., solid particles from welding) may be entrained in the fluid in the fluid treatment system 100D due to piping, equipment, connections (e.g., welding of pipes, soldering of pipes), etc. Solid particles in the fluid and / or high pressure of the fluid may cause wear and / or erosion of the PX components (e.g., rotors, end covers) of the hydraulic energy transfer system 110.

[0046] 2A-2E are exploded perspective views of a rotary PX 40 (eg, a rotary pressure exchanger, a rotary liquid piston compressor (LPC)) according to certain embodiments. The PX 40 may include a motor 92 and / or a control module 94.

[0047] In some embodiments, PX40 includes one or more of the features described in one or more of Figures 3A-3M (e.g., sealing rings, gaskets, pins, etc.) to provide alignment and / or prevent fluid leakage.

[0048] 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, HPin fluid 130) and a second fluid (e.g., fracking fluid or superheated carbon dioxide gas, LPin fluid 120) with minimal fluid mixing. The rotary PX 40 may include a generally cylindrical body portion 42 including a sleeve 44 (e.g., rotor sleeve) and a rotor 46. The rotary PX 40 may also include two end caps 48 and 50 including manifolds 52 and 54, respectively. The manifold 52 includes respective inlet and outlet ports 56 and 58, and the manifold 54 includes respective inlet and outlet ports 60 and 62. In operation, the inlet ports 56, 60 allow the first and second fluids to enter and exchange pressure with the rotary PX 40, while the outlet ports 58, 62 allow the first and second fluids to exit the rotary PX 40. In operation, the inlet port 56 may receive a first fluid (e.g., HPin fluid 130) at high pressure and, after exchanging pressure, the outlet port 58 may be used to pump the first fluid (e.g., LPout fluid 140) at low pressure out of the rotary PX 40. Similarly, the inlet port 60 may receive a second fluid (e.g., LPin fluid 120) at low pressure and the outlet port 62 may be used to pump the second fluid (e.g., HPout fluid 150) at high pressure out of the rotary PX 40. The end caps 48 and 50 are disposed within the respective manifolds 52 and 54 and include respective end covers 64 and 66 (e.g., end plates) that enable fluid-sealing contact with the rotor 46.

[0049] As noted above, one or more components of PX 40, such as rotor 46, end cover 64 and / or end cover 66, may be constructed from 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 number of at least 1000, 1250, 1500, 1750, 2000, 2250 or more). For example, tungsten carbide may provide increased durability and improved wear resistance to abrasive fluids compared to other materials, such as alumina ceramic.

[0050] The rotor 46 may be cylindrical and disposed within the sleeve 44, which allows the rotor 46 to rotate about an axis 68. The rotor 46 may have a number of channels 70 (e.g., ducts, rotor ducts) that run generally longitudinally through the rotor 46, with openings 72 and 74 (e.g., rotor ports) at each end symmetrically disposed about the longitudinal axis 68. The openings 72 and 74 of the rotor 46 are disposed to be in fluid communication with the inlet and outlet apertures 76 and 78 (e.g., end cover inlet and end cover outlet ports) and 80 and 82 (e.g., end cover inlet and end cover outlet ports) of the end covers 64 and 66, respectively, in such a way that the channels 70 are exposed to high and low pressure fluids during rotation. As shown, the inlet and outlet apertures 76 and 78, 80 and 82 may be designed in the shape of an arc or a portion of a circle (e.g., C-shaped).

[0051] In some embodiments, a controller using sensor feedback (e.g., revolutions per minute measured via a tachometer or optical encoder, or volumetric flow rate measured via a flow meter) may control the degree of mixing of the first and second fluids in the rotary PX 40. This controller may be used to improve the operability of a fluid treatment system (e.g., fluid treatment systems 100A-100D of FIGS. 1A-1D). For example, by varying the volumetric flow rates of the first and second fluids entering the rotary PX 40, a plant operator (e.g., a system operator) can control the amount of fluid mixing in the PX 40. Additionally, by varying the rotational speed of the rotor 46, an operator can also control the mixing. Three characteristics of the rotary PX 40 that affect mixing include (1) the aspect ratio of the rotor channel 70, (2) the exposure time between the first and second fluids, and (3) the creation of a fluid barrier (e.g., an interface) between the first and second fluids in the rotor channel 70. First, the rotor channel 70 (e.g., a duct) is generally long and narrow, which stabilizes the flow in the rotary PX 40. Furthermore, the first and second fluids may move through the channel 70 in a plug-flow manner with minimal axial mixing. Second, in certain 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) may reduce the contact time between the first and second fluids 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 to exchange pressure between the first and second fluids. Thus, a certain amount of fluid remains in the channel 70 as a barrier between the first and second fluids. Any of these mechanisms may limit mixing in the rotary PX 40. Additionally, in some embodiments, the rotary PX40 may be designed to operate with all or part of an internal piston or other barrier that isolates the first and second fluids while allowing pressure transmission.

[0052] 2B-2E are exploded views of one embodiment of the rotary PX 40, showing the sequence of positions of a single rotor channel 70 within the rotor 46 as the channel 70 rotates through one complete cycle. Note that FIGS. 2B-2E are simplified views of the rotary PX 40, showing one rotor channel 70, and showing the channel 70 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, elliptical, square, rectangular, polygonal, etc.). Thus, FIGS. 2B-2E are simplified for illustrative purposes, and other embodiments of the rotary PX 40 may have different configurations than those shown in FIGS. 2A-2E. As will be described in more detail below, the rotary PX 40 facilitates pressure exchange between a first fluid and a second fluid by allowing the first and second fluids to briefly contact each other within the rotor 46. In certain embodiments, this exchange is performed at a rate that limits intermixing of the first and second fluids. The speed of the pressure wave passing through the rotor channel 70 (as soon as the channel is exposed to the aperture 76), the rate of diffusion of the fluids, and the rotational speed of the rotor 46 determine whether and to what extent any intermixing occurs.

[0053] FIG. 2B is an exploded perspective view of one embodiment of a rotary PX 40 (e.g., a rotary LPC) according to certain embodiments. In FIG. 2B, the channel opening 72 is in a first position. In the first position, the channel opening 72 is in fluid communication with an aperture 78 in the end cover 64 and thus the manifold 52, while the opposite channel opening 74 is in fluid communication with an aperture 82 in the end cover 66 and extends therefrom into the manifold 54. As discussed below, the rotor 46 may rotate in a clockwise direction as indicated by arrow 84. In operation, a low pressure second fluid 86 passes through the end cover 66 and into the channel 70 where it contacts the first fluid 88 at a dynamic fluid interface 90. The second fluid 86 then pushes the first fluid 88 out of the channel 70, through the end cover 64, and out of the rotary PX 40. However, due to the short contact time, there is minimal mixing between the second fluid 86 and the first fluid 88.

[0054] 2C is an exploded perspective view of one embodiment of a rotating PX 40 (e.g., a rotating LPC) in accordance with certain embodiments. In FIG. 2C, the channel 70 has been rotated clockwise through an arc of approximately 90 degrees. In this position, the opening 74 (e.g., outlet) is not in fluid communication with the apertures 80 and 82 in the end cover 66, and the opening 72 is not in fluid communication with the apertures 76 and 78 in the end cover 64. Thus, a low pressure second fluid 86 is temporarily contained within the channel 70.

[0055] FIG 2D is an exploded perspective view of one embodiment of a rotating PX 40 (e.g., a rotating LPC) according to certain embodiments. In FIG 2D, the channel 70 has been rotated through an arc of approximately 60 degrees from the position shown in FIG 2B. The opening 74 is now in fluid communication with the aperture 80 in the end cover 66, and the opening 72 in the channel 70 is now in fluid communication with the aperture 76 in the end cover 64. In this position, a first fluid 88 at high pressure flows in and pressurizes a second fluid 86 at low pressure, forcing the second fluid 86 out of the rotor channel 70 and through the aperture 80.

[0056] FIG 2E is an exploded perspective view of one embodiment of a rotary PX 40 (e.g., a rotary LPC) in accordance with certain embodiments. In FIG 2E, the channel 70 has rotated through an arc of approximately 270 degrees from the position shown in FIG 2B. In this position, the opening 74 is no longer in fluid communication with the apertures 80 and 82 in the end cover 66, and the opening 72 is no longer in fluid communication with the apertures 76 and 78 in the end cover 64. Thus, the first fluid 88 is no longer pressurized and is temporarily retained within the channel 70 until the rotor 46 rotates another 90 degrees to begin the cycle again.

[0057] Abrasion and / or erosion damage to the PX can occur when suspended matter is induced and mixed with the fluid entering the PX. Abrasion damage can occur when particles enter the gaps of the PX (e.g., become trapped between the stationary and rotating end covers). Erosion damage can occur due to the presence of suspended matter (e.g., erosion) in high-velocity fluid jets (e.g., slurry jets) that are formed due to high pressure differentials inside the PX. When high-velocity jets impinge on components of the PX, they can damage such components. Damage (e.g., erosion damage) can occur when high-pressure rotor ports (e.g., rotor ducts) open to low-pressure end cover ports (e.g., kidneys) or when low-pressure rotor ports (e.g., rotor ducts) open to high-pressure end cover ports (e.g., kidneys) creating high pressure differentials.

[0058] Figures 3A-3M illustrate a PX 300 according to some embodiments. One or more of the hydraulic energy transmission systems 110 of Figures 1A-1D and / or one or more of the PXs 40 of Figures 2A-2E may have one or more features, materials, functions, etc. that are the same as or similar to those of Figures 3A-3M. The PX 300 described in Figures 3A-3M may have one or more features, materials, functions, etc. as described in connection with one or more of Figures 1A-2E.

[0059] In some embodiments, the PX 300 comprises a rotor 310, a sleeve 320, end covers 330A-B, and a carrier plate 340. The rotor 310 is configured to exchange pressure between a first fluid and a second fluid. The sleeve 320 is disposed about the rotor 310. The end cover 330A is disposed at a first distal end of the rotor 310. The end cover 330B is disposed at a second distal end of the rotor 310.

[0060] In some embodiments, the PX 300 includes one or more sealing elements configured to prevent leakage between the sleeve 320 and the end cover 330.

[0061] 3A-3M show the sealing and / or alignment of a cartridge of PX 300. The cartridge of PX 300 may refer to at least two or more of sleeve 320, first end cover 330A, second end cover 330B, and / or rotor 310. PX 300 is used in a variety of applications (e.g., seawater reverse osmosis desalination plants, fracking, refrigeration, etc.) to help make the process economically viable. The PX 300 of the present disclosure improves performance while providing production capacity for a variety of applications (e.g., desalination industry, refrigeration industry, fracking industry, etc.).

[0062] Sealing the PX300 cartridge at various external interfaces (e.g., sealing end covers 330A-B to sleeve 320) improves the efficiency of the PX300. The present disclosure provides for sealing a set of interfaces on both ends of the PX300 sleeve, where sleeve 320 mates with PX300 end covers 330A-B.

[0063] The present disclosure may provide for sealing (e.g., tightly sealing) the interfaces between the end covers 330A-B and the sleeve 320 to prevent leakage (e.g., leakage due to pressure differentials across the interfaces, leakage due to fluid pressure pushing the end covers 330A-B out of the sleeve 320). With tightly overlapping interface surfaces, such a sealing scheme may prevent leakage when the PX 300 is processing liquids. When the process fluid is a gas or multi-phase fluid, active sealing methods (e.g., seal ring 352) of the present disclosure may be used to reduce leakage and maintain performance of the PX 300.

[0064] Sealing at the interface can be accomplished using a variety of methods, including a seal ring 352 (e.g., Figures 3A-3F), a flange face (e.g., flange ring 360 in Figure 3G), a gasket 354 (e.g., an O-ring) on ​​the mating surfaces, a thin gasket 354 between the mating surfaces, a counterbore on the end cover 330 or rotor 310 with a gasket 354, or a sealing tape at the joint (e.g., Figure 3H).

[0065] Each end cover / sleeve interface (e.g., a first interface between the first end cover 330A and the sleeve 320 and a second interface between the second end cover 330B and the sleeve 320) may have a set of pins 356 (e.g., at least three dowel pins, at least two dowel pins) for properly aligning and clocking the first and second end covers 330A-B (e.g., for aligning the first end cover 330A and the second end cover 330B). Some active sealing methods prevent visual access to the alignment pins, making assembly difficult. For ceramic mating components, the pins 356 (e.g., alignment pins) may be made from a plastic material such as nylon to prevent damage to the ceramic. Lack of sufficient visual access to the alignment pins during assembly may result in damage to the pin holes or plastic chips entering the radial or axial bearing gaps. This can result in unnaturally high bearing clearances or increased bearing friction torque. To avoid such issues and facilitate alignment, the present disclosure includes methods that incorporate external alignment holes or slots (e.g., radial holes, radial recesses) in the different mating parts (e.g., end cover 330, sleeve 320).

[0066] In some embodiments, the components of the present disclosure include a seal ring 352 and a pin 356 (eg, an alignment dowel pin).

[0067] New part seal rings 352, each with a pair of radial gaskets 354 (e.g., O-rings), can be used at the end cover / sleeve interfaces to prevent leakage of process fluids. The seal rings 352 are assembled at the interface between the end cover 330 and the sleeve 320 (see, e.g., Figures 3A-3F). Shallow grooves machined into either end of the sleeve 320 and end cover 330A-B interface position the seal rings 352 and prevent them from moving axially.

[0068] A pair of pins 356 (e.g., alignment dowel pins) attached to the outer surfaces of the end covers 330A-B and sleeve 320 mate with corresponding slots in the seal ring 352 to allow clocking (e.g., precise clocking) of the end covers 330 relative to the sleeve 320. This facilitates assembly and provides direct visual confirmation of the fit of the parts. The pins 356 (e.g., alignment pins) may reduce or eliminate (e.g., confirm the absence of) relative circumferential motion between the seal ring 352 and the end covers 330 and between the seal ring 352 and the sleeve 320. In some embodiments, the axial pins 356 (e.g., alignment pins) of some previous configurations may not be used because visual access is prevented by the seal rings.

[0069] FIG. 3A shows a front view of a PX 300 with seal rings 352A-B according to certain embodiments. FIG. 3B shows a front cross-sectional view of a PX 300 with seal rings 352A-B according to certain embodiments (e.g., the PX 300 of FIG. 3A). FIG. 3C shows an enlarged front cross-sectional view of a PX 300 with seal ring 352 according to certain embodiments (e.g., the PX 300 of FIG. 3A and / or FIG. 3B). FIG. 3D shows a perspective cross-sectional view of a PX 300 with seal ring 352 according to certain embodiments (e.g., one or more of the PX 300 of FIG. 3A-3C). The PX 300 of the present disclosure may reduce leakage, provide better alignment of the end cover 330, and / or improve ease of assembly compared to conventional systems.

[0070] The one or more sealing elements include a seal ring assembly 350 including a seal ring 352 disposed about one or more components of the PX 300, a gasket 354 disposed between the seal ring 352 and the end cover 330, and a gasket 354 disposed between the seal ring 352 and the sleeve 320. The seal ring 352 may be metallic (e.g., stainless steel, brass, etc.). The gasket 354 may be elastomeric.

[0071] In some embodiments, the one or more sealing elements may include a seal ring assembly 350A (e.g., including seal ring 352A) disposed around the interface between end cover 330A and sleeve 320 (e.g., to prevent leakage between sleeve 320 and end cover 330A) and a seal ring assembly 350B (e.g., including seal ring 352B) disposed around the interface between end cover 330B and sleeve 320 (e.g., to prevent leakage between sleeve 320 and end cover 330B).

[0072] In some embodiments, PX 300 includes one or more alignment elements configured to align one or more components of PX 300. In some embodiments, the one or more alignment elements align end cover 330A with at least one of sleeve 320 or end cover 330B. In some embodiments, the one or more alignment elements align end cover 330A with end cover 330B.

[0073] In some embodiments, the one or more alignment elements comprise pin 356A and pin 356B. Pin 356A is disposed in an end cover recess formed by the end cover outer surface of end cover 330. Pin 356A may engage a seal ring upper recess formed by the upper surface of seal ring 352. Pin 356B is disposed in a sleeve recess formed by the sleeve outer surface of sleeve 320. Pin 356B engages a seal ring lower recess formed by the lower surface of seal ring 352.

[0074] The pin 356 may be plastic. The pin 356 may be metal (e.g., steel, brass, etc.). The pin 356 may be a dowel pin (e.g., a straight solid pin with a chamfered end for ease of insertion and alignment, a cylindrical solid pin). The pin 356 may be an alignment pin. The pin 356 may be a radial pin that is inserted radially into the side of a part. The pin 356 may be placed in a dovetail formed by a part of the PX 300.

[0075] For each pin 356 shown in each cross-sectional view of the figures, at least three pins 356 are positioned (e.g., approximately evenly) around PX 300 (e.g., three pins 356A positioned around end cover 330A, three pins 356 positioned around end cover 330A, three pins 356B positioned around the top of sleeve 320, and three pins 356 positioned around the bottom of sleeve 320).

[0076] In some embodiments, PX 300 includes alignment elements (e.g., pins 356) configured to align end cover 330A with end cover 330B. The alignment elements may include a first alignment element radially inserted into end cover 330A and a second alignment element radially inserted into end cover 330B.

[0077] In some embodiments, the first alignment element engages with seal ring 352A (e.g., seal ring 352A is disposed about a first interface between end cover 330A and sleeve 320). The second alignment element may engage with seal ring 352B (e.g., seal ring 352B is disposed about a second interface between end cover 330B and sleeve 320).

[0078] In some embodiments, the PX 300 comprises a rotor 310, a sleeve 320, end covers 330A-B, and a sealing element. In some embodiments, the PX 300 comprises a rotor 310, a sleeve 320, end covers 330A-B, and an alignment element. In some embodiments, the PX 300 comprises a sleeve 320, end covers 330A-B, a sealing element, and an alignment element.

[0079] In some embodiments, the seal ring assembly 350 (eg, a pressure exchanger seal ring assembly) comprises a seal ring 352, gaskets 354A-B, and / or pins 356A-B.

[0080] The seal ring 352 may have an inner surface that forms a first groove and a second groove. The gasket 354A may be configured to be disposed in the first groove and the gasket 354B may be configured to be disposed in the second groove. The seal ring assembly 350 is disposed about an interface between the end cover 330 and the sleeve 320 to prevent leakage between the sleeve 320 and the end cover 330. The gasket 354A will interface with an end cover outer surface of the end cover 330 and the gasket 354B will interface with a sleeve outer surface of the sleeve 320.

[0081] Pin 356A includes a first distal end configured to be disposed within an upper seal ring recess formed by an upper surface of seal ring 352. Pin 356B further includes a second distal end configured to be radially inserted into an end cover recess formed by an outer end cover surface of end cover 330.

[0082] Pin 356B has a first distal end configured to be disposed in a lower seal ring recess formed by the lower surface of seal ring 352. Pin 356B has a second distal end configured to be radially inserted into a sleeve recess formed by the outer sleeve surface of sleeve 320.

[0083] In some embodiments, gasket 354A is a first O-ring and gasket 354B is a second O-ring. In some embodiments, gasket 354 is a hollow O-ring. In some embodiments, gasket 354 is a solid O-ring. In some embodiments, gasket 354 has a circular perimeter. In some embodiments, gasket 354 has a rectangular (e.g., square) perimeter.

[0084] In some embodiments, the pin 356 is plastic. In some embodiments, the pin 356 is nylon.

[0085] In some embodiments, PX 300 is configured to exchange pressure between a first fluid and a second fluid, where the first fluid and the second fluid are refrigerants. In some embodiments, a sealing element (such as gasket 354) prevents fluid (e.g., gas, liquid) from leaking into PX 300 and / or prevents fluid (e.g., gas, liquid, refrigerant) from leaking out of PX 300.

[0086] 3C, the end cover 330 may have a distal end having a smaller diameter (e.g., forming a recess) than the remainder of the end cover 330 and / or the sleeve 320 may have a distal end having a smaller diameter (e.g., forming a recess) than a central portion of the sleeve 320. The seal ring 352 may be disposed in the smaller diameter portion (e.g., in the recess).

[0087] 3D, the seal ring 352 may extend around the PX 300 at the interface between the end cover 330 and the sleeve 320. In some embodiments, pins 356A (e.g., three equally spaced pins 356A) may be inserted into the end cover 330, and then the seal ring 352 may slide onto the bottom of the end cover 330 to abut against the pins 356A. Pins 356B may be inserted into the sleeve 320, and then the seal ring 352 attached to the end cover 330 may slide onto the top of the sleeve 320.

[0088] Figure 3E shows a front view of a PX 300 with a seal ring 352 according to certain embodiments. Figure 3F shows a front cross-sectional view of a PX 300 with a seal ring 352 (e.g., PX 300 of Figure 3E) according to certain embodiments.

[0089] In some embodiments, the one or more sealing elements include a single seal ring 352 disposed on the interface between end cover 330A and sleeve 320 and on the interface between end cover 330B and sleeve 320 (e.g., the single seal ring 352 extends from end cover 330A to end cover 330B).

[0090] FIG. 3G illustrates a PX (eg, flange design) according to certain embodiments.

[0091] In some embodiments, one or more first sealing elements (e.g., seal ring assembly 350) include flange rings 360A-B and gaskets 354A-C. Flange ring 360A is coupled to (e.g., disposed about) an end cover outer surface of end cover 330. Flange ring 360B is coupled to (e.g., disposed about) a sleeve outer surface of sleeve 320. Gasket 354A is disposed between flange ring 360A and end cover 330. Gasket 354B is disposed between flange ring 360B and sleeve 320. Gasket 354C is disposed between flange ring 360A and flange ring 360B. Flange rings 360A-B and gaskets 354A-C may prevent leakage into and / or out of PX 300 (e.g., at the interface between end cover 330 and sleeve 320).

[0092] In some embodiments, one or more fasteners 362 (eg, bolts, screws, pins, etc.) may connect flange ring 360A and flange ring 360B.

[0093] Pin 356 may be disposed between an upper surface of sleeve 320 and a lower surface of end cover 330 (e.g., a first distal end of pin 356 is disposed in a recess formed by the lower surface of end cover 330 and a second distal end of pin 356 is disposed in a recess formed by the upper surface of sleeve 320).

[0094] FIG. 3H illustrates a PX (eg, with tape on and around the interface) according to certain embodiments.

[0095] In some embodiments, the one or more sealing elements comprise a flexible element 370 (e.g., a tape, a substrate with adhesive on one side) adhered to a portion of the pressure exchanger comprising the interface between the end cover 330 and the sleeve 320. The flexible element 370 may prevent leakage into and / or out of the PX 300 (e.g., at the interface between the end cover 330 and the sleeve 320).

[0096] Pin 356 may be disposed between an upper surface of sleeve 320 and a lower surface of end cover 330 (e.g., a first distal end of pin 356 is disposed within a recess formed by the lower surface of end cover 330 and a second distal end of pin 356 is disposed within a recess formed by the upper surface of sleeve 320).

[0097] FIG 3I illustrates a PX according to certain embodiments (e.g., with an O-ring disposed in a groove formed by the end cover between the end cover and the sleeve) and FIG 3J illustrates a PX according to certain embodiments (e.g., with an O-ring disposed in a groove formed by the sleeve between the end cover and the sleeve).

[0098] In some embodiments, the one or more first sealing elements include a gasket 354A (e.g., an O-ring) disposed between a lower surface of the end cover 330A and an upper surface of the sleeve 320, and a gasket 354B disposed between a lower surface of the sleeve 320 and an upper surface of the end cover 330B. With reference to FIG. 3I, the gasket 354A may be disposed in a recess formed by the lower surface of the end cover 330A, and the gasket 354B may be disposed in a recess formed by the upper surface of the end cover 330B. With reference to FIG. 3J, the gasket 354 may be disposed in a recess formed by the upper surface of the sleeve 320 (e.g., a second gasket 354 may be disposed in a recess formed by the lower surface of the sleeve 320).

[0099] 3K illustrates a PX (e.g., with an alignment pin using a slot) according to certain embodiments. The pin 356 may be placed in a slot formed by the PX 300 (e.g., a slot formed by the end covers 330A-B and the sleeve 320).

[0100] 3L-3M show PX (eg, with a radial seal ring integrated into the end cover or sleeve) according to certain embodiments.

[0101] 3L , in some embodiments, each end cover 330 has an overlapping portion that overlaps with an outer sleeve surface of sleeve 320. The one or more sealing elements include a gasket 354 disposed between an inner surface of the overlapping portion of end cover 330 and the outer sleeve surface of sleeve 320. A pin 356 includes a first distal end disposed in a recess formed by the inner surface of the overlapping portion of end cover 330 and a second distal end disposed in a recess formed by the outer sleeve surface of sleeve 320.

[0102] In some embodiments, the sleeve 320 may seal against a side of the end cover 330 or a distal end of the end cover 330 .

[0103] 3M , in some embodiments, sleeve 320 overlaps an outer end cover surface of end cover 330. The one or more sealing elements include a gasket 354 disposed between an inner surface of sleeve 320 and the outer end cover surface of end cover 330. A pin 356 includes a first distal end disposed in a recess formed by the inner surface of sleeve 320 and a second distal end disposed in a recess formed by the outer end cover surface of end cover 330.

[0104] The present disclosure includes new devices (eg, PX seal ring assemblies) that can be used in existing or new equipment.

[0105] Conventional systems do not have any device / mechanism to prevent leakage between the end cover and the sleeve, which can reduce efficiency. Axial alignment pins may be used to prevent relative movement between the sleeve and the end cover (e.g., solutions without a seal ring).

[0106] The present disclosure may be configured to apply pressure exchangers to refrigeration systems (e.g., transcritical carbon dioxide (CO2) refrigeration systems), but the present disclosure may be used in any application of pressure exchangers in any field.

[0107] The present disclosure can enable the use of high pressure gaseous or multi-phase fluids in a pressure exchanger by providing a leak-proof seal (eg, a seal that is substantially leak-proof).

[0108] The present disclosure (eg, one or more of the embodiments of FIGS. 3A-3M) may provide one or more improvements in pressure range, efficiency, volume, cost reduction, and the like, compared to conventional solutions.

[0109] In the above description, numerous specific details are described, such as examples of specific systems, components, methods, etc., to fully understand some embodiments of the present disclosure. However, it will be apparent to one skilled in the art that at least some embodiments of the present disclosure may be practiced without such specific details. In other instances, well-known components or methods are not described in detail or are presented in simple block diagram form to avoid unnecessarily obscuring the present disclosure. Thus, the specific details described are merely exemplary. A particular implementation may vary from such example details and still be considered within the scope of the present disclosure. The description of the system herein may include a description of one or more optional components. Components may be included in combinations not specifically discussed in the present disclosure, and such components may still be within the scope of the present disclosure.

[0110] References throughout this specification to "one embodiment" or "an embodiment" mean that a particular feature, structure, or characteristic described in connection with that embodiment is included in at least one embodiment. Thus, the appearances of the phrase "in one embodiment" or "in an embodiment" in various places throughout this specification do not necessarily all refer to the same embodiment. Furthermore, the term "or" is intended to mean an inclusive "or" rather than an exclusive "or". When the terms "about", "substantially" or "approximately" are used herein, this is intended to mean that the nominal value presented is accurate to within ±10%. In addition, the terms "first", "second", "third", "fourth", etc., used herein are intended as labels to distinguish different elements and do not necessarily have an ordinal meaning according to their numerical designations.

[0111] As used herein, the terms "throughout," "under," "between," "disposed on," "before," "after," and "on" refer to the location of a layer of material or component relative to another layer or component. For example, a layer that is disposed over, through, or under another layer may be in direct contact with the other layer or there may be one or more intervening layers. Further, a layer that is disposed between two layers may be in direct contact with the two layers or there may be one or more intervening layers. Similarly, unless expressly stated otherwise, a feature that is disposed between two features may be in direct contact with the adjacent feature or there may be one or more intervening layers or components.

[0112] It is to be understood that the above description is intended to be illustrative, and not limiting. Many other embodiments will be apparent to those skilled in the art upon reading and understanding the above description. Thus, the scope of the present disclosure should be determined with reference to the appended claims, along with the full scope of equivalents to which each claim is entitled.

Claims

1. A pressure exchanger, comprising: a rotor configured to exchange pressure between a first fluid and a second fluid; a sleeve disposed around the rotor; a first end cover disposed at a first distal end of the rotor; one or more first sealing elements configured to prevent leakage between the sleeve and the first end cover.

2. The pressure exchanger comprises: one or more alignment elements configured to align the first end cover with at least one of the sleeve or the second end cover; The pressure exchanger of claim 1 , wherein the second end cover is disposed at a second distal end of the rotor.

3. The one or more first closure elements include: a seal ring disposed around the pressure exchanger; a first gasket disposed between the seal ring and the first end cover; 10. The pressure exchanger of claim 1, further comprising: a second gasket disposed between said seal ring and said sleeve.

4. The pressure exchanger comprises: a first pin disposed within an end cover recess defined by an end cover outer surface of the first end cover, the first pin engaging an upper seal ring recess defined by an upper surface of the seal ring; 4. The pressure exchanger of claim 3, further comprising: a second pin disposed within a sleeve recess formed by an outer sleeve surface of the sleeve, the second pin engaging a seal ring lower recess formed by a lower surface of the seal ring.

5. The pressure exchanger comprises: a second end cover disposed at a second distal end of the rotor; The pressure exchanger of claim 1 , further comprising: one or more second sealing elements configured to prevent leakage between the sleeve and the second end cover.

6. The one or more first closure elements include: a first flange ring coupled to an end cover outer surface of the first end cover; a second flange ring coupled to an outer sleeve surface of the sleeve; a first gasket disposed between the first flange ring and the first end cover; a second gasket disposed between the second flange ring and the sleeve; 10. The pressure exchanger of claim 1, further comprising: a third gasket disposed between the first flange ring and the second flange ring.

7. The pressure exchanger of claim 1 , wherein the one or more first sealing elements comprise a flexible element adhered to a portion of the pressure exchanger comprising an interface between the first end cover and the sleeve.

8. The pressure exchanger of claim 1 , wherein the one or more first sealing elements comprise a gasket disposed between a lower surface of the first end cover and an upper surface of the sleeve.

9. 2. The pressure exchanger of claim 1, wherein the overlapping portion of the first end cover overlaps with an outer sleeve surface of the sleeve, and the one or more first sealing elements comprise a gasket disposed between an inner surface of the overlapping portion of the first end cover and the outer sleeve surface.

10. 2. The pressure exchanger of claim 1, wherein the sleeve overlaps an end cover outer surface of the end cover, and the one or more first sealing elements comprise a gasket disposed between an inner surface of the sleeve and the end cover outer surface of the end cover.

11. A pressure exchanger, comprising: a rotor configured to exchange pressure between a first fluid and a second fluid; a sleeve disposed around the rotor; a first end cover disposed at a first distal end of the rotor; a second end cover disposed at a second distal end of the rotor; a plurality of alignment elements configured to align the first end cover with the second end cover, the plurality of alignment elements comprising a first alignment element radially inserted into the first end cover and a second alignment element radially inserted into the second end cover.

12. The pressure exchanger comprises: one or more first sealing elements configured to prevent leakage between the sleeve and the first end cover; The pressure exchanger of claim 11 , further comprising: one or more second sealing elements configured to prevent leakage between the sleeve and the second end cover.

13. The one or more first closure elements include: a seal ring disposed around the pressure exchanger; a first gasket disposed between the seal ring and the first end cover; 13. The pressure exchanger of claim 12, further comprising a second gasket disposed between said seal ring and said sleeve.

14. The first alignment element comprises: a first pin disposed within an end cover recess defined by an end cover outer surface of the end cover, the first pin engaging an upper seal ring recess defined by an upper surface of the seal ring; 14. The pressure exchanger of claim 13, comprising: a second pin disposed within a sleeve recess formed by an outer sleeve surface of the sleeve, the second pin engaging a seal ring lower recess formed by an underside of the seal ring.

15. the first alignment element engages a first seal ring, the first seal ring being disposed about a first interface between the first end cover and the sleeve; and 12. The pressure exchanger of claim 11, wherein the second alignment element engages a second seal ring, the second seal ring being disposed about a second interface between the second end cover and the sleeve.

16. 1. A pressure exchanger seal ring assembly, comprising: a seal ring having an inner surface defining a first groove and a second groove; a first gasket configured to be disposed in the first groove; and a second gasket configured to be disposed in the second groove, wherein the pressure exchanger seal ring assembly is disposed around an interface between an end cover of a pressure exchanger and a sleeve of the pressure exchanger to prevent leakage between the sleeve and the end cover, wherein the first gasket interfaces with an end cover outer surface of the end cover and the second gasket interfaces with a sleeve outer surface of the sleeve.

17. The pressure exchanger seal ring assembly comprises: A first pin, a first distal end configured to be disposed within an upper seal ring recess defined by an upper surface of the seal ring; 17. The pressure exchanger seal ring assembly of claim 16, further comprising: a first pin having a second distal end configured to be radially inserted into an end cover recess formed by the end cover outer surface of the end cover.

18. The pressure exchanger seal ring assembly comprises: A second pin, a first distal end configured to be disposed within a lower seal ring recess defined by a lower surface of the seal ring; 17. The pressure exchanger seal ring assembly of claim 16, further comprising a second pin having a second distal end configured to be radially inserted into a sleeve recess formed by the outer sleeve surface of the sleeve.

19. 17. The pressure exchanger seal ring assembly of claim 16, wherein the first gasket is a first O-ring and the second gasket is a second O-ring.

20. 17. The pressure exchanger seal ring assembly of claim 16, wherein the sleeve is configured to be disposed about a rotor of the pressure exchanger, the rotor configured to exchange pressure between a first fluid and a second fluid, and the end cover is configured to be disposed at a first distal end of the rotor.

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