system and method of submersible fluid to operate submerged in a body of water

专利摘要:
UNDERWATER MULTIPHASE COMPRESSOR OR PUMP WITH MAGNETIC COUPLING AND COOLING OR LUBRICATION BY LIQUID OR GAS EXTRACTED FROM PROCESS FLUID This is a submersible fluid system to operate submerged in a body of water that includes an electrical machine and a fluid end. The fluid end includes a fluid end housing which has an inlet for a fluid rotor, the fluid rotor being coupled to the electrical machine and carried to rotate in the housing by a bearing in the housing. A fluid separator system receives a multiphase fluid and communicates a flow of fluid to the inlet and a substantially liquid flow withdrawn from the multiphase fluid to the bearing.
公开号:BR112015005589B1
申请号:R112015005589-3
申请日:2012-09-12
公开日:2021-04-20
发明作者:Christopher E. Cunningham；Co Si Huynh
申请人:Fmc Technologies, Inc；
IPC主号:

专利说明:

BACKGROUND OF THE INVENTION
[001] The operation of fluid systems such as pumps, compressors, mixers, separators and other such systems submerged underwater is difficult because the operating environment is harsh, particularly if that environment is deep seawater . The water that surrounds the system and often the process fluid that flows through the system is corrosive. The environment can be cold, making many materials brittle and causing large thermal expansion/contraction of equipment as equipment cycles between hot operating and cold non-operating states. The hydrostatic pressure of water and/or process fluid can be substantial. In addition, installation and access to fluid systems for maintenance and repair is difficult and costly due to the fact that the systems are often placed in geographically remote locations and at depths inaccessible by divers, therefore requiring ships built for this purpose, team specialized and robotic equipment. SUMMARY OF THE INVENTION
[002] The concepts in this document encompass a submersible fluid system to operate submerged in a body of water. The system can include an electrical machine. The system can also include a fluid end that includes a housing that has an inlet for a fluid rotor. The fluid rotor can be coupled to the electrical machine and carried to rotate in the housing through a bearing in the housing. A fluid separator system can receive a multiphase fluid and dispense multiphase fluid flows to the inlet and a substantially liquid flow drawn from the multiphase fluid to the bearing (e.g., by means of a reservoir). In some deployments, the fluid for the bearing can be gas or substantially gas.
[003] The concepts in this document encompass a method that includes operating, at a depth underwater, an electrical machine and a fluid end. The fluid end may include a fluid end housing which has an inlet for a fluid rotor, the fluid rotor is coupled to the electrical machine and carried to rotate in the housing by a bearing in the housing. The method may include operating a fluid separator system that receives a multiphase fluid and communicates a flow of fluid to the inlet and a substantially liquid flow drawn from the multiphase fluid to the bearing.
[004] The concepts in this document encompass a submersible fluid system to operate submerged in a body of water. The submersible fluid system can include an electrical machine and a fluid end. The fluid end may include a fluid end housing which has an inlet for a fluid rotor. The fluid rotor can be coupled to the electrical machine and includes a cavity that surrounds a driving end of the fluid rotor. The system may also include a fluid separator system that receives a multiphase fluid and communicates a flow of fluid to the inlet and another flow of substantially gaseous extracted from the multiphase fluid to the cavity surrounding the driving end of the fluid rotor.
[005] The above concepts may cover some, none, or all of the following features.
[006] In certain cases, the fluid rotor is carried to rotate in the housing through the first mentioned bearing around one end of the fluid rotor and a second bearing around a second end of the fluid rotor and wherein the system of fluid separator communicates a flow of liquid extracted from the multiphase flow to said first bearing and the second bearing. In certain cases, the liquid flow extracted from the multiphase fluid is at a temperature below the bearing temperature. In certain cases, the fluid separator system distributes the fluid to a cavity that surrounds the fluid rotor near the driving end. In certain cases, the driving end of the fluid rotor is coupled to an electric machine rotor of the electric machine through a magnetic coupling and the fluid separator system further distributes the fluid flow to a gap between a portion of the magnetic coupling. in the fluid rotor and a portion of the magnetic coupling in the electric machine rotor. In certain cases, the fluid separator system further distributes a substantially gaseous flow extracted from the multiphase fluid into the cavity surrounding the driving end of the fluid rotor. In certain cases, the fluid separator system further distributes the substantially gaseous flow extracted from the multiphase fluid to a gap between a portion of the magnetic coupling on the fluid rotor and a portion of the magnetic coupling on the electric machine rotor. In certain cases, the fluid separator system includes a separator tank. The separator may include an inlet for the multiphase fluid. A primary outlet may be around the bottom of the separator tank and coupled to the fluid end inlet. The system may include an outlet around the top of the separator tank and coupled to the fluid end housing (e.g., via the motor) to substantially supply gas to the cavity surrounding the fluid rotor drive rod head. In certain cases, the additional outlet comprises an upwardly extending tube configured to release sand from a stream of liquid flowing through the liquid outlet. In certain cases, the system may include a reservoir tank, the reservoir tank is between the additional outlet and the fluid end housing to receive and store liquid from the additional outlet to supply the fluid end when no liquid is being produced to from the additional output. In certain cases, the separator tank also includes an outlet around the top of the separator tank and coupled to the fluid end housing to substantially supply gas to a cavity surrounding a driving end of the fluid rotor. The reservoir tank may be between the outlet around the top of the separator tank and the fluid end for receiving fluid from the separator tank to convey liquid from the reservoir in the event that no liquid is being produced from the outlet. additional and the exit is closed. In certain cases, the system may also include an auxiliary liquid source in fluid communication with the bearing. In certain cases, the auxiliary liquid source comprises at least one of a treatment liquid also being added to the multiphase fluid apart from the submersible fluid system or liquid from an outlet downstream of the fluid end.
[007] In certain cases, operating the fluid end includes rotating the fluid rotor while being carried by the said first bearing around one end of the fluid rotor and a second bearing around a second end of the fluid rotor. In certain cases, the fluid separator system communicates a substantially liquid flow drawn from the multiphase flow to the first mentioned and the second bearings. In certain cases, the separating fluid communicates a substantially gaseous flow extracted from the multiphase fluid to a cavity surrounding a driving end of the fluid rotor. In certain cases, the driving end of the fluid rotor is coupled to an electric machine rotor of the electric machine through a magnetic coupling, and the fluid separator system further distributes a fluid flow to a gap between a portion of the magnetic coupling. in the fluid rotor and a portion of the magnetic coupling in the electric machine rotor. In certain cases, the fluid separator system further distributes a flow of gas extracted from the multiphase fluid to a cavity surrounding the driving end of the fluid rotor. In certain cases, multiphase fluid is received in a separator tank. The separator tank may include an inlet for the multiphase fluid. The separator tank may also include a primary outlet around the bottom of the separator tank and coupled to the fluid end inlet. An additional outlet can be around the bottom of the separator tank and coupled to the fluid end housing. In certain cases, the driving end of the fluid rotor is coupled to an electric machine rotor of the electric machine through a magnetic coupling and the fluid separator system further distributes the substantially gaseous flow extracted from the multiphase fluid to a gap between a magnetic coupling portion in fluid rotor and a magnetic coupling portion in electric machine rotor. In certain cases, the fluid rotor is carried to rotate in the housing through a bearing in the housing and the fluid separator system distributes a substantially liquid flow drawn from the multiphase fluid to the bearing. BRIEF DESCRIPTION OF THE DRAWINGS
[008] Figure 1 is a side view of an exemplary fluid system.
[009] Figure 2A is a side cross-sectional view of an exemplary integrated electrical machine and fluid end that can be used in the exemplary fluid system of Figure 1.
[010] Figure 2B is a side cross-sectional view of a fluid inlet portion and the magnetic coupling between an electrical machine rotor and a fluid end rotor in the exemplary fluid system of Figure 2A.
[011] Figure 2C is a side cross-sectional view of an exemplary fluid end manifold and outlet portion of Figure 2A.
[012] Figure 3 is a schematic flow of the exemplary fluid system in Figure 1. DETAILED DESCRIPTION OF THE INVENTION
[013] Fluid systems of the type disclosed herein operate on fluids ("process fluids") that may comprise substantially single phases, for example, water, oil or gas, or a mixture of more than one phase (" multiphase") which may include two or more phases and often entrained solids, e.g. sand, metal particles and/or rust flakes, wax agglomerations and/or steel scale, etc. Figure 1 is a side view of an exemplary fluid system. Figure 1 shows an exemplary fluid system 100 constructed in accordance with the concepts described herein. Fluid system 100 includes a fluid end 102 coupled to an electrical machine 104. In certain cases, fluid system 100 may also include a fluid separator system 108.
[014] Fluid system 100 may be operated submerged in open water, for example, outside an injection well or hydrocarbon production in a lake, river, ocean, or other body of water. To that end, fluid end 102 and electrical machine 104 are packaged within a sealed pressure vessel to prevent fluid passage between the interior of the pressure vessel and the surrounding environment (e.g., surrounding water). Components of fluid system 100 are constructed to tolerate ambient pressure around fluid system 100 and thermal loads exerted by the surrounding environment, as well as pressures and thermal loads incurred when operating electrical machine 104 and fluid end 102.
[015] In certain cases, for example, subsea applications, fluid end 102, electric machine 104 and fluid separator system 108 may be carried on a slider 110 or other fluid system structure 100 that aligns with, and engages other subsea structures, for example, by means of guide tubes 112 that capture guide posts from a corresponding subsea structure, or through the interaction of a large cone-to-cone-plus-pin-and-cam arrangement (not shown, but familiar to those skilled in the art of subsea systems without guide lines (guidelineless)). When the fluid system is termed a "subsea" fluid system, it is not to say that the fluid system is designed to operate only undersea. Instead, the subsea fluid system is of a type that is designed to operate under the rigors found on or near the bottom of an open body of water, such as an ocean, lake, river, or other body of salt water. or sweet. An auxiliary liquid source 114 may interface with slider 110 to supply liquids to the system, e.g., corrosion inhibiting chemicals, steel scale and hydrate.
[016] One or more buffers 120 may be affixed to the exterior of the fluid system 100 to cushion the fluid system 100's impact with surfaces, such as on a subsea structure or a transport ship deck. Buffers 120 can be configured to maintain a level orientation of fluid system 100 in situations where the surface is not level. Dampers 120 can be fluid dampers or other types of shock or impact absorbing devices.
[017] As described in greater detail below, the electrical machine 104 is an alternating current (AC), synchronous, permanent magnet (PM) electrical machine that has a rotor that includes permanent magnets and a stator that includes a plurality of windings of cable or formed and a core (typically) of stacked laminations. In other cases, the electrical machine 104 may be another type of electrical machine such as an asynchronous, AC induction machine in which both the rotor and stator include windings and laminations, or even another type of electrical machine. The electrical machine 104 can operate as a motor that produces mechanical motion from electricity, a generator that produces electrical power from mechanical motion, or alternates between generating electrical power and running. During operation, the mechanical movement output of the electrical machine 104 can drive fluid end 102. In generation, the fluid end 102 supplies mechanical movement to the electrical machine 104, and the electrical machine 104 converts the mechanical movement into electrical power.
[018] In cases where the fluid end 102 is driven by electrical machine 104, the fluid end 102 may include any one of a variety of different devices. For example, fluid end 102 may include one or more rotary and/or piston pumps, rotary and/or reciprocating compressors, mixing devices, or other devices. Some examples of pumps include centrifugal, axial, rotary vane, sprocket, spiral, lobe, progression cavity, reciprocating, plunger, diaphragm, and/or other types of pumps. Some examples of compressors include centrifugal, axial, rotary vane, spiral, reciprocating and/or other types of compressors, including that class of compressors sometimes referred to as "wet gas compressors" that can accommodate a higher liquid content in the gas stream. than is typical for conventional compressors. In other cases, the fluid end 102 may include one or more of a fluid engine operable to convert fluid flow to mechanical energy, a gas turbine system operable to ignite an air/fuel mixture and convert combustion energy. in mechanical energy, an internal combustion engine mechanism and/or another type of motor agent. In either case, the fluid end 102 can be a single or multi-stage device.
[019] Although Figure 1 illustrates a vertically oriented electrical machine 104 coupled to a vertically oriented fluid end 102, other implementations may provide a horizontally oriented electrical machine coupled to a horizontally oriented fluid end, a vertically oriented electrical machine 104 coupled to a horizontally oriented fluid end 102, a horizontally oriented electrical machine 104 coupled to a vertically oriented fluid end 102, as well as yet other electrical machine 104 and fluid end 102 orientations, including non-aligned and non-perpendicular arrangements.
[020] Although shown with a single end of fluid 102, the electrical machine 104 can also be coupled to two or more ends of fluid 102 (to drive and/or be driven by the ends of fluid 102). In certain cases, one or more fluid ends 102 may be provided at each end of electrical machine 104, and in no orientation with respect to electrical machine 104. For example, in a configuration with two fluid ends 102, one may be provided. at one end of electrical machine 104 and the other provided at an opposite end of electrical machine 104, and the fluid ends 102 may be oriented at different angles relative to electrical machine 104. In another example, a configuration with two fluid ends 102 may have one provided at an electrical machine end 104 and the other coupled to the first fluid end 102. In addition, if multiple fluid ends 102 are provided, they need not all be of the same type of device and they do not they need to operate in the same fluid, that is, they can operate in different fluids.
[021] Figure 2A is a side cross-sectional view of an exemplary electrical machine 202 and fluid end 204 that can be used in the exemplary fluid system 100 of Figure 1. The fluid end 204 includes a fluid rotor 206 disposed in a fluid end housing 208. The fluid end housing 208 contains process fluids that flow from an inlet 250 near the electrical machine 202 to an outlet 272 distal to the electrical machine. Electric machine 202 is carried by and contained within an electric machine housing 210 secured to fluid end housing 208 of fluid end 204 by cable terminator 214a. The electrical machine housing 210 is secured at the upper end thereof to the cable terminator 214b, which is secured to the cap 233. The aforementioned attachments are sealed to create an electrical pressure vessel encapsulation machine 202 that prevents the passage of fluid between the interior of it and the surrounding environment (eg water). Another collection of parts and interfaces (described later in this disclosure) prevents the passage of fluid between the electrical machine 202 and the fluid end 204. As a result of the aforementioned barriers, the electrical machine 202 operates in its own fluid environment, which can be gas or liquid depending on specific offsets (with preferred gas from an overall system efficiency perspective). Figure 2A shows a closely coupled submerged fluid system 200 in which electrical machine structural elements 202 directly attach to fluid end structural elements 204.
[022] The electric machine 202 disposed within the electric machine housing 210 includes an electric machine stator 218 and an electric machine rotor 220. The electric machine housing 210 is coupled to the fluid end housing 208 and includes a hermetically cavity fenced. The cavity has a gas at a pressure less than the hydrostatic pressure at the specified underwater depth. The electric machine 202 is disposed within the cavity of the electric machine housing. Electric machine stator 218 interfaces with an external power source through penetrators / connectors 238 which pass through lower cable terminator 214a. It is known to those skilled in the art of underwater electrical power interconnect systems that minimizing pressure differential acting across such interfaces is recommended for long-term success. Electric machine rotor 220 is magnetically coupled to rotate with process fluid rotor 206 with a magnetic coupling 258. In other cases, a mechanical coupling may be used. Electric machine rotor 220, which may be tubular, includes a rotor shaft (or core in the case of an AC machine) 221 and permanent magnets 226 affixed to the outside of rotor shaft 221, particularly in an area close to the core of stator 222. Magnetic coupling 258 couples electric machine rotor 220 and fluid rotor 206 to rotate at the same speed and without contact (ie, magnetic coupling out of contact). Fluid rotor 206 is arranged to rotate in fluid end housing 208 and receive and interact with a process fluid flowing from inlet 250 to outlet 272 of fluid end housing 208. Fluid rotor 206 is set to push vertically toward the top edge when rotating.
[023] The permanent magnets 226 are fixed to the rotor shaft 221 by a sleeve 228 including any material and/or material construction that does not adversely affect the magnetic field and that satisfies all other functional and design requirements. In certain cases, sleeve 228 may be made of a suitable non-ferrous metal, for example, American Iron and Steel Institute (AISI) 316 stainless steel or a nickel and chromium alloy, for example, Inconel (a product of Inco Alloys, Inc.), or may include a composite construction of high strength fibers such as carbon fiber, ceramic fiber, basalt fiber, aramid fiber, glass fiber and/or other fibers in, for example, a thermoplastic matrix. or thermoset. Permanent magnets 226 provide a magnetic field that interacts with a magnetic field from stator 218 to at least one of rotating electrical machine rotor 220 relative to stator 218 in response to electrical power supplied to stator 218, or to generate electricity in stator 218 when rotor 220 is moved relative to stator 218.
[024] The electric machine rotor 220 is supported to rotate in the stator 218 by magnetic bearings 230a and 230b separated at a significant distance from the electric machine rotor length 220, and typically, but not essentially, close to the rotor ends of electrical machine 220. In at least one alternative to the configuration shown in Figure 2A, the magnetic bearing 230a can be positioned closer to the stator core 222 so that a substantial portion or even all of the magnetic coupling 258 extends beyond the bearing. magnetic 230a in what is known to those skilled in the art of rotating machinery as an engineered configuration. Magnetic bearing 230a is a combination ("combo") magnetic bearing that supports electric machine rotor 220 both axially and radially, and magnetic bearing 230b is a radial magnetic bearing. In the case of a vertically oriented electrical machine 202, a passive magnetic lifting device 254 can be provided to carry a significant portion of the electrical machine rotor 220 weight to reduce the capacity required for the axial portion of magnetic combo bearing 230a, enabling less optimized size and dynamic performance for 230a combo bearing. Machines incorporating magnetic bearings typically also include booster bearings 231a and 231b to compress the motor rotor 220 as it rotates to an interruption in the event that the magnetic bearings cease to be effective, for example, due to loss of power or another glitch. Reinforcement bearings 231a, 231b will support motor rotor 220 whenever magnetic bearings 230a, 230b are not energized, for example, during fluid system transport 100. The number, type and/or placement of bearings in electrical machine 202 and fluid end 204 may be different for different fluid system 100 configurations.
[025] Other electrical machine elements 202 are closely associated with integrated fluid end 204, and an overview of some higher level attributes for submerged fluid system 200 at this juncture may facilitate the reader's understanding of the functions and nature of integrated operation of those other electrical machine elements 202.
[026] Certain subsea fluid system modalities 200 may include: An electrical machine 202 whose contents operate in a gas environment at atmospheric pressure nominally 1 that delivers fewer losses than existing technologies (for example, while housing an electrical machine of which 210 is externally exposed to potentially deep water and associated high pressure); an electric machine 202 using magnetic bearings 230a, 230b for additional loss savings when compared to machines operating in a submerged liquid environment with the use of, for example, fluid film bearings or laminating element; a magnetic coupling 258 for which an inner portion 262 is contained in potentially very high pressure process fluid and is isolated from the associated outer portion thereof 293 located within the nominally 1 atmospheric pressure environment of the electrical machine 202 through a static (non-rotating) sleeve 235 which, together with its associated static (non-rotating) end seals 246, 248 are capable of tolerating the large pressure differential acting therethrough; an electrical machine 202 which, because of the operating environment of atmosphere 1, the use of magnetic bearings 230a, 230b, and the use of a magnetic coupling(s) 258 to engage the integrated fluid end(s) thereof 204, produces much less heat during operation when compared to other known technologies (used in submerged fluid 200 system applications) and can therefore transfer heat from it to the surrounding environment using low passive, durable materials. cost and techniques (not including any circulated refrigerant and associated pump impeller, etc.); a way to cool the magnetic coupling 258 which, under certain circumstances, can allow the submerged portion of process fluids of that coupling to rotate within a gas core (with corresponding lower loss and other benefits); one or more fluid ends 204 employing fluid film bearings 264a, 264b, 274 or any other types of bearings lubricated and cooled by process fluid (e.g., water or oil or a combination thereof) or alternative fluid; one or more fluid ends 204 employing bearings 264a, 264b, 274 provided as fluid film bearings, magnetic bearings or any other types of bearings at those same locations or different locations, or a combination of any types of bearings; a vertical top inlet/bottom outlet fluid end arrangement 204 that provides a manifold 271 at the bottom end thereof for securing fluid film bearings 264b, 274 in a useful environment.
[027] Although the contents of electric machine 202 have previously been described as operating in a nominally 1 atmosphere pressure environment, the fluid system 200 may alternatively be configured to maintain the contents of electric machine 202 in an environment compensated to be substantially equal to the water pressure around the 200 fluid system.
[028] Although the magnetic coupling 258 has been previously described with the inner portion 262 in the process fluid and the outer portion 293 in the atmosphere pressure environment nominally 1 of electrical machine 202, as an alternative, the magnetic coupling 258 may be provided of the opposite topology, having an inner portion in the atmosphere pressure environment nominally 1 and an outer portion in the process fluid.
[029] Electric machine housing 210 (and associated parts) plus magnetic coupling 258 combined with sleeve 235 (and associated parts) establish three substantially separate environments that can be exploited to unprecedented value for submerged fluid systems 200, i.e. : A process gas environment potentially within sleeve 235 at the upper end of fluid end 204 (otherwise multiphase process fluid or liquid); an atmosphere gas environment nominally 1 outside sleeve 235 and inside electrical machine housing 210; an underwater environment outside the electrical machine housing 210 (and also outside the fluid end housing 208). In an alternative embodiment, the environment within the electrical machine housing 210 may be pressurized (e.g., with gas or liquid) a little or a lot (i.e., any of several levels up to and including that of the process fluid), with corresponding compensations in overall system efficiency (increased losses), possibly different cross-section for, for example, electrical machine housing 210, upper sleeve 296 and lower sleeve 298, reduced sleeve cross-section 235 and therefore increased coupling efficiency magnetic 258, different pressure field through eg electrical power penetrators, different heat management considerations, etc. With the foregoing context, further description will now be provided for electrical machine components 202 and other subsea fluid system components 200.
[030] Consistent with the present disclosure, it should be understood that the process fluid can be used to lubricate and cool fluid film bearings or other types of bearings 264a, 264b, 274 at the fluid end 204, and to cool the magnetic coupling 258. It is further understood that the process fluid in liquid form will best satisfy the requirements for cooled and lubricated process bearings (not applicable if the fluid end 204 uses magnetic bearings), and that the process fluid containing at least some gases can benefit the coupling-cooling application, i.e., reducing drag loss associated with movement of the process fluid rotor 206 and conducting heat from within sleeve 235. Observed applications may originate from any one of, or more than one of, several locations in relation to the submerged fluid system 200 depending on the properties of the fluid d. and process at such source location(s) (eg, water, oil, gas, multiphase), the pressure of such source(s) in relation to the point of use, and the properties required of the fluid at the point of use. For example, process fluid may come upstream from submerged fluid system 200, such as from buffer tank 278, liquid reservoir 284, or other sources including some not associated with the process stream passing through submerged fluid system 200 and /or some associated with the process stream passing through the submerged fluid system 200 which undergo, for example, preconditioning prior to joining the process stream passing through the submerged fluid system 200 (e.g. a well stream which is throttled to a lower pressure before being mixed with one or more lower pressure stream streams including the stream stream which finally enters the submerged fluid system 200). Process fluid may be sourced from within submerged fluid system 200 itself (for example, from any one of submerged fluid system 200 pressure rise stages, near outlet 272, from manifold 271 and/or immediately adjacent to the respective desired point of use). The process fluid may be sourced downstream of the submerged fluid system 200, for example, from the downstream process flow stream directly or from the liquid extraction unit 287, among others. Non-process stream fluids can also be used for lubrication and cooling, such as chemicals available at the seabed location (which is normally injected into the process stream to inhibit corrosion and/or the formation of, for example, hydrates and/or deposition of asphaltenes, steel scale, etc.).
[031] In cases where the upstream process fluid is used for lubrication and/or cooling, and the source does not exist at a pressure greater than that at the intended point of use, such process fluid may need to be "boosted" . That is, the pressure of such a process fluid can be increased using, for example, a dedicated/separate ancillary pump, an integrated impeller with a rotating element within the subsea fluid system 200, or by some other means. In certain deployments, the pressure drop across the fluid end inlet homogenizer (i.e., mixer) 249 can create a sufficient pressure bias to deliver desired fluids from upstream thereof to, for example, upper radial bearing. 264a and coupling chamber 244, the latter being the space surrounding the inner magnetic coupling portion 262 and residing within the sleeve 235 (such implementation is discussed further herein).
[032] Regardless of the source of process fluid, it can be refined and/or cleaned prior to delivery to the point(s) of use. For example, multiphase fluid can be separated into gas, one or more liquid streams, and solids (e.g. sand, metal particles, etc.), with solids typically diverted into the end flow of fluid 204 through the inlet main of the same 250 and/or collected for removal. Such fluid separation can be achieved with the use of, for example, gravitational means, cyclonic and/or magnetic centrifuges (among other mechanisms) to achieve desired fluid properties for each point of use. After the fluid has been cleaned, it can also be cooled by passing the refined fluid through, for example, thin-walled pipes and/or thin plates separating small channels, etc. (ie, heat exchangers) exposed to the water surrounding fluid system 200.
[033] The electrical machine 202 includes a cap 233 attached to the upper cable terminator 214b. For the configuration shown in Figure 2A, connecting rod 234 is downwardly pressed onto sleeve 235 via spring mechanism 239 reacting between shoulder bearing ring 240 and shoulder bearing ring 289. Cable terminator 214b, machine housing electrical 210, cable terminator 214a, fluid end housing 208, sleeve support ring 270, and various fasteners associated with the preceding items close the axial load path for connecting rod 234 and sleeve 235. Connecting rod 234 contains a conduit internal axial 242 that connects the process environment within the sleeve 235 with a cavity provided between the upper end of the connecting rod 234 and the underside of the cap 233. The cap 233 includes a conduit 245 that connects this underside cavity with external service conduit 290 which delivers, for example, process-sourced coolant to the coupling (described previously). Pressurized fluid transported through the observed conduits fills the cavity below cap 233 and acts on connecting rod 234 through bellows 288, piston 286 and liquid supplied between bellows 288 and piston 286. Piston seal diameter 286 is dictated by sleeve seal diameter 235 and the force created by spring mechanism 239, and is specified to ensure a substantially constant compressive axial load on sleeve 235 independent of, for example, pressure and temperature acting on the inside and outside of the fluid system subsea 200. For other variants of subsea fluid system 200, the aforementioned elements are modified to ensure an axial load of substantially constant tension is maintained in sleeve 235. Sleeve 235 may be a cylinder. Sleeve 235 may be substantially non-magnetic which defines a substantially non-magnetic wall, for example made of a non-magnetic material. In certain cases, sleeve 235 can be made of an electrically conductive material which, although it experiences an associated magnetic field, the effects of such a magnetic field can be practically mitigated. Sleeve 235 may include a substantially non-conductive wall.
[034] In certain cases, sleeve 235 may be a gas-impermeable glass and/or ceramic cylinder held "in compression" for all load conditions expected by an integrated support system, for example, external compression sleeve 292 for radial support and connecting rod 234-plus sleeve support ring 270 for axial support. Sleeve 235 including external compression sleeve 292 are ideally made of materials and/or constructed in such a way as not to significantly obstruct the magnetic field of magnetic coupling 258, and generate little, if any, heat from, by example, eddy currents associated with the coupling rotating magnetic field. In certain cases, the outer compression sleeve 292 may be a composite construction of high strength fibers such as carbon fiber, ceramic fiber, basalt fiber, aramid fiber, fiberglass and/or other fiber in, for example, a thermoplastic or thermoset matrix. In certain cases, sleeve 235 may have metallized end surfaces and/or other treatments to facilitate, for example, a metal-to-metal seal with the mating surfaces of connecting rod 234 and sleeve support ring 270.
[035] In certain embodiments of the subsea fluid system 200, the electrical machine 202 is filled with gas, for example, air or an inert gas such as nitrogen or argon, at or near atmosphere pressure 1. Unlike vacuum, which it is difficult to establish and maintain, and since it provides low heat transfer properties, a very low gas pressure environment provides the best conditions to operate an electrical machine efficiently (eg, low drag loss, etc.), assuming that the heat produced by the machine can be efficiently removed.
[036] When submerged in deep water the pressure outside the gas filled electric machine 202 will collapse, for example, the electric machine housing 210 if it is not adequately strong or internally supported. In certain embodiments of the subsea fluid system 200, the electrical machine housing 210 is thin and possibly "finned" to improve heat transfer between the electrical machine 202 and the surrounding environment. Machine housing 210 may be fitted tightly around stator core 222 and sleeves 296, 298, and the ends thereof similarly may be fitted securely over support surfaces provided on cable terminators 214a, 214b. The structures supporting the machine housing 210 are sized to be strong enough for that purpose, and when practical (eg for sleeves 296, 298) these structures can be made using materials with a useful balance of strength properties for mass and heat transfer (eg carbon steel, low alloy steel and selected stainless steels, including 316 stainless steel materials, and high-copper materials, including beryllium copper, respectively, among others).
[037] Figure 2B is a side cross-sectional view of a fluid inlet portion and magnetic coupling 258 between an electrical machine rotor 220 and a fluid end rotor 206 in an exemplary fluid system 200 of Figure 2A . Permanent magnets 236a, 236b are affixed to an inner diameter of the rotor shaft of the electric machine 221 and an outer diameter of the upper end 207 of the process fluid rotor 206, respectively. The magnets 236a, 236b are unitized to the respective rotors thereof by sleeves 237a, 237b, and these sleeves also serve to isolate the magnets from their respective surroundings. Sleeves 237a, 237b are ideally made of materials and/or constructed in such a way as not to significantly obstruct the magnetic field of magnetic coupling 258, and generate little heat, if any, from, for example, associated eddy currents. with the coupling rotating magnetic field. In certain cases, sleeves 237a, 237b may be cylinders and made of a suitable non-ferrous metal, eg, AISI 316 stainless steel or nickel and chromium alloy, eg, Inconel (a product of Inco Alloys, Inc.), or they may include a composite construction of high strength fibers such as carbon fiber, ceramic fiber, basalt fiber, aramid fiber, glass fiber and/or other fiber in, for example, a thermoplastic or thermosetting matrix. Magnetic fields produced by permanent magnets 236a, 236b interact through sleeve 235 to magnetically lock (for rotational purposes) electrical machine rotor 220 and process fluid rotor 206, thereby forming magnetic coupling 258.
[038] Friction between the rotating process fluid rotor 206 and the fluid within the coupling chamber 244 tends to "drag" the latter together (in the same direction) with the former (and resists movement of the former, consuming energy ), but as friction also exists between static sleeve 235 and said fluid (tends to resist fluid movement), the fluid will typically not rotate at the same speed as the process fluid rotor 206. Centrifugal forces will be established in the fluid of rotation process that will cause heavier elements (eg, solids and dense liquid components) to move outward (toward sleeve 235) while lighter elements (eg, less dense liquid components and gas that can having been mixed with heavier elements before being "spun") will be relegated to a central core, close to the rotating process fluid rotor 206. The relative movement described between the mechanical parts and the fluid, and between di. Different components of the fluid, among other phenomena, produce heat which is subsequently removed from the coupling chamber 244 through various mechanisms. Less heat will be generated and less energy will be consumed by rotating process fluid rotor 206 if the fluid close to rotating process fluid rotor 206 has low density and is easily sheared, which is characteristic of gas. Fluid system 100 can supply gas to coupling chamber 244 whenever gas is available from the process stream, for example, through internal axial conduit 242 of connecting rod 234 (and associated conduits). Regardless of the fluid properties within coupling chamber 244, this fluid (made hot through shear, etc.) can be displaced with coolant fluid to prevent overheating near surrounding components and components (eg, engine).
[039] The fluid inlet portion of Figure 2B is located next to the electric machine 202 and magnetic coupling 258. The process fluid enters the fluid end 204 through three conduits before being combined immediately upstream of the first impeller 241 at the flow mixing area of all inlets 243. As none of these three flows (described in more detail below) typically originate downstream of subsea fluid system 200, they were not acted upon by subsea fluid system 200 and do not constitute a "loss" for general system efficiency calculation purposes.
[040] Most of the process fluid enters the fluid end 204 through the main inlet 250. The coupling refrigerant enters the electrical machine 202 through a port 245 in the hood 233, and is directed to the coupling chamber 244 through of conduit 242. Radial bearing coolant 264a enters through port 260 to join gallery 262, from which it is directed through ports 251 to bearing chamber 247. For the purpose of current discussion, the fluid of process entering fluid end 204 should be anticipated to come from a common source close to subsea fluid system 200 (not shown in Figure 2A) and therefore the pressure in main inlet gallery 252, coupling chamber 244 and chamber. mancai 247 can be predicted to be approximately the same. The mechanism that causes fluid to enter fluid end 204 through ports 260 and 245 with preferably lightweight and "tunable" to main inlet 250 is the pressure drop created through inlet homogenizer 249. inlet flow homogenizer chamber 251 and therefore refrigerant flow mixing chamber 253 (by virtue of their shared influence across the flow mixing area of all inlets 243) is smaller than the source of all flows inlet, which creates a pressure field sufficient to create the desired cooling flows.
[041] For the fluid in the coupling chamber 244 to reach the mixing chamber of refrigerant flows 253, it passes through the bearing 264a. It does this through bypass ports 269 provided in cage ring 268. In order for fluid in bearing chamber 247 to reach refrigerant flow mixing chamber 253, it first exits chamber 247 via either of the two routes . Most of the fluid exits chamber 247 through the opening between the upper inner hole of the cage ring 268 and the outer diameter of the rotor sleeve 267. Once in the coupling chamber 244, it mixes with the fluid of coupling cooling and reaches the mixing chamber of refrigerant flows through bypass ports 269.
[042] Fluid may also exit bearing chamber 247 via seal 256 to emerge in refrigerant flow mixing chamber 253. An example of a seal that can be used as seal 256 is more fully described below in relation to to seal 282 associated with manifold top plate 280. Seal 256 has a much smaller opening relative to rotor sleeve 267 than cage ring 268 (located on top of bearing 264a), and has a very high leakage rate. smaller as a result. This configuration encourages fluid entering bearing chamber 247 to exit therefrom at bearing upper end 264a. This tendency in combination with gravity and centrifugal forces pushing heavier fluid components (eg, liquids) downward and radially outward, respectively, also causes any gas that may have entered the fluid stream entering the bearing chamber. 247 moves radially inward so that it is exhausted immediately after the cage ring 268.
[043] Keeping the gas out of bearing chamber 247 and removing it quickly if it is present in bearing chamber 247 will promote good performance and long life for the 264a fluid film bearing. To increase the probability that active bearing surfaces 264a are constantly submerged in liquid (i.e., on the inside of surfaces of incline pads 266 and outside of the surface of rotor sleeve 267 adjacent to incline pads 266), incline pads 266 are positioned to interact with rotor sleeve 267 at a larger diameter than the spans (above and below tilt pads 266) that allow fluid to move out of bearing chamber 247. Gas separates from the liquid and moves towards the center of rotation in a rotating fluid system will ensure that gas moves out of bearing chamber 247 before liquids whenever gas is present within bearing chamber 247. Add an additional seal 256 that is positioned above the bearing chamber 247 can improve the ability to manage the gas inherently present in the process stream.
[044] In some embodiments of the subsea fluid system 200, the combined process fluid immediately upstream of the first impeller 241 in the flow mixing area of all inlets 243 is, downstream of it, increased in pressure through hydraulic stages including impellers attached to the process fluid rotor 206 interacting with intermeshed static diffusers (also known as stators). Static and dynamic seals are provided at appropriate locations within the hydraulic stages to minimize backflow from higher to lower pressure regions, thereby improving the hydraulic performance of fluid end 204.
[045] Figure 2C is a side cross-sectional view of a fluid outlet and manifold portion of an exemplary fluid end 204 of Figure 2A. There are five main regions of interest in this area separated by two significant functional elements. These elements are process fluid rotor thrust balancing devices 259 and manifold top plate 280. Above, around and below thrust balancing device 259 are final stage impeller 255, output gallery 257 of fluid end 204 and balancing circuit output device 261 (shown in Figure 2C as integrated with a manifold top plate 280, which is not a stringent requirement), respectively. Above and below the collector top plate 280 are the balancing circuit output device 261 and the collector 271, respectively.
[046] The higher pressure in certain embodiments of subsea fluid system 200 may occur immediately downstream of final stage impeller 255. Passing through openings 278 provided in balancing device stator 263, the process fluid enters the outlet gallery 257 at slightly lower pressure and exits to process fluid outlet 272 which is connected to a downstream piping system. The total pressure change from the final stage impeller 255 to the inlet point to the downstream pipe can be a reduction (small if, for example, care is taken in the design of fluid paths 278 of the stator of stator 263 , volute geometry is provided in exit gallery 257 and the transition from exit gallery 257 is carefully contoured, etc.) or an increase (for some modalities with some fluids to well executed volute).
[047] When a submersible fluid system 200 is not in operation, that is, when the process fluid rotor 206 does not rotate, the fluid that enters fluid end housing 208 at inlet 250 and flows beyond the hydraulic stages ( impellers/diffusers) to exit through outlet 272 will impart relatively little axial force on process fluid impeller 206. When process fluid impeller 206 rotates, the interaction of impellers, diffusers and associated components creates pressure fields that vary in magnitude depending on local fluid properties existing at many physical locations within fluid end 204. These pressure fields of multiple magnitudes act on various geometric areas of process fluid rotor 206 to produce substantial thrust. Such thrust generally tends to drive process fluid rotor 206 toward inlet 250, however, several operating scenarios can produce "reverse thrust". Depending on the magnitude and direction of thrust, thrust bearing 291 may have sufficient capacity to constrain process fluid rotor 206. In case the thrust acting on process fluid rotor 206 exceeds the capacity of an achievable thrust bearing 291, considering the many complex exchanges known to those skilled in the art of fluid end design, a thrust balancing device 259 can be used. Thrust bearing 291 is located near the lower end of fluid end housing 204. Thrust bearing 291 includes upwardly facing bearing surfaces on thrust collar 294 (coupled to fluid rotor 206) and bearing surfaces facing upwards. low in fluid end housing 208, the bearing surfaces cooperate to sustain upward thrust of fluid rotor 206. Similar components and associated surfaces are provided on the opposite side of thrust collar 294 to resist "reverse thrust" and the like. scenarios that make the fluid rotor 206 tend to move downward.
[048] Several types of impulse balancing devices are known, the two most common being called "magnetic disk" and "piston" (or "drum") types. Each device type has positive and negative attributes and sometimes a combination of the two and/or a completely different device is appropriate for a given order. Embodiments described herein include a piston-type thrust balancing device; however, other types can be implemented.
[049] A piston-type thrust balancing device is essentially a carefully defined diameter radial clearance rotary seal created between the process fluid rotor 206 and a corresponding interface to generate a desired pressure drop by exploiting pressure fields that already exist at the fluid end 204 to substantially balance the thrust loads acting on the process fluid rotor 206. The thrust balancing device includes two main components (not including process fluid rotor 206), however, a conduit of fluid (balance circuit conduit 276) connecting the low pressure side of impulse balancing device 259 to inlet pressure 250 is also provided. Balancing device rotor 265 is secured to process fluid rotor 206 in a manner that provides a tight seal therebetween. As an alternative, the balancer rotor profile 265 may be provided as an integral part of the fluid rotor 206. The balancer stator 263 is secured to the fluid end housing 208 through sealed interfaces with other components. . A small gap is provided between the balancing device rotor 265 and the stator 263 to establish a "rotating seal". High pressure from final stage impeller 255 acts on one side of balancing device rotor 265 while low pressure corresponding to that at inlet 250 acts on the other side. Inlet pressure 250 is maintained on the low pressure side of balancing device 259 independent of high pressure fluid leakage at low pressure throughout the clearance span (between balancing device rotor 265 and stator 263) due to the fact that such leakage is small compared to the volume of fluid that can be accommodated by the balancing circuit conduit 276. The balancing circuit output device 261 collects and redirects fluid exiting the balancing device 259 to deliver the same to the balance circuit conduit 27 6. The nominal diameter of the clearance gap (which defines the geometric areas where relevant pressures act) is selected to achieve the desired degree of residual thrust that needs to be carried by thrust bearing 291 (note that some residual is valuable from bearing loading and rotor dynamic stability perspectives).
[050] Back briefly to thrust bearing 291, the side that is normally loaded in operation is called the "active" side (upper side in Figure 2C), while the other side is called the "inactive" side. In certain embodiments, the active side of thrust bearing 291 is protected during high-risk long-term storage, shipping, transport, and allocation activities, while remaining "unloaded" during such activities. Specifically, process fluid rotor 206 "rests" on the idle side of thrust bearing 291 whenever subsea fluid system 200 is not in operation, for example, during storage, handling, shipping, and allocation. This arrangement is advantageous due to the fact that design attributes that increase tolerance, for example, to high impact loads during allocation, which, however, can reduce the normal operating capacity, can be deployed to the idle side of the bearing. thrust 291 without affecting the operating thrust capability of the fluid end 204. Such design attributes (among others) may include the selection of bearing pad materials that are tolerant to static loads and/or prolonged impact loads and that, however they do not have the highest operational capacity available. In addition, one or more energy absorbing devices 295, e.g. shock absorbers, springs, sticky pads (made of elastomeric and/or thermoplastic materials, etc.) and/or "crush" devices (ref. "crunch zones" in automobiles) may be added integral to and/or below thrust bearing 291, as well as external to fluid end housing 208 (including in slide 110 and/or shipping stands, travel tools, etc. - see damper 120 described in Figure 1). It may also be advantageous to "lock" the rotors 206, 220 so that they are prevented from "swinging" during, for example, transport, allocation, etc., or to support them in "decentralization" devices that prevent, for example, critical bearing surfaces to make contact during such events. Such locking and decentralization functionalities can be affected by using devices that can be engaged and/or released manually (eg, locking screws, etc.), or preferably devices that are automatically engaged/disengaged depending on whether the 206 , 220 are stopped, rotating, transitioning to stop, or transitioning to rotate. Devices that provide the attributes mentioned above include permanent magnetic and/or electromagnetic attraction devices, among others ("locking" devices) and bearing type bushings or cushion type supports/, among others, which have adequate geometry for the decentralization function while rotors 206, 220 do not rotate and have, for example, a "less intrusive" geometry that allows bearings (intended to support rotors 206, 220 during operation) to perform their functions when rotors 206, 220 rotate (devices for "decentralization"). Displacement mechanisms that can enable the desired "dual geometry" capability for "decentralization" devices include mechanical, hydraulic, thermal, electrical, electromagnetic, and piezoelectric, among others. Automatic passive means to order the locking and/or decentralizing functions can be used, however a control system can also be provided to ensure correct operation.
[051] Manifold top plate 280 in combination with seals 282 and 273 substantially isolate the fluid in manifold 271 from interacting with process fluid from fluid end 204. Manifold 271 contains fluid film type radial bearing 264b and bearing thrust pressure 291. To allow satisfactory performance and long service life, film fluid bearings are lubricated and cooled with clean liquid and the process fluid (especially crude hydrocarbon process fluid) may contain large volumes of gas and/or solids that could damage such bearings.
[052] The seal 282 may be substantially the same as the seal 256 associated with the upper radial bearing 264a described above. Seal 282 is secured to manifold top plate 280 and effects a hydrodynamic film fluid seal (typically a gap in the micrometer range) relative to rotor sleeve 275 (shown in Figure 2C as integrated with bearing sleeve 288, which is not a stringent requirement) when the process fluid rotor 206 is rotating and also a static seal (typically zero clearance) when the process fluid rotor 206 is not rotating. In certain examples, seal 282 may include a plurality of pads biased inwardly against the rotor shaft to provide static seal, but allow formation of the hydrodynamic film fluid seal when the rotor is rotating. Seal 282 can be designed to maintain, increase or decrease its hydrodynamic clearance, even for zero clearance in operation, when subjected to differential pressure transients from both sides (above or below) and therefore to maintain, increase or decrease substantially, respectively, its leakage rate during especially sudden pressure transients. The 282 seal includes features that allow its hydrodynamic performance that allows a small amount of leakage in dynamic (regardless of clearance magnitude relative to rotor sleeve 275) and static performance modes whenever it is exposed to differential pressure and therefore can be characterized for some applications as a flow restrictor rather than an absolute seal. A small amount of leakage is desired for manifold 271 application. Seals 273 and 282 seal between fluid end housing 208 and fluid rotor 206 and define an upper enclosure of a manifold 271 of fluid end housing 208 A fluid bearing 291 resides in the manifold 271 and the seal 282 is responsive to provide a tighter seal when subjected to a change in pressure differential between the manifold and another portion of the fluid end housing.
[053] Prior to allocation and with the use of port(s) 277 provided for such purpose (as well as for refilling the gas and/or debris discharge collector and/or collector, etc.), the manifold 271 can be filled with a fluid that ideally has attractive properties for the target field application, for example, chemically compatible with process fluid and chemicals that can be introduced into the process stream and/or manifold 271, higher density than process fluid, useful viscosity over a wide temperature range, satisfactory heat transfer performance, low gas absorption tendency, etc. Following installation and upon commissioning (during which the subsea fluid system 200 is operated), the fluid end 204 will be pressurized according to its design and the temperature of the collector 271 will rise significantly, with the latter doing the collector fluid expand. The ability of the seal 282 to transfer fluid axially in both directions ensures that the pressure in the manifold 271 is not significantly increased as a result and further ensures that the pressure in the manifold 271 substantially matches the inlet pressure 250 of the fluid end 204 during operational and non-operational states, except during axial position transients of the 206 process fluid rotor (explained below).
[054] The low leak rate, static seal, and hydrodynamic seal capabilities of the 282 seal, combined with an otherwise "sealed" 271 manifold, provide unique and valuable attributes for the 204 fluid end. The 282 seal provides a low leakage rate even when subjected to sudden high differential pressure and therefore equalizes pressure more or less gradually depending mainly on the initial pressure differential and fluid properties involved (eg liquid, gaseous, multiphase, high/low viscosity , etc.). In one scenario, prior to beginning to rotate the process fluid rotor 206, an operator may inject liquid into port 277 at a rate sufficient to create a pressure differential across seal 282 suitable to lift the process fluid rotor 206 , which thereby avoids a potential dynamic rotor instability that can accompany the transition from the "inactive" side of thrust bearing 291 (not normally used) to the "active" side (used during normal operations) upon startup. In another scenario, the reverse process can almost be employed. That is, prior to stopping the rotation of the process fluid rotor 206, liquid can be injected into port 277 at a rate sufficient to maintain the elevation thereof. Upon shutdown, the process fluid rotor 206 will continue to be lifted until it has stopped rotating, at which point liquid injection through port 277 can be stopped to allow the process fluid rotor 206 to arrive smoothly. , no rotation, on inactive surfaces of thrust bearing 291. This will reduce potential damage and therefore promote longer bearing life. In another scenario, any tendency to drive the process fluid rotor 206 to the manifold 271 ("reverse thrust") will encounter "damped resistance" due to the fact that the fluid typically needs to bypass the seal 282 (which happens only slowly ) in order for the process fluid rotor 206 to move axially. Similar resistance will be encountered if the process fluid rotor 206 is motivated to rise quickly from its full-down position, however, the fluid needs to pass seal 282 to enter manifold 271 in this case. The above "damped axial translation" attribute will protect thrust bearing 291 and thus provide long life for submerged fluid system 200. In another scenario, in case the process gas permeates the collector fluid and the inlet 250 (which dictates the nominal pressure of the manifold) is subsequently subjected to a sudden pressure drop, the seal 282 will only gradually equalize the manifold pressure to the pressure of the lower inlet 250 and thereby prevent a sudden expansion of the collector gas which may otherwise evacuate from the collector. This is a scenario for which designing the 282 seal to "reduce its clearance relative to the 275 impeller sleeve when subjected to differential pressure transients" (described above) may be applicable. As noted earlier, holding liquid in manifold 271 will facilitate the operability of bearings 264b, 291. In any scenario that potentially subjects the rotating process fluid rotor 206 to "reverse thrust," the higher pressure than is present at the time at the inlet 250 (and therefore manifold 271) can be applied to manifold port 277 to resist such "reverse thrust" and thereby protect, for example, the idle side elements of thrust bearing 291. A substantial sensor array and system The associated quick-acting control devices, possibly including algorithms, actuated valves, and a high-pressure fluid source, can be used to effect the "process fluid rotor active shaft impulse management" functionality described herein. It should be understood that similar ability to apply pressure to the top of the process fluid rotor 206 (for example, by means of supplemental 308 fluid conduit and 321 gas conduit discussed later in this disclosure) can be developed to provide "management active impulse" for fluid end 204.
[055] Significant heat will be generated in the manifold 271 caused by fluid shear and other phenomena associated with the 206 rotating process fluid rotor and the 294 fixed thrust collar. The bearing is achieved by circulating the fluid through a heat exchanger 301 positioned in the water around the fluid end 204. The careful positioning of flow paths in and around the bearings 264b, 291 and to the inlet and outlet ports (302 and 300, respectively) of heat exchanger 301, combined with naturally occurring convection currents aided, for example, by volute and/or flow-directing (e.g. circumferential to axial) geometry in the lower cavity of the collector 285, will create a "pumping effect" for collector 271. Such a pumping effect can be improved by adding features, eg "scallops", "propellers" ", "fans", etc., outside rotating elements including elements including process fluid rotor 206 (e.g., at locations 279, 281; lastly on the end face and/or possibly on an extension of the process fluid rotor 206) and/or thrust collar 294 (eg at location 283). Alternatively or in addition, an impeller or similar device may be attached to the lower end of the process fluid rotor 206.
[056] It is unlikely that process fluid-born solids of significant size or volume will make their way to the manifold 271 of the fluid system 200. As noted earlier, the manifold 271 is normally pressure balanced relative to inlet 250 via the balance circuit conduit 276, so normally there is no fluid flow between manifold 271 and areas containing process end process fluid 204. Additionally, seal 282 allows only small volume, low rate fluid transfer throughout. the same (even during high differential pressure transients). Additionally, a circinal path with multiple intercalated axial and radial surfaces exists between the bottom of the balancing device rotor retainer 298 and the top of the collector top plate 280, so solids need to intermittently move upward against gravity and inward against centrifugal force before they can approach the top of seal 282. Independently, two or more ports 277 may be provided to circulate liquid through manifold 271 and/or heat exchanger 301 to effectively discharge the same. , at least one port for supplying fluid and one for evacuating fluid (for example, to any conduit or vessel located upstream of inlet 250 or downstream of outlet 272). Ports 277 can be provided to intersect with the lower cavity of manifold 285 (as shown in Figure 2C), which represents a larger diameter and lowest point on manifold 271 and also an area where solids are likely to collect. Alternative locations for ports 277 may also be provided and may provide additional benefits that include an ability to deliver high rate flow of liquids directly to heat exchanger 301 to discharge solids and/or gas (if any of the latter are trapped in the same). Note that the 301 heat exchanger can take many forms in addition to that shown in Figure 2C, including some optimized for solids removal and/or gas removal.
[057] Figure 3 illustrates an exemplary subsea fluid system 300 that can be packaged within the fluid system 100 of Figure 1 for the purpose of extracting discrete service fluid streams from a multiphase process stream to meet elemental needs within subsea fluid system 300 (also 200) . Subsea fluid system 300 contains an integrated electrical machine 301, fluid end 302, and magnetic coupling 303 as previously described for subsea fluid system 200 of Figures 2A to C. It also contains upstream and downstream processing packages 304 and 305, respectively. The upstream processing package 304 includes a buffer tank 306, a liquid reservoir 307, a supplemental fluid conduit 308, and a selection of flow control devices and interconnected piping, various elements of which will be described later in this disclosure. The downstream processing package 305 contains a liquid extraction unit 339 and a flow regulation device (known as a throttling or process control valve) 309. An optional downstream service conduit 336 that includes an isolation valve 337 can be provided to connect the liquid extraction unit 339, for example, to the gas conduit 330 (for reasons explained below).
[058] Multiphase fluid enters subsea fluid system 300 at inlet 310 for transport through inlet tube 311 to buffer tank 306. Crude hydrocarbon production fluids delivered to subsea fluid system 300 from wells, directly or by means of, for example, distribution manifolds, it can at various times include as much as 100% gas or 100% liquid, as well as all fractional combinations of gas and liquid (commonly with some volume of solids in addition). The transition between multiphase gas-dominated and liquid-dominated currents may occur frequently (eg timeframe of seconds or less) or rarely and such transitions may be gradual or abrupt. Abrupt changes from very high Gas Volume Fraction (GVF) currents to very low GVF currents, and vice versa (typically termed "aggregative fluidization"), can be harmful to the submerged fluid system 300 for reasons known to those skilled in the art. technique of fluid reinforcement devices and associated tube systems. Buffer tank 306 can even accommodate rapidly changing fluid conditions at inlet 319 and reduces the abruptness of such fluid condition changes at its main outlet 320 and in so doing acts as a moderator of detrimental effects on the downstream fluid system 300 Buffer tank 306 means a "fat spot" in inlet tube 311 that allows fluid to reside in it long enough for gravity to drive heavier currents/elements (liquid/solids) to the bottom of the tank while simultaneously forcing the lifting the gas to the top of the tank. A perforated vertical tube 312 or similar device controls the rate at which the separate streams/elements are gathered before leaving the tank at the main outlet 320. Notably, when a high GVF multiphase flow stream enters the buffer tank 306 the gas volume in the tank can increase in relation to the volume of liquid/solids already in the tank and similarly when a low GVF current enters the tank the opposite can occur. Meanwhile, the GVF of the fluid leaving the tank will typically be different from that entering due to the fact that the GVF of the output current is automatically (and gradually) adjusted according to the volume of gas and liquid/solids allowed to enter the perforated standpipe 312. The level of gas/liquid interface in buffer tank 306 dictates the flow area (number of holes) accessible for each stream.
[059] In certain embodiments of the subsea fluid system 300, separate gas 313 and separate liquid 314 can be withdrawn from the buffer tank 306 through a gas tap 315 and a liquid tap 316, respectively. It is beneficial that no solids enter conduits downstream of gas tap 315 and liquid tap 316. Solids in the fluid stream entering buffer tank 306 will typically be ported through with the liquid phase(s) Therefore, while some scenarios may be envisioned for which solids may enter gas tap 315 (typically accompanied by liquids) or formed into gas conduit 321, subsea fluid system 300 is operated to minimize the chance that these scenarios will occur . The large size of the liquid cock 316 relative to the small size of and the flow rate in conduits downstream thereof allows a substantially quiescent environment to be established within the liquid cock 316 which allows solids to settle in it. The steep angle of the liquid cock 316 suggested in Figure 3 promotes gravity-driven return of settled solids to the main chamber of the buffer tank 306, from which they can subsequently exit through the main outlet 320. The baffle(s) 317 and/or similar device(s) and/or features may be added to the 316 liquid tap to improve the solids separation effect and/or otherwise inhibit the transfer of solids to areas downstream of the liquid tap 316.
[060] Downstream of liquid tap 316 is a normally open valve 318 through which ideally only liquid will pass to enter liquid reservoir 307. Level monitor 327 provides sensory feedback necessary for an associated control system to command valve 318 to close if the liquid level of buffer tank 306 approaches the level of liquid tap 316 and threatens to allow an unacceptable volume of gas to enter liquid reservoir 307 by that route. The liquid reservoir 307 and the conduit including the valve 318 can be oriented vertically and can be fixed to the liquid tap 316 such that solids possibly remaining in the fluid delivered to those spaces can settle and fall into the liquid tap 316 (and subsequently , buffer tank 306) so as not to be carried downstream from liquid reservoir 307. The fluid in liquid reservoir 307 will typically be quite immobile and under certain circumstances will reside in it for several minutes before the liquid phase gives way to downstream, substantially free of solids and free gas.
[061] There are two other flow paths into/out of liquid reservoir 307, specifically gas line link 322 with isolation valve 323 normally open and liquid line link 324 with isolation valve 325 normally open. It is beneficial that only gas flows through gas conduit link 322 and only liquid flows through gas conduit link 324. Level monitor 329 provides sensory feedback necessary for an associated control system to command valve 325 to close if the liquid level of the liquid reservoir 307 approaches the level of the gas conduit link 324 and threatens to allow free gas to enter the same. The main scenario to which valve 323 can be closed is related to the discharge of solids from the liquid reservoir 307, which is described elsewhere in this disclosure.
[062] The liquid level of the liquid reservoir 307 can be forced higher in an absolute direction than in the buffer tank 306 by manipulating isolation valves 323, 325 and the gas flow control device (known as a pressure valve throttling or process control) 326. Maintenance of the liquid reservoir 307 substantially full of liquid is necessary for optimal performance. The use of choke 326 to reduce pressure in gas conduit 321 relative to pressure in buffer tank 306 (thus also liquid tap 316 and liquid reservoir 307) will cause the fluid in liquid reservoir 307 to flow in the direction (to ) of the gas conduit 321. The gas in the liquid reservoir 307, either introduced through the liquid tap 316 (as free gas or gas in solution) or the gas conduit link 322, will naturally collect near the top of the reservoir. liquid 307 and therefore be exhausted into the gas conduit 321 before liquids enter from below during the process of "filling the liquid reservoir". The 329 level monitor provides the sensory feedback necessary to effect a level control system for the 307 liquid reservoir.
[063] The liquid reservoir 307 is provided to maintain a volume of liquid sufficient to lubricate the bearing 264a (named in relation to the description in Figure 3, but shown in Figure 2B) for a specific period of time in the event that the liquid is not most available from buffer tank 306 for such period of time. The time period depends on several factors such as liquid reservoir size 307, pressure drop across fluid end inlet homogenizer 249, bearing chamber leakage rate 247, fluid exiting coupling chamber rate 244 through bypass ports 269 and liquid viscosity are some. Knowing the flow behavior and physical properties of the process fluid entering inlet 310 allows the liquid reservoir 307 to be correctly sized. Recognize that it is difficult to predict such attributes for new production fields and predict how such attributes may vary over the many years that most fields are expected to produce, field replacement of liquid reservoir 307, for example, by a larger unit , independent of other elements within submersible fluid system 300, 100 and/or in combination with other elements within submersible fluid system 300, 100 may be permitted. While features that allow for substitution in specific fields for liquid reservoir 307 are not described in detail in this disclosure (Figure 1 shows process connectors 115 that suggest how such capability can also be provided for fluid system 100 containing the liquid reservoir 307), it should be obvious to someone versed in the art of designing replaceable modular submersible systems how such a capability can be realized.
[064] The nozzle 328 is the input to the gas conduit link 324 and can also be used as an output device for a function described later in this disclosure. It can be configured in any number of shapes and/or associated with devices, eg baffles and/or baffles to passively resist the ingress of solids that may remain in liquid entering or stored in liquid reservoir 307. Typically one or more substantially side-facing or downward-facing ports can be used instead of an upwardly angled port or ports to avoid the undesirable tendency of the latter alternatives to collect solids that may settle from fluids from the liquid reservoir 307, then transfer such solids for elements downstream of them. One or more of any number of filtration devices and/or devices and/or may also be provided to resist ingress of solids, regardless of the orientation of the ports observed.
[065] Unless forced to behave otherwise, for example, by a flow restricting device and/or added flow booster, fluid (e.g., liquid) will exit liquid reservoir 307 to flow through the gas conduit 330 to the bearing 264a at a rate dictated by at least the pressure drop across the inlet fluid end homogenizer 249, the leakage rate of the bearing chamber 247, the rate of fluid exiting the coupling chamber 244 through bypass ports 269 and liquid viscosity. Isolation valves 331, 332, 333 associated with supplemental fluid conduit 308 are normally closed and thus do not normally affect the flow rate through gas conduit 330 (or gas conduit 321). Isolation valve 334 normally open, when closed or substantially closed, allows fluid supplied from a source capable of delivering fluid at a pressure greater than in buffer tank 306, such as supplemental fluid conduit 308 or supply conduit. downstream service 336 (when accessed by opening a normally closed isolation valve 337), to be directed to the liquid reservoir 307 through the nozzle 328, for example, to fill the liquid reservoir 307 with liquid and/or to discharge solids out of liquid reservoir 307 (in addition to valve 318 to liquid tap 316 and buffer tank 306). If it is desired to increase the pressure in the gas conduit 324 upstream of the closed or substantially closed isolation valve 334, for example, to create or intensify a "blasting action" produced, for example, by the nozzle 328, a pump 335 may be added (typically not required for downstream service conduit 336, however possibly useful for supplemental fluid conduit 308). An alternative to the 334 isolation valve is a throttling or process control valve, which is generally better able to accommodate partial opening and associated potentially large pressure drop without suffering significant wear. Such an alternative throttling or process control valve, when associated with suitable instrumentation, for example, upstream, downstream and/or differential pressure sensors and control algorithms (controller) facilitates increased controllability of the liquid flow provided to the bearing. 264a and therefore the rate of liquid consumption in the liquid reservoir 307.
[066] A sufficiently sophisticated system and control that includes automation algorithms will be able to operate the various valves and especially process throttling/control valves (326 and that which is an alternative to isolation valve 334) to optimize refrigerant flows to the bearing 264a and magnetic coupling 258 and possibly to effect "active impulse management" for the rotor fluid end 206. The controller may be configured to receive gas and liquid pressure information and, for example, component position information, etc., from one or more sensors located at relevant points within the submersible fluid system 200 and further configured to control one or more pressure regulating devices to adjust gas or liquid pressures in the submersible fluid system. In some applications the cost of achieving the flexibility and performance improvement delivered by a throttling valve, instrumented process control or other variable position valve (an option for isolation valve 334) is not justified and a fixed flow restriction (eg, an orifice or venturi) or no flow restriction may be adequate to ensure that an acceptable supply of liquid is delivered to bearing 264a. Independently, at least one open/closed type isolation valve 334 can be used to allow the direction of fluids in the manner and for the same purpose described below for isolation valve 338.
[067] A normally open isolation valve 338 is provided in gas conduit 321 so that it can be closed at selected times, for example, following shutdown of submersible fluid system 200 when the duration of such shutdown is expected to be long enough that the process fluid can undergo property changes that can be detrimental to the subsequent operation of fluid system 300 (and 200). With isolation valve 338 closed, chemicals supplied by supplemental fluid conduit 308 can be selectively directed to alternate locations throughout submersible fluid system 300 to displace potentially unwanted process fluids and/or to otherwise protect against undesirable consequences, eg formation of hydrates, wax, etc. Note that the ability to deliver heat to critical locations within submersible fluid systems described herein may be desirable and can be accomplished using known techniques, eg electrical heat tracking and/or heated fluids circulated through conduits dedicated, etc.
[068] Several functions have already been described for supplemental fluid conduit 308. Another function is to supply liquid to bearing 264a for as long as necessary in case the liquid becomes unavailable on a continuous basis from buffer tank 306 and for a period of time from liquid reservoir 307 (eg limited by its size). Facilities providing the 308 supplemental fluid conduit, eg the top hydraulic power unit (HPU) and electrical power supply, plus a single or multiple umbilical conduit to transport HPU chemicals to approach underwater points of use, are provided for subsea production systems as a matter of course to provide mitigation of potential "flow assurance" issues such as those mentioned throughout this disclosure (eg hydrates, wax, scale, etc.). Submersible fluid systems capable of multiphase process fluid described herein do not require that an additional top-end HPU, electrical power supply, umbilicals and other costly equipment (known as a "barrier fluid system") are provided to cool and lubricate your bearings and other sensitive components.
[069] Fluid systems disclosed in this document are sophisticated devices designed to perform complex and challenging functions reliably for extended periods of time. They contain many active devices including electrical machines, fluid ends, auxiliary pumps, valves and sensing instruments, among others. Condition and Performance Monitoring (CPM) of such devices and subsystems is recommended and requires that equally sophisticated data collection, mitigation, historical, control and potentially automation systems be deployed.
[070] A number of modalities have been described. Nevertheless, it will be understood that several modifications can be made. Accordingly, other embodiments are within the scope of the following claims.

权利要求:
Claims (21)
[0001]
1. Submersible fluid system to operate submerged in a body of water characterized by the fact that it comprises: an electrical machine; a fluid end comprising a fluid end housing having an inlet for a fluid rotor, the fluid rotor coupled to the electrical machine and carried to rotate in the housing by a bearing in the housing; and a fluid separator system that receives a multiphase fluid and distributes flows of a multiphase fluid to the inlet and distributes flows of a liquid flow withdrawn from the multiphase fluid to the bearing through a port separate from the inlet; wherein the fluid separator system comprises a separator tank having a surface and a bottom, the separator tank comprising an inlet for the multiphase fluid; a primary outlet at the bottom of the separator tank and coupled to the fluid end inlet; and an outlet on the surface of the separator tank and coupled to the fluid end housing for supplying gas to a cavity around a driving end of the fluid rotor.
[0002]
2. Submersible fluid system according to claim 1, characterized in that the fluid rotor is carried to rotate in the housing by the said first bearing around an end of the fluid rotor and a second bearing around a second end of the fluid rotor and where the fluid separator system communicates a flow of liquid extracted from the multiphase flow to the first bearing and to the second bearing.
[0003]
3. Submersible fluid system according to claim 1, characterized in that the flow of liquid extracted from the multiphase fluid is at a temperature below the bearing temperature.
[0004]
4. Submersible fluid system according to claim 1, characterized in that the fluid separator system distributes a fluid to a cavity around the fluid rotor near a driving end.
[0005]
5. Submersible fluid system according to claim 4, characterized in that the driving end of the fluid rotor is coupled to an electric machine rotor of the electric machine by a coupling and the fluid separator system additionally distributes the fluid flow into a gap between a portion of the coupling on the fluid rotor and a portion of the coupling on the electric machine rotor.
[0006]
6. Submersible fluid system according to claim 5, characterized in that the coupling comprises a magnetic coupling.
[0007]
7. Submersible fluid system according to claim 4, characterized in that the fluid separator system additionally distributes a gaseous flow extracted from the multiphase fluid to a gap between a coupling portion in the fluid rotor and a coupling portion on electric machine rotor.
[0008]
8. Submersible fluid system according to claim 1, characterized in that the fluid separator system comprises: an additional inlet at the bottom of the separator tank and coupled to the fluid end housing to supply fluid, mainly liquid, to the bearing.
[0009]
9. Submersible fluid system according to claim 8, characterized in that the additional outlet comprises an upwardly extending tube configured to release sand from a stream of liquid flowing through the additional outlet.
[0010]
10. Submersible fluid system according to claim 8, characterized in that it further comprises a reservoir tank, the reservoir tank being between the additional outlet and the fluid end housing for receiving and storing liquid from the additional outlet to supply the fluid end when no liquid is produced from the additional outlet.
[0011]
11. Submersible fluid system according to claim 1, characterized in that it additionally comprises a source of auxiliary liquid in fluid communication with the bearing.
[0012]
12. Submersible fluid system according to claim 11, characterized in that the auxiliary liquid source comprises at least one of a treatment liquid that is also added to the multiphase fluid in addition to the submersible fluid system or liquid of a outlet downstream of the fluid end.
[0013]
13. Submersible fluid system according to claim 1, characterized in that the fluid separator system Ml receives multiphase fluid upstream of the fluid end.
[0014]
14. Submersible fluid system for operating submerged in a body of water characterized by the fact that the system comprises: an electrical machine; a fluid end comprising a fluid end housing having an inlet for a fluid rotor, the fluid rotor being coupled to the electrical machine and driven to rotate in the housing through a bearing in the housing; and a fluid separator system that receives a multiphase fluid and distributes multiphase fluid flows to the inlet and distributes flows of an extracted liquid flow from the multiphase fluid to the bearing; wherein the separator system comprises a separator tank having a surface and a bottom; the separator tank comprising an inlet for the multiphase fluid; a primary outlet at the bottom of the separator tank and coupled to the fluid end inlet; and an additional outlet at the bottom of the separator tank and coupled to the fluid end housing for supplying fluid, primarily liquid, to the bearing; wherein the submersible fluid system further comprises a reservoir tank, the reservoir tank being between the additional outlet and the fluid end housing for receiving and storing liquid from the additional outlet to supply the fluid end when no liquid is being produced from it. the additional output; wherein the separator tank further comprises an outlet on the surface of the separator tank and coupled to the fluid end housing for supplying gas to a cavity around a driving end of the fluid rotor; and wherein the reservoir tank is between the outlet on the surface of the separator tank and the fluid end for receiving fluid from the separator tank to drive liquid from the reservoir in the event that no liquid is being produced from the additional outlet and the additional output is closed.
[0015]
15. Submersible fluid system according to claim 14, characterized in that the bearing is configured to cause gas to exit the bearing, preferably as a liquid, whenever gas is present inside the bearing.
[0016]
16. Method, characterized in that it comprises: operating, at an underwater depth, an electrical machine and a fluid end, the fluid end comprising a fluid end housing having an inlet for a fluid rotor, the rotor of fluid coupled to the electrical machine and carried to rotate in the housing by a bearing in the housing; operating a fluid separator system that receives a multiphase fluid comprising raw hydrocarbon processed fluid and communicates a flow of the multiphase fluid to the inlet and an extracted liquid flow of the multiphase fluid to the bearing through a port separate from the inlet; wherein multiphase fluid is dispensed from the fluid end away from the fluid end and fluid separator system; wherein the fluid separator system comprises a separator tank having a surface and a bottom, the separator tank comprising: an inlet for the multiphase fluid; a primary outlet at the bottom of the separator tank and coupled to the fluid end inlet; and an outlet on the surface of the separator tank and coupled to the fluid end housing for supplying gas to a cavity around a driving end of the fluid rotor.
[0017]
17. The method of claim 16, characterized in that the fluid end operation includes rotating the fluid rotor while being carried by said first bearing around one end of the fluid rotor and a second bearing around from a second end of the fluid rotor.
[0018]
18. Method according to claim 17, characterized in that the fluid separator system communicates a mainly liquid flow extracted from the multiphase flow to the first bearing and to the second bearing.
[0019]
19. Method according to claim 16, characterized in that the driving end of the fluid rotor is coupled to an electric machine rotor of the electric machine by a coupling and the fluid separator system additionally distributes a fluid flow to a gap between a portion of the coupling on the fluid rotor and a portion of the coupling on the electric machine rotor.
[0020]
20. Method according to claim 19, characterized in that the coupling comprises a magnetic coupling.
[0021]
21. Method according to claim 16, characterized in that the multiphase comprises: an additional outlet at the bottom of the tank separator and coupled to the fluid end housing.

类似技术:

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公开号 | 公开日 | 专利标题

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BR112015005589B1|2021-04-20|system and method of submersible fluid to operate submerged in a body of water

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US9954414B2|2018-04-24|Subsea compressor or pump with hermetically sealed electric motor and with magnetic coupling

---

US10161418B2|2018-12-25|Coupling an electric machine and fluid-end

---

US20190195057A1|2019-06-27|Submersible well fluid system

---

US10801309B2|2020-10-13|Up-thrusting fluid system

---

US20110058966A1|2011-03-10|Flushing system

---

AU2009244519A1|2009-11-12|Flushing system

同族专利:

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公开号 | 公开日

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US20150322756A1|2015-11-12|

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WO2014042626A1|2014-03-20|

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CA2894739A1|2014-03-20|

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AU2012389801A1|2015-04-09|

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EP2901018B1|2021-04-21|

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SG11201501906UA|2015-05-28|

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US10393115B2|2019-08-27|

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RU2015113439A|2016-11-10|

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CN105074223A|2015-11-18|

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EP2901018A1|2015-08-05|

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AU2012389801B2|2017-12-14|

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BR112015005589A2|2018-05-22|

引用文献:

---

公开号 | 申请日 | 公开日 | 申请人 | 专利标题

---

---

US2356482A|1940-09-27|1944-08-22|Thrush Company|Water circulator|

---

US2577559A|1948-07-01|1951-12-04|Jacuzzi Bros Inc|Submersible pump assembly|

---

DE858196C|1950-09-16|1952-12-04|Ritz & Schweizer Geb|Submersible motor pump with vertical axis of rotation|

---

US2996994A|1955-06-09|1961-08-22|Tokheim Corp|Motor-pump apparatus|

---

US2947259A|1957-12-06|1960-08-02|Tokheim Corp|Motor-pump unit for automotive fuel|

---

US2968248A|1957-12-16|1961-01-17|Gen Motors Corp|Magnetic drive impeller pump|

---

US2970548A|1958-06-23|1961-02-07|Pumpindustri Ab|Magnetically driven pump|

---

US3074347A|1958-11-21|1963-01-22|Tokheim Corp|Electric drive unit and mounting|

---

US3186513A|1962-11-09|1965-06-01|James T E Dunn|Method and mechanism for lubricating the bearings of a pump rotor and motor combination for pumping an abradant-containing liquid|

---

US3213736A|1963-10-16|1965-10-26|William B Keeton|Cutter for picture frame mats|

---

US3411450A|1967-03-07|1968-11-19|Little Giant Corp|Pump|

---

US3802804A|1967-07-21|1974-04-09|March Mfg Co|Magnetically coupled pump structure|

---

US3520642A|1968-10-29|1970-07-14|Process Ind Inc|Motor driven pump|

---

US4080112A|1976-02-03|1978-03-21|March Manufacturing Company|Magnetically-coupled pump|

---

US4235569A|1977-03-31|1980-11-25|Alois Schillinger|Submersible pump for radioactive liquids|

---

SU787583A1|1977-10-17|1980-12-15|За витель А. В. Кеменов|Pumping station|

---

US4276002A|1979-03-09|1981-06-30|Anderson James H|Turbopump unit for deep wells and system|

---

US4266914A|1979-03-12|1981-05-12|Dickinson David G|Magnetic drive laboratory pump|

---

JPS6329117B2|1979-07-10|1988-06-10|Tokico Ltd|

---

FR2480360A1|1980-04-14|1981-10-16|Guinard Pompes|Sealed electric motor for use in wet conditions - has shaft connected to magnet inside sealed casing with driven magnet mounted on output shaft outside casing|

---

DE3037217C2|1980-10-02|1985-06-20|Bernhard 8071 Lenting Kessel|Waste water tank|

---

US4526518A|1981-07-23|1985-07-02|Facet Enterprises, Inc.|Fuel pump with magnetic drive|

---

US4478054A|1983-07-12|1984-10-23|Dunham-Bush, Inc.|Helical screw rotary compressor for air conditioning system having improved oil management|

---

JPS6291692A|1985-10-16|1987-04-27|Ngk Insulators Ltd|Magnet driving device for rotating apparatus|

---

DE3636404C2|1986-10-25|1990-09-27|Richter Chemie-Technik Gmbh, 4152 Kempen, De|

---

DE3642729C3|1986-12-13|1997-05-07|Grundfos Int|Pump unit for conveying liquids or gases|

---

FR2609118A1|1986-12-29|1988-07-01|Brahic Claude|Submerged vertical centrifugal pump with magnetic drive without a shaft and fluid-cooled|

---

DE3712459C2|1987-04-11|1991-01-24|Franz Klaus Union Armaturen, Pumpen Gmbh & Co, 4630 Bochum, De|

---

DE3729486C1|1987-09-03|1988-12-15|Gutehoffnungshuette Man|Compressor unit|

---

FR2646882B1|1989-05-12|1994-05-20|Brahic Claude|WATERPROOF VERTICAL PUMP WITHOUT SHAFT|

---

NO172076C|1991-02-08|1993-06-02|Kvaerner Rosenberg As Kvaerner|COMPRESSOR SYSTEM IN AN UNDERWATER STATION FOR TRANSPORTING A BROWN STREAM|

---

FR2672636B1|1991-02-12|1995-01-13|Bertin & Cie|ROTATING MACHINE OF THE COMPRESSOR OR TURBINE TYPE FOR COMPRESSION OR EXPANSION OF A DANGEROUS GAS.|

---

JP2580275Y2|1992-03-24|1998-09-03|三和ハイドロテック株式会社|Magnet pump|

---

US5248245A|1992-11-02|1993-09-28|Ingersoll-Dresser Pump Company|Magnetically coupled centrifugal pump with improved casting and lubrication|

---

US5297940A|1992-12-28|1994-03-29|Ingersoll-Dresser Pump Company|Sealless pump corrosion detector|

---

US5301091A|1993-04-14|1994-04-05|Chen We C|Motor vehicle neon lamp device|

---

US5310265A|1993-06-15|1994-05-10|Rockwell International Corporation|Axially fed hydrostatic bearing/seal|

---

US5485905A|1994-04-01|1996-01-23|Rader, Iii; H. John|Lightweight overrunning clutch assembly|

---

US7836950B2|1994-10-14|2010-11-23|Weatherford/Lamb, Inc.|Methods and apparatus to convey electrical pumping systems into wellbores to complete oil and gas wells|

---

US7325606B1|1994-10-14|2008-02-05|Weatherford/Lamb, Inc.|Methods and apparatus to convey electrical pumping systems into wellbores to complete oil and gas wells|

---

US5642989A|1995-10-13|1997-07-01|National Compressed Air Canada Limited|Booster compressor system|

---

US6059539A|1995-12-05|2000-05-09|Westinghouse Government Services Company Llc|Sub-sea pumping system and associated method including pressure compensating arrangement for cooling and lubricating|

---

US5660520A|1996-01-25|1997-08-26|Camco International Inc.|Downhole centrifugal pump|

---

US5779456A|1996-10-28|1998-07-14|Finish Thompson Inc.|Magnetic drive|

---

US5779434A|1997-02-06|1998-07-14|Baker Hughes Incorporated|Pump mounted thrust bearing|

---

KR20010041509A|1998-03-04|2001-05-25|마에다 시게루|Performance regulating device for fluid machinery|

---

US6293772B1|1998-10-29|2001-09-25|Innovative Mag-Drive, Llc|Containment member for a magnetic-drive centrifugal pump|

---

US6213736B1|1998-11-28|2001-04-10|G Louis Weisser|Electric motor pump with magnetic coupling and thrust balancing means|

---

WO2001033083A1|1998-12-04|2001-05-10|SØRENSEN, Emil, Aarestrup|A tank and a centrifugal pump for emptying the tank|

---

US6443710B1|1999-08-10|2002-09-03|Iwaki Co., Ltd.|Magnetic pump|

---

US6322335B1|2000-07-24|2001-11-27|Chi Wei Shi|Pump structure|

---

JP3930243B2|2000-11-06|2007-06-13|本田技研工業株式会社|Magnet pump|

---

JP2002250294A|2001-02-21|2002-09-06|Nikkiso Co Ltd|Centrifugal pump|

---

JP4033648B2|2001-03-26|2008-01-16|株式会社神戸製鋼所|Liquid volume calculation device|

---

US6863124B2|2001-12-21|2005-03-08|Schlumberger Technology Corporation|Sealed ESP motor system|

---

GB2385076B|2002-02-11|2006-03-15|Abb Offshore Systems As|Integrated subsea power pack for drilling and production|

---

JP4411201B2|2002-05-07|2010-02-10|エーエムウーウンターヴァッサープムペンゲゼルシャフトミットベシュレンクテルハフツング|Drive motor, especially drive motor for pump|

---

US7178592B2|2002-07-10|2007-02-20|Weatherford/Lamb, Inc.|Closed loop multiphase underbalanced drilling process|

---

US7572115B2|2002-07-19|2009-08-11|Innovative Mag-Drive, Llc|Corrosion-resistant rotor for a magnetic-drive centrifugal pump|

---

US20040144534A1|2003-01-28|2004-07-29|Lee Woon Y|Self lubricating submersible pumping system|

---

GB2399864A|2003-03-22|2004-09-29|Ellastar Ltd|A system and process for pumping multiphase fluids|

---

KR100536062B1|2003-05-07|2005-12-12|한국기계연구원|Process for Manufacturing Nano TaC- Transition Metal Based Composite Powder|

---

US7029246B2|2003-05-07|2006-04-18|Viking Pump, Inc.|Rotor shaft bearing design and coupling mechanism|

---

GB0314550D0|2003-06-21|2003-07-30|Weatherford Lamb|Electric submersible pumps|

---

NO323324B1|2003-07-02|2007-03-19|Kvaerner Oilfield Prod As|Procedure for regulating that pressure in an underwater compressor module|

---

US6933638B2|2003-10-30|2005-08-23|A. O. Smith Corporation|Electric motor having a reverse air flow cooling system|

---

US7370697B1|2003-12-29|2008-05-13|Wood Group Esp, Inc.|Thrust section wear preventor|

---

US7101158B2|2003-12-30|2006-09-05|Wanner Engineering, Inc.|Hydraulic balancing magnetically driven centrifugal pump|

---

US7137793B2|2004-04-05|2006-11-21|Peopleflo Manufacturing, Inc.|Magnetically driven gear pump|

---

US7001063B1|2005-02-18|2006-02-21|Spx Corporation|Cleanable mixer driver apparatus and method|

---

US7393188B2|2005-03-16|2008-07-01|Ecotech, Inc.|Bracketless magnetic pump|

---

CN100479297C|2005-05-20|2009-04-15|合肥三益江海泵业有限公司|Large submersible electric pump|

---

US7549205B2|2005-06-24|2009-06-23|Peopleflo Manufacturing Inc.|Assembly and method for pre-stressing a magnetic coupling canister|

---

US7625187B2|2005-08-24|2009-12-01|Johnson Pumps Of America Inc.|Submersible pump with integrated liquid level sensing and control system|

---

US7604049B2|2005-12-16|2009-10-20|Schlumberger Technology Corporation|Polymeric composites, oilfield elements comprising same, and methods of using same in oilfield applications|

---

RU2303161C1|2006-02-14|2007-07-20|Государственное образовательное учреждение высшего профессионального образования "Воронежский государственный технический университет"|Underwater pumping station for transfer of multicomponent gas-containing mixture|

---

EP1999374A1|2006-03-24|2008-12-10|Siemens Aktiengesellschaft|Compressor unit|

---

AT507396T|2006-03-24|2011-05-15|Siemens Ag|COMPRESSOR UNIT AND ASSEMBLY PROCEDURE|

---

US7741744B2|2006-03-27|2010-06-22|Schlumberger Technology Corporation|System and method for protecting a submersible motor|

---

US7530391B2|2006-05-31|2009-05-12|Baker Hughes Incorporated|Seal section for electrical submersible pump|

---

WO2008119404A1|2007-03-31|2008-10-09|Ebm-Papst St. Georgen Gmbh & Co. Kg|Arrangement for delivering fluids|

---

DE102007016380A1|2007-04-03|2008-10-09|Voith Patent Gmbh|Diving power plant|

---

DE102007021720B4|2007-05-09|2014-01-23|Siemens Aktiengesellschaft|Compressor system for underwater use in the offshore sector|

---

JP4909185B2|2007-06-11|2012-04-04|アスモ株式会社|Pump device, assembling method of pump device, vehicle washer device|

---

US7718899B2|2007-06-25|2010-05-18|Harald Benestad|High pressure, high voltage penetrator assembly for subsea use|

---

US7950906B2|2007-08-14|2011-05-31|Baker Hughes Incorporated|Insulated bearings for downhole motors|

---

US20090098003A1|2007-10-11|2009-04-16|General Electric Company|Multiphase screw pump|

---

US7828066B2|2007-11-29|2010-11-09|Baker Hughes Incorporated|Magnetic motor shaft couplings for wellbore applications|

---

US9601964B2|2008-05-06|2017-03-21|Fmc Technologies, Inc.|In-line flow mixer|

---

US8696331B2|2008-05-06|2014-04-15|Fmc Technologies, Inc.|Pump with magnetic bearings|

---

EP2149673A1|2008-07-31|2010-02-03|Shell Internationale Researchmaatschappij B.V.|Method and system for subsea processing of multiphase well effluents|

---

CA2678560A1|2008-09-12|2010-03-12|Artificial Lift Company Limited|Downhole pumping system|

---

RU2522695C2|2009-01-08|2014-07-20|Акер Сабси АС|Device for spraying with liquid at well inflow compression|

---

DE102009000160B4|2009-01-13|2019-06-13|Robert Bosch Gmbh|Method and control device for controlling personal protective equipment for a vehicle|

---

EP2233745A1|2009-03-10|2010-09-29|Siemens Aktiengesellschaft|Drain liquid relief system for a subsea compressor and a method for draining the subsea compressor|

---

US20100278672A1|2009-04-30|2010-11-04|General Electric Company|Method and apparatus for lubricating a screw pump system|

---

US8393876B2|2009-05-06|2013-03-12|Curtiss-Wright Electro-Mechanical Corp.|Gas tolerant subsea pump|

---

EP2263767A1|2009-06-17|2010-12-22|M-I Epcon As|A separator tank for separating oil and gas from water|

---

US8347983B2|2009-07-31|2013-01-08|Weatherford/Lamb, Inc.|Drilling with a high pressure rotating control device|

---

CN201650775U|2010-03-02|2010-11-24|淄博市博山光明实业公司|Axial electromagnetic force anti-thrust energy saving submersible electric pump|

---

US20130136634A1|2010-06-22|2013-05-30|Vetco Gray Scandinavia As|Motor and pump barrier fluids pressure regulation system in a subsea motor and pump module|

---

US8425667B2|2010-08-31|2013-04-23|General Electric Company|System and method for multiphase pump lubrication|

---

CN103261571B|2010-09-13|2016-08-31|阿克海底公司|The system and method stablizing subsea power conveying is provided to seabed high-speed electric expreess locomotive|

---

US8727737B2|2010-10-22|2014-05-20|Grundfos Pumps Corporation|Submersible pump system|

---

NO333684B1|2011-03-07|2013-08-12|Aker Subsea As|UNDERWATER PRESSURE COOKING MACHINE|

---

NO334268B1|2011-04-15|2014-01-27|Apply Nemo As|An underwater cooling device|

---

NO334554B1|2011-06-01|2014-04-07|Vetco Gray Scandinavia As|Submarine compression system for pressure increase of well flow|

---

US9151131B2|2011-08-16|2015-10-06|Zeitecs B.V.|Power and control pod for a subsea artificial lift system|

---

WO2013028594A2|2011-08-24|2013-02-28|Dresser-Rand Company|Efficient and reliable subsea compression system|

---

JP4969695B1|2011-09-15|2012-07-04|三菱重工業株式会社|Drive device for magnetic coupling pump and magnetic coupling pump unit|

---

EP2626563B1|2012-02-10|2020-06-03|Sulzer Management AG|Pump, recirculating device for a pump and rotor shaft for a pump|

---

US10161418B2|2012-09-12|2018-12-25|Fmc Technologies, Inc.|Coupling an electric machine and fluid-end|

---

EP2901018B1|2012-09-12|2021-04-21|FMC Technologies, Inc.|Subsea multiphase pump or compressor with magnetic coupling and cooling or lubrication by liquid or gas extracted from process fluid|

---

WO2014042630A1|2012-09-12|2014-03-20|Cunningham Christopher E|Subsea compressor or pump with hermetically sealed electric motor and with magnetic coupling|

---

SG11201501905TA|2012-09-12|2015-05-28|Fmc Technologies|Up-thrusting fluid system|US10880340B2|2008-11-26|2020-12-29|Free Stream Media Corp.|Relevancy improvement through targeting of information based on data gathered from a networked device associated with a security sandbox of a client device|

---

WO2014042630A1|2012-09-12|2014-03-20|Cunningham Christopher E|Subsea compressor or pump with hermetically sealed electric motor and with magnetic coupling|

---

EP2901018B1|2012-09-12|2021-04-21|FMC Technologies, Inc.|Subsea multiphase pump or compressor with magnetic coupling and cooling or lubrication by liquid or gas extracted from process fluid|

---

US10161418B2|2012-09-12|2018-12-25|Fmc Technologies, Inc.|Coupling an electric machine and fluid-end|

---

SG11201501905TA|2012-09-12|2015-05-28|Fmc Technologies|Up-thrusting fluid system|

---

US10221662B2|2013-03-15|2019-03-05|Fmc Technologies, Inc.|Submersible well fluid system|

---

RU2578738C1|2014-10-15|2016-03-27|Цзянсуская корпорация по ядерной энергетике|Hydraulic lock device for protection against ingress of nitrogen in radial-axial bearing of main circulation pump|

---

RU2578767C1|2014-10-15|2016-03-27|Цзянсуская корпорация по ядерной энергетике|Pressure stabilization system of channel for cooling and lubricating radial-axial bearing of main circulation pump|

---

EP3286436B1|2015-04-21|2020-04-08|Nuovo Pignone Tecnologie - S.r.l.|Integrated turbomachine with an axial locking device|

---

NO341049B1|2015-12-20|2017-08-14|Vetco Gray Scandinavia As|A cooling- and barrier fluid system and method for a subsea motor and drive|

---

US10859084B2|2016-04-26|2020-12-08|Onesubsea Ip Uk Limited|Subsea process lubricated water injection pump|

---

US10781668B2|2016-12-28|2020-09-22|Upwing Energy, LLC|Downhole power generation|

---

US10697276B2|2016-12-28|2020-06-30|Upwing Energy, LLC|Downhole power generation|

---

US10584533B2|2016-12-28|2020-03-10|Upwing Energy, LLC|Downhole blower system with pin bearing|

---

US10612351B2|2016-12-28|2020-04-07|Upwing Energy, LLC|Isolating a downhole-type electric machine|

---

NO344365B1|2017-12-21|2019-11-18|Fsubsea As|Magnetic coupling assembly|

---

NO346033B1|2018-12-20|2022-01-10|Fsubsea As|Subsea pump system with process lubricated bearings, related method and use|

---

US10731557B1|2019-04-19|2020-08-04|Hamilton Sundstrand Corporation|Cyclonic dirt separator for high efficiency brayton cycle based micro turbo alternator|

---

EP3883355A1|2020-03-16|2021-09-22|ABB Schweiz AG|A subsea installation|

法律状态:
2018-12-11| B06F| Objections, documents and/or translations needed after an examination request according [chapter 6.6 patent gazette]|

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2020-02-04| B06U| Preliminary requirement: requests with searches performed by other patent offices: procedure suspended [chapter 6.21 patent gazette]|

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2021-02-02| B09A| Decision: intention to grant [chapter 9.1 patent gazette]|

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2021-04-20| B16A| Patent or certificate of addition of invention granted|Free format text: PRAZO DE VALIDADE: 20 (VINTE) ANOS CONTADOS A PARTIR DE 12/09/2012, OBSERVADAS AS CONDICOES LEGAIS. |

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申请号 | 申请日 | 专利标题

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PCT/US2012/054832|WO2014042626A1|2012-09-12|2012-09-12|Subsea multiphase pump or compressor with magnetic coupling and cooling or lubrication by liquid or gas extracted from process fluid|

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