WO2014168488A1 - Ensemble turbomachine sous-marin comprenant un dispositif de levage magnétique et un accouplement magnétique - Google Patents

Ensemble turbomachine sous-marin comprenant un dispositif de levage magnétique et un accouplement magnétique Download PDF

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Publication number
WO2014168488A1
WO2014168488A1 PCT/NO2014/050056 NO2014050056W WO2014168488A1 WO 2014168488 A1 WO2014168488 A1 WO 2014168488A1 NO 2014050056 W NO2014050056 W NO 2014050056W WO 2014168488 A1 WO2014168488 A1 WO 2014168488A1
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WO
WIPO (PCT)
Prior art keywords
magnetic
turbomachine
shaft
motor
assembly
Prior art date
Application number
PCT/NO2014/050056
Other languages
English (en)
Inventor
Kjell Olav Stinessen
Svenn Ivar FURE
Terje STEINGRIMSEN
Original Assignee
Aker Subsea As
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Aker Subsea As filed Critical Aker Subsea As
Publication of WO2014168488A1 publication Critical patent/WO2014168488A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • F04D29/058—Bearings magnetic; electromagnetic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/026—Units comprising pumps and their driving means with a magnetic coupling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D25/0686—Units comprising pumps and their driving means the pump being electrically driven specially adapted for submerged use

Definitions

  • the present invention relates to a turbomachine assembly adapted for pressure boosting. More specifically, the invention relates to subsea compressors and pumps, for boosting the pressure of gas, multiphase or liquid from subsea petroleum production wells or systems.
  • the pressure of a petroleum reservoir declines during production.
  • pressure boosting can be required.
  • a typical power requirement for pressure boosting with pumps is 200-1000 kW and with compressors 5-15 MW.
  • the state of the art of subsea pumps (single and multiphase) (cf. Fig. 1 ) is that there is a mechanical seal between the liquid filled motor and the pump to prevent ingress of contaminants from the pump to the motor.
  • the motor is supplied with a barrier fluid through a tube in an umbilical.
  • a tube in the umbilical for supply of barrier fluid represents a significant cost. If for instance the umbilical has a length of 100 km, the cost of the tube for the barrier fluid could cost more than the turbomachine itself.
  • a pressure-volume-regulator can be connected to the barrier supply and the internal of the motor such that the motor has an overpressure compared to the pump. Hence leakages will flow from the motor to the pump and prevent ingress of harmful contaminants.
  • a mechanical seal is however a weak point of a turbomachine assembly with a high failure rate due to wear and tear, thus reducing the reliability of the machine. The invention completely eliminates this source of failure together with completely elimination of leakage.
  • a common design of subsea compressors includes a labyrinth seal between motor and compressor to prevent ingress of particles.
  • the motor will be filled with gas that has the same chemical composition as the gas that is being compressed because there will always be some pressure communication between the internal of the motor and the compressor.
  • the internal of the motor will therefore be subject to chemical degradation due to harmful components of the gas, e.g. H2S
  • the motor is filled with an inert liquid, i.e. a liquid that is not harmful to the internal materials of the motor.
  • inert gas in the context of this patent description means any gas that is not harmful to the materials of the motor.
  • the inert gas can be dry nitrogen or dry methane.
  • bearings are magnetic bearings, it is also advantageous with reduction of the forces because the dimensioning of the electromagnets of magnetic bearings with their power supply, including amplifiers, can be significantly reduced. This is also favourable for cooling of the subsea control system for the magnetic bearings.
  • a continuous reduction of the downward force on the magnetic bearings will also be beneficial if the power supply to the electromagnets should disappear and the shaft lands on the auxiliary back up bearings because the load and frictional heating and wear of these bearings will be reduced.
  • a subsea turbomachine assembly comprising a motor driving a motor shaft and a turbomachine with a
  • turbomachine shaft an axial bearing and two radial bearings.
  • the turbomachine assembly further comprises a magnetic lifting assembly comprising a magnetic reaction element coupled to the motor shaft and/or the turbomachine shaft, and a magnetic lifting element coupled to the housing and operatively connectable to the magnetic reaction element.
  • the magnetic lifting assembly is adapted to exert a lifting force onto the motor shaft or the turbomachine shaft.
  • the turbomachine assembly further comprises a magnetic coupling between the motor shaft and the turbomachine shaft.
  • the magnetic coupling is adapted to transmit rotational movement between them.
  • a fluid tight barrier extends through the magnetic coupling and separates the motor shaft from the turbomachine shaft.
  • both the turbomachine shaft and the motor shaft are provided with a magnetic lifting assembly.
  • the turbomachine assembly is employed for boosting pressure of a hydrocarbon flow at the seabed.
  • the magnetic coupling can be of any type, e.g. cylindrical or flat.
  • the barrier between the driver and the follower is leakage tight and hence prevents leakages between the compartment of the motor and the turbo- machine.
  • the design of driver and follower shall not be limited to the designs shown herein.
  • Another advantage is if the barrier is strong enough to withstand pressure differences between motor and turbo-machine in all modes of operations, including start-up, steady sate, transients, shut down, stand still and installation and retrieval. Hence a pressure balancing system during the aforementioned modes of operation is not necessary.
  • a system for keeping the pressure difference between the internal motor room (motor compartment) and the turbo-machine between some limits, say ⁇ 100 bar, may be included as an emergency system to prevent high strain to the barrier during some modes of operation or destruction of barrier at off-design or unpredicted and unexpected conditions.
  • the coupling is a permanent magnet coupling, but couplings with electromagnets either on the driver or the follower or on both sides can also be adapted for subsea pressure boosters.
  • the invention shall not be limited with respect to type of magnetic coupling and it can either be of the permanent magnet or the electromagnet type.
  • the most suitable type of coupling will be selected from case to case base among other things on the state of the art of the various types.
  • the motor, coupling and turbo-machine can advantageously be arranged in a common pressure housing.
  • the barrier also sometimes called partition or shroud
  • the motor then divides the common pressure housing into two compartments where the motor with the driver of the magnetic coupling is installed in one compartment and the turbo-machine with the follower of the magnetic coupling is installed. Because there is no leakage from the motor to the turbo-machine, the motor can be filled with a suitable inert fluid, i.e. an inert gas or liquid, and there will be no need additional supply of said fluid.
  • the inert fluid will neither be harmed by ingress of contaminants.
  • the pressure housing can be one piece, since the number of possible fluid leakage paths thereby is minimized.
  • the pressure housing can have flanges between the compartments with main components if this is found favorable for replacing components at a later stage.
  • the turbomachine assembly comprises shafts with any type of suitable bearings for the different turbo-machines. There will be at least two radial bearings for the motor shaft, and also at least one trust bearing if the trust is higher than the radial bearings can take. The same configuration of bearings will be for the turbomachine.
  • turbomachine is a pump or multiphase pump
  • it will be favorable to drive the pump by a high speed gas filled motor with magnetic bearings because this will allow larger capacities of such pumps by not being limited by the maximum size and speed of liquid filled motors.
  • Liquid filled motors are limited in power size because the diameter of the rotor must be small to prevent too much frictional losses and hence a motor of say more than 3 MW will be impractically long and susceptible to rotodynamic problems.
  • frictional losses the practical speed limit of a large liquid filled electric motor is in the order of 4000 rpm, that also reduces the feasibility of stretching the power size of the motor (power is proportional to speed).
  • the limitation in speed of liquid filled motors implies a high number of impellers to achieve a high pressure increase over the pump and hence prevents a compact design. If the motor can be gas filled, the power and speed can be increased significantly before meeting some limitations, say 10-15 MW and 10 000 rpm as current status and more in the future. The limitation in speed will then be on the losses on the pump side, i.e. frictional and turbulent losses through the pump and losses in the bearings. Losses in the pump bearings depend on the type of bearings and their lubrication. If the bearings are product lubricated this will give a lower limitation in speed than with oil lubricated. The best solution in this respect will be magnetic bearings.
  • a solution of especially high potential for design of high speed pumps, say 6000 rpm and more, is by using magnetic bearings both for the motor shaft and the pump shaft. This will allow compact pumps with power of 10 MW or more and the motor will be protected from ingress of contaminants by the barrier of the magnetic coupling. If the motor is liquid filled, the motor compartment must have a system to allow for expansion and contraction of the liquid at different temperatures without harming the barrier or the motor housing.
  • a favorable solution for this is to pressure balance the motor compartment to the sea by a pressure balance device in a known way, e.g. a metal bellow.
  • Fig. 1 is a schematic view of a turbomachine assembly according to prior art
  • Fig. 2 is a schematic view of a turbomachine assembly according to the
  • Fig. 3 is a schematic part view of another turbomachine assembly according to the invention.
  • Fig. 4 is a cross section view through some parts of two embodiments of a horizontally arranged turbomachine assembly according to the invention
  • Fig. 5 is a schematic view of a control system in the form of a magnet control unit 80 which supplies electrical current to a magnetic lifting element 1 of a magnetic lifting assembly;
  • Fig. 6 is a schematic view of a control system in the form of a magnet control unit 80 which supplies electrical current to a bearing magnet of a magnetic bearing
  • Fig. 7 is a schematic view of a control system supplying electrical current to electromagnet of a magnetic lifting assembly as well as electromagnet of a magnetic bearing;
  • Fig. 8 is a schematic view of a control system supplying electrical current to electromagnet of a magnetic lifting assembly as well as electromagnet of a magnetic bearing, wherein the control system receives measuring input;
  • Fig. 9 shows an embodiment of the present invention, wherein the
  • turbomachine assembly is provided with a pressure control system.
  • Fig. 1 presents a prior art turbomachine assembly 100. Shown is a vertically arranged turbomachine assembly 100 having an electric motor 6 coaxially arranged with a turbomachine, here in the form of a pump 7.
  • the pump 7 has an inlet 10 and an outlet 11.
  • the inlet 10 and the outlet 1 1 are arranged on opposite sides of a set of impellers 9 that are arranged on a turbomachine shaft 15.
  • the turbomachine shaft 15 is coaxially fixed to a motor shaft 16.
  • the motor shaft 16 extends through the electric motor 6.
  • a motor rotor 12 is attached to the motor shaft 16, while a motor stator 13 is arranged to a housing 23.
  • the housing 23 encloses the motor 6 and the turbomachine 7.
  • the housing 23 encloses both the pump 7 and the motor 6.
  • the motor 6, along with the motor shaft 16, are arranged within a motor chamber 41.
  • the turbomachine 7, along with the turbomachine shaft 15, are arranged within a turbomachine chamber 42.
  • a shaft seal 8 is arranged in order to close fluid communication between the motor chamber 41 and the turbomachine chamber 42.
  • an axial bearing assembly comprising an axial bearing rotating disc 3 which is arranged axia between two axial bearing elements 4, which are fixed with respect to the housing 23.
  • the weight of the shafts 15, 16, motor rotor 12 and other components attached to the shaft 15, 16 is carried by the axial bearing assembly. During rotation of the impellers the force on the axial bearing assembly will vary.
  • Fig. 2 illustrates an embodiment according to the invention.
  • This turbomachine assembly 200 is also vertically arranged. It comprises a magnetic coupling 50 adapted to transmit rotational forces and movement between the coaxially arranged motor shaft 16 and turbomachine shaft 15.
  • the magnetic coupling 50 comprises a coupling driver 19 which is arranged on the motor shaft 16 and a coupling follower 18 which is arranged on the turbomachine shaft 15.
  • the coupling driver 19 is arranged within the coupling follower 18.
  • a barrier 17, such as an appropriately shaped wall, is arranged between the driver 19 and the follower 18.
  • the barrier ensures that fluid within the motor chamber 41 is not communicated with fluid within the turbomachine chamber 42. In this manner, it is ensured that the fluid flowing through the turbomachine 7, between the inlet 10 and outlet 1 1 , does not enter the motor chamber 41.
  • a fluid will typically be a fluid produced from a subsea well and may contain components that could be harmful to the motor 6, as described above.
  • the motor chamber 41 can advantageously be filled with an inert gas.
  • the pressure of this gas should initially be adjusted to some suitable level between a maximum and minimum pressure which the turbomachine 7 will experience in the operational period, say some years. This is in order to limit the maximum pressure difference between motor compartment 6 and turbo-machine compartment 7.
  • a system 60 for keeping the pressure difference between the motor chamber 41 and the turbomachine chamber 42 within some chosen limits, say ⁇ 100 bar, can be included as an emergency system to prevent high strain to the barrier 17.
  • the pressure control system 60 comprises a pressure tank 61 connected to a valve and control assembly 62.
  • the valve and control assembly 62 is connected to the motor chamber 41 through a motor chamber line 63, and is thus able to control the pressure within the motor chamber 41.
  • To the turbomachine chamber 42 extends a turbomachine chamber sensor line 64, adapted to provide the valve and control assembly 62 with current pressure values of the turbomachine chamber 42.
  • the magnetic lifting assembly 20 comprises a magnetic reaction element 2 and a magnetic lifting element 1 arranges axially opposite of the magnetic reaction element 2.
  • the magnetic lifting element 1 is fixed relative to the housing 23 and exerts a magnetic force on the magnetic reaction element 2, thereby relieving the weight carried by the axial bearing assembly (axial bearing rotating disc 3 and axial bearing elements 4).
  • the motor shaft 16 is provided with a magnetic lifting assembly 20 having a magnetic reaction element 2 at its upper end. Axially above the magnetic reaction element 2 there is a magnetic lifting element 1 which is fixed to the housing 23.
  • the magnetic lifting element 1 exerts an upwardly directed force on the magnetic reaction element 2 arranged on the motor shaft 16, thereby relieving the weight carried by the axial bearing assembly 3, 4 of the motor shaft 16.
  • the magnetic lifting element 1 can comprise a permanent magnet. In such embodiments the magnetic lifting element(s) 1 will always exert an upwardly directed force onto the shafts 15, 16.
  • the direction of the magnets will naturally be arranged so that there is provided a repulsive magnetic force at the lower end of the turbomachine shaft 15 and an attractive magnetic force at the upper end of the motor shaft 16 (provided the motor 6 and turbomachine 7 are arranged in the mutual orientation as shown in Fig. 2). Also shown in Fig. 2 are a set of magnetic radial bearings 150, which will be described below.
  • Fig. 3 shows the upper portion of an embodiment of a turbomachine assembly 300 which is similar to the one shown in Fig. 2, however with another type of magnetic lifting assembly.
  • the magnetic lifting assembly 30 comprises a disc shaped magnetic reaction element 2, shaped as a flange, attached to the motor shaft 16 at a distance from its upper end. Axially below the magnetic reaction element 2, the magnetic lifting assembly 30 comprises a circular magnetic lifting element 1 which is fixed relative to the housing 23. A repulsive magnetic force exists between the magnetic reaction element 2 and the magnetic lifting element 1.
  • Such a magnetic lifting assembly 30 may also be arranged in association to the turbomachine shaft 15.
  • the subsea turbomachine assembly 300 further comprises a magnetic bearing 70.
  • the turbomachine assembly 300 is vertically arranged, and the magnetic bearing 70 is an axial magnetic bearing.
  • the magnetic bearing 70 comprises a disc magnet 71 fixed to the motor shaft 16.
  • the disc magnet 71 is arranged axially between a pair of circular bearing magnets 73.
  • the bearing magnets 73 are fixed relative to the housing 23.
  • the turbomachine shaft 15 (not shown in Fig. 3) may
  • Fig. 4 shows a cross section view through another type of magnetic lifting assembly 40.
  • the magnetic lifting assembly 40 is adapted for a horizontally arranged shaft (the shaft is not shown in Fig. 4).
  • a magnetic reaction element 2 has a circular shape and is adapted to be fixed to a horizontal shaft.
  • a magnetic pole of the magnetic reaction element 2 faces radially outwards, while the opposite pole faces radially inwards.
  • the first magnetic lifting element 1 a is adapted to face the magnetic reaction element 2 with an identical magnetic pole, thereby providing a repulsive magnetic force onto the shaft.
  • Above magnetic reaction element 2 there is a second magnetic lifting element 1 b which is adapted to attract the magnetic reaction element 2. Even if two magnetic lifting elements 1 a, 1 b are shown in Fig. 4, one could also imagine having only one of them.
  • Fig. 4 could also be interpreted as a schematic view of a magnetic radial bearing 150 (cf. Fig. 2).
  • the inner ring could then be a disc magnet 151 , while the two curved elements would be a first bearing magnet 153a and second bearing magnet 153b of the magnetic radial bearing 150.
  • magnetic bearing 70 and/or the magnetic lifting assembly 20, 30, 40 may be based on permanent magnets, they may, in stead or in addition, comprise electrically operated magnets. With electromagnets one may control the function of the magnetic bearing and/or the lifting assembly.
  • Fig. 5 schematically illustrates a control system comprising or being in the form of a magnet control unit 80 which supplies electrical current to a magnetic lifting element 1 of a magnetic lifting assembly 20, 30, 40.
  • the magnetic force inflicted on the magnetic reaction element 2 depends on the amount of current delivered to the electromagnet of the magnetic lifting element 1 .
  • Fig. 6 schematically illustrates a magnet control unit 80 which supplies electrical current to bearing magnets 73 of the magnetic bearing 70.
  • Fig. 7 shows a similar schematic illustration of a magnet control unit 80 which controls both a magnetic bearing 70, via the bearing magnet 73, and a magnetic lifting assembly 20, 30, 40, via the magnetic lifting element 1 .
  • the magnet control unit 80 controls a bearing magnet 73, and a magnetic lifting element 1 .
  • a sensor input unit 90 which provides the magnet control unit 80 with information of the characteristics of the shaft 15, 16. That is, the magnet control unit 80 is provided with information regarding the position of the shaft(s) 15, 16, thereby making the magnet control unit 80 able to adapt the control according to physical behavior of the shaft.
  • the magnet control unit 80 could also control the first bearing magnet 153a and second bearing magnet 153b of the magnetic radial bearing 150.
  • the magnet control unit 80 also could control the first and/or second magnetic lifting element 1 a, 1 b of the embodiment shown in Fig. 4, namely the horizontal shaft.
  • a permanent magnet V which could typically be a magnetic reaction element of a magnetic lifting assembly 20, 30, 40. It could also be a part of a magnetic bearing 70, 150. As indicated in Fig. 8, the permanent magnet V is not controlled by the magnet control unit 80.
  • the magnet control unit 80 may also be part of a larger control system adapted for control of more parameters of the turbomachine assembly 200, 300.
  • Fig. 9 depicts a schematic view of the magnetic coupling 50 between the motor shaft 16 and the turbomachine shaft 15, and the intermediate barrier 17.
  • the coupling follower 18 is arranged within a surrounding coupling driver 19.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Magnetic Bearings And Hydrostatic Bearings (AREA)

Abstract

L'invention concerne un ensemble turbomachine sous-marin comprenant un moteur (6) entraînant un arbre de moteur (16) et une turbomachine (7) comprenant un arbre de turbomachine (15), un palier axial (3, 4) et deux paliers radiaux (5). L'ensemble turbomachine comprend un ensemble de levage magnétique (20, 30, 40) comprenant un élément de réaction magnétique (2) accouplé à l'arbre de moteur (16) et/ou à l'arbre de turbomachine (15) et un élément de levage magnétique (1, 1a, 1b) accouplé à un logement (23) et pouvant être fonctionnellement raccordé à l'élément de réaction magnétique (2). L'ensemble turbomachine comprend en outre un accouplement magnétique (50) entre l'arbre de moteur (16) et l'arbre de turbomachine (15) conçu pour transmettre un mouvement de rotation entre eux. Une barrière étanche aux fluides (17) s'étend à travers l'accouplement magnétique (50) et sépare l'arbre de moteur (16) de l'arbre de turbomachine (15).
PCT/NO2014/050056 2013-04-12 2014-04-11 Ensemble turbomachine sous-marin comprenant un dispositif de levage magnétique et un accouplement magnétique WO2014168488A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
NO20130506A NO335529B1 (no) 2013-04-12 2013-04-12 Turbomaskinsammenstilling med magnetkobling og magnetløft
NO20130506 2013-04-12

Publications (1)

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WO2014168488A1 true WO2014168488A1 (fr) 2014-10-16

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WO (1) WO2014168488A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016087303A1 (fr) * 2014-12-05 2016-06-09 Nuovo Pignone Srl Unité de moteur-compresseur à paliers magnétiques
US20160333677A1 (en) * 2015-05-11 2016-11-17 Fuglesangs Subsea As Omnirise hydromag "variable speed magnetic coupling system for subsea pumps"
US20230235740A1 (en) * 2016-09-20 2023-07-27 Vetco Gray Scandinavia As Arrangement for pressurizing of fluid

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3802950A1 (de) * 1988-02-02 1989-08-10 Klein Schanzlin & Becker Ag Pumpe mit permanentmagnetischer abhebevorrichtung
JPH07119680A (ja) * 1993-10-27 1995-05-09 Hitachi Ltd 液化ガスタンク用潜没ポンプ装置
JPH1061584A (ja) * 1996-08-21 1998-03-03 Hitachi Ltd 液化ガス用潜没ポンプ装置およびその磁気軸受装置
WO2012121605A1 (fr) * 2011-03-07 2012-09-13 Aker Subsea As Turbomachine sous-marine
WO2012125041A1 (fr) * 2011-03-15 2012-09-20 Aker Subsea As Surpresseur sous-marin

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5961301A (en) * 1997-07-31 1999-10-05 Ansimag Incorporated Magnetic-drive assembly for a multistage centrifugal pump
GB2490149A (en) * 2011-04-20 2012-10-24 Corac Group Plc Magnetic gearbox with gas bearings

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3802950A1 (de) * 1988-02-02 1989-08-10 Klein Schanzlin & Becker Ag Pumpe mit permanentmagnetischer abhebevorrichtung
JPH07119680A (ja) * 1993-10-27 1995-05-09 Hitachi Ltd 液化ガスタンク用潜没ポンプ装置
JPH1061584A (ja) * 1996-08-21 1998-03-03 Hitachi Ltd 液化ガス用潜没ポンプ装置およびその磁気軸受装置
WO2012121605A1 (fr) * 2011-03-07 2012-09-13 Aker Subsea As Turbomachine sous-marine
WO2012125041A1 (fr) * 2011-03-15 2012-09-20 Aker Subsea As Surpresseur sous-marin

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016087303A1 (fr) * 2014-12-05 2016-06-09 Nuovo Pignone Srl Unité de moteur-compresseur à paliers magnétiques
CN107250548A (zh) * 2014-12-05 2017-10-13 诺沃皮尼奥内股份有限公司 具有磁性轴承的马达压缩机单元
US10151316B2 (en) 2014-12-05 2018-12-11 Nuovo Pignone Srl Motor compressor unit with magnetic bearings
US20160333677A1 (en) * 2015-05-11 2016-11-17 Fuglesangs Subsea As Omnirise hydromag "variable speed magnetic coupling system for subsea pumps"
WO2016189397A1 (fr) * 2015-05-11 2016-12-01 Fuglesangs Subsea As Unité d'entraînement à vitesse variable, magnétique, hydrodynamique submergé
WO2017013519A1 (fr) * 2015-05-11 2017-01-26 Fuglesangs Subsea As Unité d'entraînement à vitesse variable, magnétique, hydrodynamique immergée
US9964113B2 (en) 2015-05-11 2018-05-08 Fuglesangs Subsea As Omnirise hydromag “variable speed magnetic coupling system for subsea pumps”
US20180209253A1 (en) * 2015-05-11 2018-07-26 Fuglesangs Subsea As Omnirise hydromag "variable speed magnetic coupling system for subsea pumps"
US10151318B2 (en) 2015-05-11 2018-12-11 Fuglesangs Subsea SA Omnirise hydromag “variable speed magnetic coupling system for subsea pumps”
EA033282B1 (ru) * 2015-05-11 2019-09-30 Фуглесангс Сабси Ас Погружное регулируемое приводное устройство с гидродинамической и магнитной муфтами
US20230235740A1 (en) * 2016-09-20 2023-07-27 Vetco Gray Scandinavia As Arrangement for pressurizing of fluid

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NO335529B1 (no) 2014-12-22
NO20130506A1 (no) 2014-10-13

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