• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    SUBSEA PRESSURE Boost. The invention relates to a subsea turbomachine for increasing the pressure of oil fluid flow from wells or subsea oil production systems, which comprises an electric motor and a compressor or a pump driven by the electric motor, an inlet of fluid and a fluid outlet, characterized in that the turbomachine comprises: a common pressure housing for the electric motor or stator, and a compressor, pump or rotor; a magnetic gear within the common pressure housing for operative connection between the motor or stator and compressor, pump or rotor, and a partition within the common pressure housing, arranged to separate an engine compartment, or stator from a compressor, pump or rotor compartment.
    公开号:BR112013023523B1
    申请号:R112013023523-3
    申请日:2012-03-15
    公开日:2021-05-18
    发明作者:Olav Stinessen Kjell；Eriksen Asbjørn
    申请人:Aker Solutions As；
    IPC主号:
    专利说明:

    field of invention
    [001] The present invention relates to pressure increase. More specifically the invention relates to compressors and pumps, particularly subsea compressors and pumps, including multiphase pumps for increasing the pressure of gas, multiphase or liquid from subsea wells or oil production systems. In the following, a common term will be used: Pressure intensifiers; for turbomachinery such as compressors, multiphase pumps and pumps for liquids. Background of the invention and prior art
    [002] The pressure of an oil reservoir, in particular a gas reservoir, decreases very quickly during production. In order to maintain and prolong the production of subsea reservoirs, often involving long transport through a pipeline of produced fluid, it is necessary to increase the pressure.
    [003] In Figure 1 the process of a subsea compression station is illustrated. The rotating equipment deals with compressors and pumps. Pump rotation speed is typically in the range 3000 to 4000 rpm, while compressors typically operate in the range 5000 to 12000 rpm. Reference is made to Table 1 for the understanding of this figure. To give an idea of the dimensions, the diameter of the separator in Figure 1 can be in the range of 3 m and 10 m in height. Table 1


    [004] The typical energy requirement for the pressure intensifier of such a compressor train is 5 to 15 MW. This, combined with high frequency transmission limits the length of a subsea output electrical cable, established and controlled from the surface (surface or on land) via a surface variable speed drive (VSD). More specifically the Ferranti effect, and possibly other effects as well, limit the subsea length of high-frequency high power electrical output cables to about 40 to 50 km.
    [005] The state of the art of subsea compressors (motor compressors) is indicated in Figure 2, in which the main components are the compressor that is driven by a high-speed electric motor that rotates at a speed that the compressor needs, that is. that is, the engine rotates at a speed typically in the range of 5000 to 12000 rpm. Motor speed is transmitted to the compressor by at least one shaft that connects the motor and the compressor. The frequency of electrical energy to give this speed to the motor and thus the compressor should be in the range of about 80 to 200 Hz, for a two-pole motor. The compressor motor shaft power can typically be in the range of 5 to 15 MW and possibly higher in the future. The stable transmission of electrical energy at high frequencies that the motor needs is feasible if the distance between the power source, usually from land or coast (surface) is limited to the range of 40 to 50 km. If the output distance is greater than this, power transmission through the cable becomes unstable and inoperable. In these cases there will be contradictory requirements between the high frequency that the motor needs to give the proper speed and the low frequency, for example, typically 40 to 70 Hz that is needed to have stable power transmission. This contradiction can be resolved by the low frequency of power transmission and the local increase in frequency by placing a subsea variable speed drive (SVSD) close to the motor.
    [006] The atmosphere of the engine compressor in figure 1 will be the gas, either the gas to be potentiated or an inert gas supplied from a reservoir. The term inert gas in the context of the present patent specification means any gas that is not harmful to the internal materials of the engine as well as to the gearing in cases where such equipment is located in the same compartment as the engine. Typically, the inert gas can be dry nitrogen or dry methane, however, dry nitrogen is preferable and in the context here covers all applicable inert gas types.
    [007] In cases where the pumps have a liquid-filled motor, the motor is filled with an inert liquid, that is, a liquid that is not harmful to the internal materials of the motor and the gear in cases where a gear is located in the same compartment as the bomb.
    [008] It should be mentioned that only the main components necessary to understand the state of the art of subsea motor-compressor included in Figure 2 and in Figures 3 to 6 below. Other vital components necessary for the design of a subsea operable complete compressor or pressure intensifier not included are: gas engine cooling system, high voltage power connectors for power transmission to the engine, low voltage cables for the signal and control of magnetic bearings, balance piston and others.
    [009] However, while subsea processing equipment has gained acceptance over recent years as a realistic option, there is more reluctance against electrical and electronic equipment, ie a perception that this type of equipment will have low reliability and robustness. This is particularly true for static variable speed subsea drives, VSD, for electric motors. [VSD is also called variable frequency drive (VFD) and frequency converters]. Therefore, it is a common view in the professional environment that the risk of loss of production by application of subsea VSDs is considered high and should if possible be avoided.
    [0010] An SVSD (Subsea VSD) will also be large in dimensions and weight and therefore not easy to install and retrieve. The cost will also be high.
    [0011] A subsea VSD located close to the turbomachine will allow the transmission of high power and low frequency electrical energy through the subsea output cable, which allows for a much longer length of output. However, the cost of a viable subsea VSD for a 10 MW engine can be indicatively 100 million Norwegian Kroner, and weight about 100 tons, height about 11 m, and diameter about 3 m. But a more serious issue is the risk of limited reliability of a subsea VSD.
    [0012] Even though the subsea VSD contains superior quality components, each of very high quality and reliability, the high number of components and the complexity of the structure result in total subsea VSD reliability which can be a significant issue.
    [0013] The demand for further improvements still exists, for pressure intensifiers in general and subsea pressure intensifiers in particular, and the aim of the present invention is to meet said demand. Brief description of the invention
    [0014] Demand is satisfied with a subsea turbomachine to increase the pressure of oil fluid flow from wells or subsea oil production systems, comprising an electric motor and a compressor or pump driven by the electric motor, an inlet of fluid and a fluid outlet, characterized by the fact that the turbomachine comprises:
    [0015] a common pressure housing for the electric motor or stator, and a compressor, pump or rotor;
    [0016] a magnetic gear inside the common pressure housing for operative connection between the motor or stator and compressor, pump or rotor, and
    [0017] a partition within the common pressure housing, arranged to separate an engine or stator compartment from a compressor, pump or rotor compartment.
    [0018] The partition preferably comprises magnetic poles or electromagnets, or both, to modulate the magnetic field coupling ratio and the magnetic gear ratio. Gear ratio can be controlled via energizing or de-energizing electromagnets in the partition. In general, the low speed side is the motor or stator side, usually at a speed of up to about 4000 revolutions per minute - rpm, while the high speed side is the compressor side of the pump or rotor, typically at a speed of up to about 12,000 rpm, in an effect up to about 15 MW. However, speeds and effects may at least in the future be varied beyond the limits indicated here.
    [0019] The magnetic gear is preferably a step-up magnetic gear that allows subsea output lengths far in excess of 40 km, as the Ferranti effect can be manipulated. An output magnetic gear is estimated to result in much greater reliability than an SVSD. Indicative costs of such a gear will be in the range of 10 to 15% of that of an SVSD, the diameter in the range of 1.5 m and length of 1.5 m and weight in the range of 5 to 10 tons. Compared with the use of SVSD, it is very favorable to provide a step-up magnetic gear between the motor and the compressor to increase the speed from the low motor speed, necessary for stable electrical transmission, to the speed that is necessary for the compressor. Typically the step-up gear ratio can be in the range of 2 to 3, but the present invention covers all ratios starting from 1, i.e. a 1:1 magnetic coupling, up to what may be needed in a case to another. Compared to prior art solutions, reliability can be 10 times better, each of size, weight and cost can be 1/10. Many embodiments of the pressure intensifier of the invention are non-contact, having magnetic gear and magnetic bearings, providing extremely low loss combined with high reliability, making said embodiments particularly favorable in both subsea and dry locations.
    [0020] The magnetic gear can be of any type, eg parallel, planetary and cycloid. Normally the transmission is a permanent magnet gear, but gears with electromagnets or on the motor side (ie the low speed side) either on the compressor side or on both sides can also be adapted for subsea pressure intensifiers.
    [0021] A favorable design of the magnetic gear is a cycloid permanent magnet gear which operatively links the engine and turbomachinery, most preferably a permanent magnet cycloid inner gear whose inner gear ring is connected to the turbomachinery. This allows for very high torque transfer, because the inner ring permanent magnets are influenced by the outer ring permanent magnets to a greater number of magnets, increasing the magnetic coupling and thus the torque transfer capacity. Another advantage is the compact construction over the conventional sprocket design, as one ring is inside the other, and also the simple design that improves reliability and does not require bearings.
    [0022] The planetary gear will also have these favorable characteristics and more perfect alignment of the motor and compressor shaft. Planetary gear embodiments can be very favorable as torque transfer can be very high due to a large number of pole interactions and stability can be very good due to the symmetrical structure to the motor shafts and arranged coaxially with the turbomachinery. In addition, the planetary gears can be arranged to allow for gear shifting.
    [0023] As mentioned above, the invention should not be limited with regard to the type of magnetic equipment and it can either be a permanent magnet or an electromagnet type. The most appropriate type of gear will be selected according to each case, among other things in the state of the art of the various types.
    [0024] A magnetic gear can be provided as a gearbox in which the step-up ratio can be changed in steps. This can be done by stopping the pressure intensifier by ROV or by an electric motor mounted in the gearbox.
    [0025] The most conventional way to change the step-up ratio is to recover the pressure impression and change the gear to another gear with the new desired step-up ratio. This can be done in connection with the regrouping of the compressor or pump.
    [0026] Magnetic gears with electromagnets on the low-speed side of the engine or on the high-speed side of the turbomachine makes it possible to continuously vary the speed of the turbomachinery by increasing or reducing the speed of rotation of the magnetic field of the electromagnets, when energizing or do not energize the electromagnets.
    [0027] The motor, gear and compressor will be arranged in the common pressure housing, however, one or more partitions with shaft seals are situated between the main components separating the common pressure housing into compartments in which the main components are installed . A favorable design for protecting the motor and gear with its magnetic bearings is to have a partition between a compartment containing motor and gear on one side of at least one shaft seal and the compressor on the other side.
    [0028] The pressure housing can be a single piece, as the number of possible fluid leakage paths is thus minimized. Alternatively, the pressure housing may have flanges between the compartments with the main components, if this is considered favorable to replacing the components at a later stage, for example, in order to increase the compressor speed at the final production end of a reservoir, increasing the gear ratio.
    [0029] The pressure intensifier preferably comprises shafts with magnetic bearings, a shaft for the motor with the low-speed part of the gear and a shaft for the turbomachine with the high-speed part of the magnetic gear. If the cycloid gear is used, an outer ring of the magnetic gear is attached to the engine shaft and an inner ring of the magnetic gear is attached to the turbomachinery shaft. Each shaft is suspended in two radial magnetic bearings, at or near either end, and a magnetic thrust bearing and a 5-axis control system is operatively connected to the bearings of each shaft. Magnetic bearings require a comprehensive control system in order to be operative, requiring a control unit on the seabed, as the shafts are actively controlled by the bearing's electromagnets in order to rotate without physical contact. A 5-axis control system is favorable because it is a proven design and verified to have sufficient reliability for the purpose.
    [0030] Although two radial bearings and one thrust bearing are sufficient for one shaft, the number of bearings should not be a limitation of the invention.
    [0031] Alternative bearings such as mechanical bearings are possible, but this will result in a need for lubricating oil susceptible to contamination by the driven media and requires a rather complicated lubricating oil system.
    [0032] Compared to prior art high-speed subsea pressure intensifiers, which include a subsea VSD, the intensifier type of the invention is estimated to have much greater reliability, presumably on the order of more than a decade. And so are dimensions, weight and cost. There are, therefore, strong cost and technical incentives for invention.
    [0033] By separating the engine and the gear with its bearings from the turbomachine by a partition or a diaphragm with a shaft seal, that is, in such a way that the geared engine and the turbomachine are located in separate compartments, it will be possible to protect the engine and gear from harmful amounts of contaminants from the medium driven by the supply of a small supply of an inert fluid in relation to the engine and gear materials such that this fluid at all times constitutes the main composition of the engine volume -gear, and the contaminants that must enter this volume will be diluted to non-harmful concentrations. The inert fluid supplied will be lost by flowing through the seal.
    [0034] As an example, it can be indicated that the loss of inert liquid for a pump is on the order of 1 liter per day per seal.
    [0035] For a compressor, the atmosphere of the gear and engine compartment, in theory, should be kept protected from contamination by having a flow rate of an inert gas through a seal higher than the rate of diffusion of the contaminants . If the total volume of engine and gear atmosphere included gas cooler and piping is 2 m2, it is assumed that a supply of inert gas, eg dry nitrogen or dry methane, at a rate that results in few changes of volume per year is sufficient to protect the materials from being damaged.
    [0036] If, for example, a 10 m3 pressure vessel or tank is located on or in the compressor and has a starting pressure of 450 bar and the compressor suction pressure is 50 bar, an estimate will result in the 2 m3 engine-gear compartment atmosphere can be changed about 20 times, that is, with one atmosphere change per month, the tank will last well below a year before recharging, which can be done from the ship by ROV when necessary.
    [0037] Another design that completely protects the low speed part of the motor and gear on the motor or stator side from contaminants is to hermetically separate the low and high speed part (compressor or rotor side) by means of a partition or partition wall sometimes called protective cover, similar to what is used for magnetic couplings. In order to maintain the necessary strength and the consequent thickness of the protective cover reasonable, the pressure difference between the compressor and the engine atmosphere must at all times be kept within acceptable limits by some type of pressure balancing device. The partition, skirt or partition wall is for the most part non-magnetic, however it should preferably comprise pole pieces or electromagnets arranged in the partition between the magnets on each side of the partition, in order to modulate the gear coupling and the transmission ratio.
    [0038] A very preferred embodiment of the invention is a distinct turbomachine in that it is a pressure intensifier comprising a stator compartment and a rotor compartment, the rotor compartment comprises a compressor or pump disposed directly on the rotor or coupled to the rotor. The compartments are separated by a diaphragm, divider or protective cover, preferably hermetically separated, and pole pieces or electromagnets are arranged in the divider between the magnets on each side of the divider in order to modulate the gear coupling and gear ratio . Said turbomachine is for subsea and surface use as the solution appears to be completely new. Brief Description of Drawings Figures 1 and 2 illustrate prior art solutions, Figures 3 to 6 illustrate embodiments and features of the present invention, and Figure 7 gives examples of magnetic gears. Figure 8 illustrates a preferred embodiment of the invention, and Figure 9 illustrates in more detail the magnetic gear of a subsea turbomachine of the invention. Detailed description of the invention
    [0039] In the following the invention in various embodiments will be explained and illustrated by the figures. Reference is made to Table 2 for an understanding of Figures 3 to 5. It should be mentioned that only the main components necessary for an understanding of the invention are included in Figures 3 to 6. Table 2


    [0040] Reference is made to Figure 3, which illustrates a pressure intensifier in the form of a compressor with magnetic gear and an electric motor, and where the magnetic gear has a step-up ratio that intensifies the motor shaft speed , which is low enough to be supplied with a low enough frequency to have stable cable transmission, up to the required compressor speed. The motor can, for example, rotate at a speed of 3000 rpm, that is, the electrical power has a frequency of 50 Hz for a two-pole motor, and the transmission can have a step-up ratio of 2.5: 1, which means the compressor has a speed of 7500 rpm. If the power source located on the surface has a VSD, the frequency can be changed, for example, between 33 and 67 Hz. A partition (4') is arranged between the magnetic gear (13) and the pressure housing and inside of the magnetic gear, not shown, between the higher speed and lower speed sides of the gear.
    [0041] Reference is made to Figure 4 which illustrates that there is a partition (4') with a shaft seal between the compressor (2) in the engine compartment (8) and the magnetic gear in the compartment (7). Pressure vessel or tank contains nitrogen reservoir (17) at high pressure, eg 400 bar charge pressure, and nitrogen is supplied at a small but sufficient rate for the engine-gear compartment to maintain its Harmless atmosphere with respect to components to penetration of harmful driven gases which, in principle, will be kept out of the engine-gear compartment by the flow of nitrogen from the engine compartment and to that of the compressor. Some penetration of contaminants into the gas being boosted can sometimes occur, but these components will be diluted to harmless levels by the continuous supply of nitrogen. Alternatively, nitrogen can be supplied through an umbilical tube.
    [0042] If the arrangement shown in Figure 4 is used with nitrogen supply from a pressure vessel, the flow regulation by a valve (18) can be controlled by measuring the pressure in the vessel (17). The pressure decrease is of expression for the flow out of the container with sufficient precision, because the temperature of the gas volume in the reservoir is close to constant, that is, the temperature of sea water, which in deep water is close to constant throughout the year. As an alternative to providing a small flow of nitrogen through a valve based on calculations and experience to keep the nitrogen atmosphere in compartment (7) harmless, the valve can be controlled by sensors having in the nitrogen atmosphere, which measure the concentration of contaminants in nitrogen: eg total hydrocarbons, selected hydrocarbons (eg heavy hydrocarbon molecules), water vapor, H2S, CO2, MEG vapor or other harmful components, which indicates the degree of contamination of the atmosphere. The valve (18) can thus based on these measurements regulate the nitrogen supply to keep the degree of contamination below a dangerous level. This level can be established by experience and knowledge about the tolerance of the various contaminants of materials in the compartment (7). Valve control (18) can be continuous or intermittent.
    [0043] In Figure 5 an illustration of a compressor is given in which the high-speed side of the motor of the magnetic gear is hermetically separated from the low-speed side of the motor by a partition or diaphragm also called a shield. In this way, the motor with its gear part and magnetic bearings is hermetically separated (compartment (7)) from the compressor with the high-speed gear part and magnetic bearings (compartment (8)). Some kind of pressure balance of the engine-gear compartment (7) atmosphere pressure compared to the compressor suction pressure in the (8) compartment will be necessary to keep the shield strength requirements reasonable. In Figure 5, pressure balance is provided by the supply of nitrogen from the reservoir (17) (or, alternatively, from the umbilical tube), through the transmission pressure tube (20), and by a Pressure-Volume Regulator, PVR which is a well known and proven device. A pressure transmission tube is connected to the compressor compartment, and the PVR will continuously compare and control the gear motor atmosphere pressure to be close to the compressor suction pressure.
    [0044] Pressure balancing can also be provided with an arrangement of pressure regulating valves (18) and (18') and a pressure sensor or sensors that detect the pressure difference between the engine-gear compartment and the compressor suction pressure.
    [0045] In Figure 6 is illustrated the pressure balance through the use of two counter valves controlled by measuring the pressure differential between the compartments (7) and (8). Nitrogen is supplied by the control valve (18), while the overpressure in the compartment (7) compared to the suction pressure of the compressor is released by the control valve (18’).
    [0046] In Figure 7 the following types of magnetic gears are illustrated: spur gear (parallel, radial), planetary and cycloid.
    [0047] Figure 8 illustrates a preferred embodiment of the invention in which a stator (21) is arranged in a stator housing (22) separated by a partition (16) from a rotor housing (28), the housing of rotor comprises a compressor (2) or pump disposed directly on the rotor shaft or coupled to the rotor (23). Preferably, pump or compressor impellers, or both, are disposed directly on the rotor shaft. Preferably the partition (16) hermetically seals the stator compartment from the rotor compartment. The partition preferably includes pole pieces (24), electromagnets, or both, for better magnetic coupling, disposed between the gear sides for a controllable gear ratio or assembly. The gear ratio can be controlled through the control of optional electromagnets in the partition, the rotor position can be inferred from the stator impedance through an algorithm or a look-up table. The rotor shaft may preferably comprise bearings at each end, and also on the shaft between the rotor and impellers if necessary.
    [0048] Figure 9 illustrates a preferred subsea turbomachine or a general effect turbomachine or pressure intensifier, according to the invention, in which the magnetic gear is a radial magnetic gear with the partition (16) placed between the inner part ( 25) and external parts (26). Increased gear length allows for better magnetic coupling and greater transfer effect, which is preferable, but may require extra bearings at the gear end of the shaft. The divider comprises pole magnetic pieces or electromagnets (25) or both in the partition between the lower speed and higher speed sides of the gear. The number of pole parts and/or electromagnets is related to the gear ratio, preferably the number of rotor elements and the number of pole parts or electromagnets is a multiple or fraction of the number of stator elements, the fractional or fractional ratios or multiples refer to gear ratio. The gear ratio can be controlled by energizing or not energizing the electromagnets in the partition, said electromagnets are preferably electrically connected to the power source or stator side, avoiding any slip rings or other types of rotating electrical connections. This figure illustrates in greater detail the magnetic gear, the partition (16) and pole parts (24), or similar, and the common pressure housing (3), while the motor with stators (21) and rotor (23), and the compressor (2) are illustrated out of scale and not in detail for clarity. Bearings and some other features are not illustrated or are only indicated for the sake of clarity in order to show more clearly how the magnetic gear coupling can be configured and arranged. With a radial gear of the illustrated type, whose side is the inner or outer side, or the faster or slower side, it may be subject to a design choice, however, in many cases, the faster side should be the side. internal as this, in most cases results in lower levels of stress.
    [0049] Some of the advantages of the invention are as follows: Non-contact elements - no friction between the elements. High torque transfer due to multi-pole interaction. Peak torque utilization. Input and output shafts can be isolated. Increased temperature range, no elastomer seals. Inherent overload protection. Increased misalignment tolerance. Various options to arrange gear ratio changes, various electronic and mechanical options. The lubrication and liquid supply system can be eliminated. The pressure boosters or turbomachines of the invention may include any features described or illustrated herein, in any operative combination, each such combination being an embodiment of the present invention. The invention also provides the use of the turbomachinery and pressure intensifier of the present invention to increase the pressure of fluids in subsea and surface regions, particularly of subsea oil and gas.
    权利要求:
    Claims (13)
    [0001]
    1. Subsea turbomachine for intensifying the pressure of oil fluid flow from wells or subsea oil production systems comprising an electric motor (1) comprising a rotor (23) and a stator (21), the rotor and the stator being arranged in an engine compartment (7); and a compressor (2) or pump driven by the electric motor, a fluid inlet (5) and a fluid outlet (6), wherein the turbomachine comprises: a pressure housing (3) common to the electric motor, and compressor or pump; a magnetic gear (13) inside the common pressure housing (3) for operative connection between the motor and the compressor or pump; a shaft (9) for electric motor and a shaft (9') for compressor or pump, characterized in that an outer ring of the magnetic gear (13) is connected to the motor shaft (9) and an inner ring of the magnetic gear (13) is connected to the compressor (9') or pump shaft, or the reverse, each shaft is suspended on radial bearings (11, 11', 11'', 11''') and at least one thrust bearing (12, 12'); and a partition (16) within the common pressure housing (3) arranged to hermetically separate the engine compartment from the compressor or pump compartment; a pressure balance system arranged between the engine compartment and the suction part of the compressor or pump compartment.
    [0002]
    2. Underwater turbomachinery, according to claim 1, characterized in that the ratio of the magnetic gear (13) is 1:1.
    [0003]
    3. Underwater turbomachinery, according to claim 1 or 2, characterized in that the magnetic gear (13) comprises permanent magnets.
    [0004]
    4. Underwater turbomachinery according to any one of claims 1 to 3, characterized in that the magnetic gear (13) comprises electromagnets (25) on the low speed side (14) or on the high speed side (15) or on both sides of the gear.
    [0005]
    5. Underwater turbomachinery according to claim 4, characterized in that the rotation speed of the magnetic field on the low speed side (14) or on the high speed side (15) or on both sides of the gear can be controlled to vary the speed of the compressor (2), up and down, compared to the speed of the motor shaft.
    [0006]
    6. Underwater turbomachinery according to any one of claims 1 to 5, characterized in that the magnetic gear (13) is arranged as a gearbox that makes it possible to change the step-up ratio when stopped by using a vehicle operated remotely or by a dedicated electric motor mounted inside or on the gearbox.
    [0007]
    7. Underwater turbomachinery, according to claim 1, characterized in that the bearings are magnetic bearings, operatively connected to the bearings of each axis through a 5-axis control system.
    [0008]
    8. Underwater turbomachinery, according to claim 1, characterized in that the engine compartment (7) is filled with liquid.
    [0009]
    9. Underwater turbomachinery, according to claim 1, characterized in that an engine compartment (7) has a supply of nitrogen that constitutes the main component of the atmosphere of said compartment; the internal pressure of the pressure compartment is balanced with the suction pressure of the compressor by a pressure-volume regulator or the pressure of the compartment is balanced with the suction pressure of the compressor by means of control valves (18) and (18' ) by controlled sensing of the pressure differential between the suction side of the compressor and the atmosphere in the engine compartment (7).
    [0010]
    10. Underwater turbomachinery, according to claim 9, characterized in that the supply of nitrogen by the valve (18) to the atmosphere of the engine compartment (7) is controlled by the measurement of contaminants in the atmosphere, and the supply is regulated in such a way that the level of contaminants is controlled and the flow of nitrogen from the reservoir (17) to the engine compartment (7) is controlled through the regulation of the valve (18).
    [0011]
    11. Underwater turbomachinery according to claim 10, characterized in that the magnetic gear is a radial magnetic gear with the partition disposed between the inner and outer parts of said radial magnetic gear.
    [0012]
    12. Underwater turbomachinery according to claim 10, characterized in that the magnetic gear is a cycloid magnetic gear with the partition disposed between the inner and outer parts of said cycloid magnetic gear.
    [0013]
    13. Underwater turbomachinery, according to claim 7, characterized by the fact that it does not have a lubrication system and external liquid supply.
    类似技术:
    公开号 | 公开日 | 专利标题
    BR112013023523B1|2021-05-18|subsea turbomachine
    US10151318B2|2018-12-11|Omnirise hydromag “variable speed magnetic coupling system for subsea pumps”
    AU2008239947B2|2013-06-27|Fluid pump system
    BR112013030477B1|2020-11-17|compressor system
    EP2683944B1|2017-01-11|Subsea motor-turbomachine
    AU2012298577B2|2017-02-23|Dual motor pump for subsea application
    CN104235020A|2014-12-24|Rotary vane vacuum pump
    BRPI1105919A2|2013-05-28|system and method for hydrostatic temporary operation of hydrodynamic thrust bearings in a vertical fluid displacement module
    Grynning et al.2009|Tyrihans subsea raw seawater injection system
    CN103227521A|2013-07-31|Hollow rotor motor and systems comprising the same
    CN112913119A|2021-06-04|Motor pump
    CN112889203A|2021-06-01|Motor pump
    Stover et al.2019|Barrier Fluidless, Sealless Seawater Canned Motor Pumps
    US20210156384A1|2021-05-27|Pressure booster with integrated speed drive
    BR102020017390A2|2021-10-13|MULTIPHASE PUMP
    RU2418348C1|2011-05-10|Electric power generator of downhole telemetric system
    RU2307439C2|2007-09-27|Turbogenerator shaft stuffing arrangement
    Turnquist et al.2013|High-Temperature-High-Volume Lifting for Enhanced Geothermal Systems
    RU2435027C1|2011-11-27|Birotatory borehole generator
    RU2426874C1|2011-08-20|Borehole generator
    RU2442890C2|2012-02-20|Well generator
    RU2453698C2|2012-06-20|Downhole generator
    同族专利:
    公开号 | 公开日
    WO2012125041A1|2012-09-20|
    GB201317218D0|2013-11-13|
    GB2502505A|2013-11-27|
    GB2502505B|2018-06-27|
    US9841026B2|2017-12-12|
    AU2012229589A2|2014-04-24|
    BR112013023523A2|2016-12-06|
    CN103459853A|2013-12-18|
    CA2846780A1|2012-09-20|
    US20140086764A1|2014-03-27|
    US20180023573A1|2018-01-25|
    AU2012229589A1|2013-10-17|
    AU2012229589B2|2017-09-14|
    NO343629B1|2019-04-15|
    RU2608662C2|2017-01-23|
    RU2013143389A|2015-04-20|
    NO20131358A1|2013-10-14|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US1042965A|1912-06-26|1912-10-29|Corydon A Priest|Grafting-tool.|
    SU81471A1|1949-01-13|1949-11-30|А.М. Харитонов|Submersible pump|
    JPS5735195A|1980-08-08|1982-02-25|Izumi Pump:Kk|Submerged pump with magnet|
    FR2651839B1|1989-09-22|1992-07-10|Seeley Nominees Pty Ltd Ff|IMMERSED PUMPE.|
    NO172075C|1991-02-08|1993-06-02|Kvaerner Rosenberg As Kvaerner|PROCEDURE FOR OPERATING A COMPRESSOR PLANT IN AN UNDERWATER STATION FOR TRANSPORTING A BROWN STREAM AND COMPRESSOR PLANT IN A UNDERWATER STATION FOR TRANSPORTING A BROWN STREAM|
    DE9412591U1|1994-08-04|1994-10-06|Friatec Rheinhuette Gmbh & Co|Magnetic clutch pump|
    WO1996019034A1|1994-12-12|1996-06-20|Jorge De Armas|Electromagnetic-coupled/levitated apparatus and method for rotating equipment|
    US5641275A|1995-01-26|1997-06-24|Ansimag Inc.|Grooved shaft for a magnetic-drive centrifugal pump|
    RU2140574C1|1998-01-06|1999-10-27|Институт проблем морских технологий Дальневосточного отделения РАН|Submersible electromechanical drive for actuating mechanisms of underwater facilities|
    GB2396167B|2002-11-15|2005-06-08|Kvaerner Oilfield Products Ltd|Connector assembly|
    NO323324B1|2003-07-02|2007-03-19|Kvaerner Oilfield Prod As|Procedure for regulating that pressure in an underwater compressor module|
    JP2005269709A|2004-03-16|2005-09-29|Maguneo Giken:Kk|Magnetic rotation transmitting unit and sealed agitator|
    US7481270B2|2004-11-09|2009-01-27|Schlumberger Technology Corporation|Subsea pumping system|
    WO2006133703A1|2005-06-13|2006-12-21|Aalborg Universitet|Magnetic device for transfer of forces|
    CA2632042C|2005-11-30|2012-08-28|Dexter Magnetic Technologies, Inc.|Wellbore motor having magnetic gear drive|
    US7508101B2|2006-02-24|2009-03-24|General Electric Company|Methods and apparatus for using an electrical machine to transport fluids through a pipeline|
    NO326747B1|2006-06-30|2009-02-09|Aker Subsea As|Device and method for preventing the entry of seawater into a compressor module during immersion to or collection from the seabed|
    NO330192B1|2007-04-12|2011-03-07|Framo Eng As|Fluid Pump System.|
    NO327557B2|2007-10-09|2013-02-04|Aker Subsea As|Pump protection system|
    EP2065555B1|2007-11-30|2012-09-12|Siemens Aktiengesellschaft|Method for operating a compressor device and the compressor device|
    GB2457226B|2008-01-11|2013-01-09|Magnomatics Ltd|Drives for sealed systems|
    DE102008014379A1|2008-03-17|2009-09-24|Sycotec Gmbh & Co. Kg|Electromechanical machine e.g. permanent magnet synchronous motor, has rotor arranged in rotor area, whose boundary with exclusion of feed through of rotor shaft from rotor area is pressure sealed|
    US20100032952A1|2008-08-08|2010-02-11|Hatch Gareth P|Turbine generator having direct magnetic gear drive|
    CN101818736B|2009-02-27|2012-06-27|西门子（中国）有限公司|Magnetic pump|
    CN101705944B|2009-11-19|2011-04-13|中国石油大学|Underwater vertical oil-gas multiphase pump for offshore production wells|
    EP2330725B1|2009-12-02|2014-02-26|Grundfos Management A/S|Flow generation unit|
    CN101922456B|2010-04-16|2012-02-15|江苏大学|Magnetic-gear high temperature-resistant high-speed magnetic pump|
    WO2012125041A1|2011-03-15|2012-09-20|Aker Subsea As|Subsea pressure booster|WO2012125041A1|2011-03-15|2012-09-20|Aker Subsea As|Subsea pressure booster|
    US10020711B2|2012-11-16|2018-07-10|U.S. Well Services, LLC|System for fueling electric powered hydraulic fracturing equipment with multiple fuel sources|
    US10119381B2|2012-11-16|2018-11-06|U.S. Well Services, LLC|System for reducing vibrations in a pressure pumping fleet|
    NO337176B1|2013-01-10|2016-02-01|Aker Subsea As|Sealed pump|
    NO335314B1|2013-03-01|2014-11-10|Aker Subsea As|Turbo machine assembly with magnetic shaft lift|
    NO335529B1|2013-04-12|2014-12-22|Aker Subsea As|Turbo machine assembly with magnetic coupling and magnetic lift|
    DE102013214911A1|2013-07-30|2015-02-05|Siemens Aktiengesellschaft|Underwater compressor for compressing a gas under water and using the underwater compressor|
    EP3165510A1|2015-11-03|2017-05-10|Grundfos Holding A/S|Centrifugal pump assembly|
    US10859084B2|2016-04-26|2020-12-08|Onesubsea Ip Uk Limited|Subsea process lubricated water injection pump|
    US10763736B2|2016-06-24|2020-09-01|Onesubsea Ip Uk Limited|Long distance power transmission with magnetic gearing|
    GB201708289D0|2017-05-24|2017-07-05|Rolls Royce Plc|Preventing electrical breakdown|
    NO20180224A1|2018-02-13|2018-11-06|Aker Solutions As|Subsea machine with magnetic coupling|
    WO2020081313A1|2018-10-09|2020-04-23|U.S. Well Services, LLC|Electric powered hydraulic fracturing pump system with single electric powered multi-plunger pump fracturing trailers, filtration units, and slide out platform|
    EP3883355A1|2020-03-16|2021-09-22|ABB Schweiz AG|A subsea installation|
    RU2751727C1|2020-09-21|2021-07-16|Федеральное государственное бюджетное учреждение науки Институт океанологии им. П.П. Ширшова РАН|Remote-controlled underwater maneuvering vehicle|
    法律状态:
    2018-12-18| B06F| Objections, documents and/or translations needed after an examination request according [chapter 6.6 patent gazette]|
    2019-10-01| B25F| Entry of change of name and/or headquarter and transfer of application, patent and certif. of addition of invention: change of name on requirement|Owner name: AKER SUBSEA AS (NO) Free format text: A FIM DE ATENDER A(S) ALTERACAO(OES) REQUERIDA(S) ATRAVES DA PETICAO NO 870190054497 DE 13/06/2019, E NECESSARIO APRESENTAR PROCURACAO ATUALIZADA ONDE CONSTE O NOVO NOME DA TITULAR E A NOMEACAO DO PROCURADOR DEFINITIVO. |
    2019-12-03| B25L| Entry of change of name and/or headquarter and transfer of application, patent and certificate of addition of invention: publication cancelled|Owner name: AKER SUBSEA AS (NO) Free format text: ANULADA A PUBLICACAO CODIGO 25.6 NA RPI NO 2543 DE 01/10/2019 POR TER SIDO INDEVIDA. |
    2019-12-24| B25D| Requested change of name of applicant approved|Owner name: AKER SOLUTIONS AS (NO) |
    2020-01-07| B06U| Preliminary requirement: requests with searches performed by other patent offices: procedure suspended [chapter 6.21 patent gazette]|
    2021-03-02| B09A| Decision: intention to grant [chapter 9.1 patent gazette]|
    2021-05-18| B16A| Patent or certificate of addition of invention granted|Free format text: PRAZO DE VALIDADE: 20 (VINTE) ANOS CONTADOS A PARTIR DE 15/03/2012, OBSERVADAS AS CONDICOES LEGAIS. |
    优先权:
    申请号 | 申请日 | 专利标题
    NO20110398|2011-03-15|
    NO20110398|2011-03-15|
    PCT/NO2012/000028|WO2012125041A1|2011-03-15|2012-03-15|Subsea pressure booster|
    [返回顶部]