EP3132142B1 - Anti-surge control of a subsea compressor - Google Patents

Anti-surge control of a subsea compressor Download PDF

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Publication number
EP3132142B1
EP3132142B1 EP15716522.6A EP15716522A EP3132142B1 EP 3132142 B1 EP3132142 B1 EP 3132142B1 EP 15716522 A EP15716522 A EP 15716522A EP 3132142 B1 EP3132142 B1 EP 3132142B1
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EP
European Patent Office
Prior art keywords
surge
valve
controller
compressor
rotor
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Active
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EP15716522.6A
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German (de)
English (en)
French (fr)
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EP3132142A1 (en
Inventor
Jorgen Harald CORNELIUSSEN
Duccio Fioravanti
Massimiliano ORTIZ NERI
Leonardo Baldassarre
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Vetco Gray Scandinavia AS
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Vetco Gray Scandinavia AS
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Priority to PL15716522T priority Critical patent/PL3132142T3/pl
Publication of EP3132142A1 publication Critical patent/EP3132142A1/en
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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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/001—Testing thereof; Determination or simulation of flow characteristics; Stall or surge detection, e.g. condition monitoring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/02—Surge control
    • F04D27/0207—Surge control by bleeding, bypassing or recycling fluids
    • F04D27/0223—Control schemes therefor
    • 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

Definitions

  • the present invention refers to the prevention of surge in a compressor that is arranged to be operated and used in the transport of gas from a subsea hydrocarbon fluid deposit.
  • the invention refers to a method by which a subsea compressor, the rotor of which is supported by active magnetic bearings for contact-free rotation, is arranged to be switched from normal operation into anti-surge operational mode, such as in a case of insufficient flow in a fluid processed by the compressor.
  • the invention also refers to a subsea compression system arranged for implementation of the method.
  • the radial or centrifugal compressor In subsea hydrocarbon production compressors can be used to aid in transport of gas from a subsea hydrocarbon fluid deposit via an offshore pipeline to a surface platform, e.g. Suitable for compression of gas in the subsea environment, the radial or centrifugal compressor comprises a rotor equipped with wheels or impellers, operated in rotation by an electric motor.
  • the compressor is capable of achieving a rise in pressure in a gaseous fluid that is fed continuously through the compressor.
  • a gas compressor can be described in terms of three operating parameters: speed, head and flow.
  • speed the compressor delivers a maximum head and a corresponding flow, defining a state of stable operation.
  • Stable operation can be maintained as long as a reduction in head is compensated by an increase in flow. If flow is reduced when the compressor has reached its maximum head capability, the compressor rotor spins idling in the gas which is no longer propelled forward by the rotor.
  • the system pressure that is build up at the compressor outlet may force the gas to pass the rotor backwards, reversing the flow through the compressor. At a point where the compressor can no longer add to the fluid the energy required to overcome the backpressure, the compressor is going into surge.
  • a compressor's performance can be defined as a relation between pressures at compressor inlet and outlet, or pressure ratio (discharge pressure divided by suction pressure) over the compressor, and flow at a given rotor speed.
  • pressure ratio discharge pressure divided by suction pressure
  • For each compressor its performance can be quantified and illustrated in a diagram wherein the horizontal axis represents the flow or amount of uncompressed gas passing the compressor inlet. The vertical axis represents compression pressure ratio that occurs inside the compressor.
  • For each rotor speed there is one relation between pressure ratio and flow at which the operation is stable. At a point where the flow no longer matches the pressure ratio and the relation is broken the compressor leaves the region of stable operation, going into a region characterized as the surge zone.
  • a line connecting the surge points for the whole range of operational rotor speeds represents the surge limit in a compressor map that illustrates and quantifies the performance of the subject compressor.
  • Preventing a compressor from operating in the surge zone usually involves recycling of the processed fluid from the compressor outlet to the compressor inlet to supplement an insufficient flow via the compressor inlet.
  • a valve normally closed in the recycle line is arranged to be shifted into open state in case of insufficient flow, switching the compressor from normal operation into what can be called an anti-surge operational mode.
  • An anti-surge control system is arranged to maintain the recycle valve, also called anti-surge valve (ASV), in closed position as long as the compressor operates well outside the surge zone. If the compressor gets close to the surge limit the anti-surge control system shifts the valve into the open position thus increasing the flow at the compressor inlet.
  • ASV anti-surge valve
  • the anti-surge control system may be arranged to generate a valve operating command based on several parameters which are monitored by appropriate sensors and meters.
  • the monitored parameters are typically the inlet and outlet pressures and temperatures, the differential pressure over the compressor, and the rotor speed.
  • US patent no. 4464720 discloses an anti-surge control based on sensing the inlet and outlet pressures and calculating an actual differential pressure that is compared with a desired set-point.
  • US patent no. 4971516 discloses an anti-surge control based on sensing the flow and the rotor speed and calculating the actual flow/speed ratio which is compared with the corresponding ratio at surge.
  • US patent no. 7094019 discloses an anti-surge control system that calculates the actual pressure ratio and the pressure ratio at surge based on monitoring speed, inlet and outlet pressures in order to operate the recycle valve when the actual pressure ratio is safely distanced from the pressure ratio at surge.
  • WO 2009/055878 A2 discloses measuring the electric currents flowing through the coils of magnetic bearings to calculate the forces on the bearings.
  • the gas compressor in general is very sensitive to disturbances in the flow and the demands are high on the anti-surge control system to react rapidly to changes in the process.
  • Anti-surge control systems wherein the valve operating command is generated topside from a main control system and based on input from sensors and transmitters that monitor the process parameters of flow, pressure and temperature in a compression system located at the sea floor, run the risk of being too slow to safeguard the compressor against surge.
  • the delay in reaction increases with increasing length of signal pathways between the subsea compression system and the topside facility hosting the main control system and its central logic.
  • EP 2042743A1 One earlier solution aiming for short signal pathways and fast response in the control and operation of the recycle valve is disclosed in EP 2042743A1 .
  • This document describes a land based gas compression system wherein the input voltage to the compressor motor drive unit is monitored, and a control unit adapted to determine whether there is a risk of surge based on the measured input voltage, and if that is the case, to generate a valve opening command.
  • Another attempt to reduce response times in an anti-surge control system involves the arrangement of a dedicated closed loop control system handling the anti-surge control through a compression system control module located at the site.
  • the present invention provides another solution for fast anti-surge valve response to be applied in conjunction with gas compressors wherein the compressor rotor is supported for contact free rotation by active magnetic bearings (AMB).
  • Active magnetic bearings can be arranged for contact-free support of the compressor rotor in both radial and axial directions of the rotor.
  • a magnetic conductive rotor is journalled in a stator that is magnetized by the current fed through appropriate electric windings.
  • the magnetic field generated by the stator windings induces the magnetic force needed to support the rotor.
  • Stator winding's currents are actively modulated on the basis of a feedback rotor position signal.
  • the feedback rotor position signal is provided by a sensor (i.e. inductive or eddy current) which is reacting to changes in the position of the rotor relative to the sensors and other non-rotating parts of the compressor.
  • the detected change in position is used in an AMB controller that controls the supply of current to the electric windings in the stator correspondingly, this way forcing the rotor to return to a centered position in the bearing.
  • the AMB controller is usually located short distance from the bearing for short signal pathways and fast response.
  • the AMB controller will not register much change in the position of the rotor which then rotates substantially free from vibration and under substantially constant load from the processed fluid. Should the compressor get close to or pass the surge limit the AMB controller will react to vibration and changes in the rotor's position resulting from changing loads applied to the rotor from the processed fluid.
  • the first mentioned object is met in a method comprising:
  • the first and second objects are both met in a method which further comprises:
  • the AMB control data used in determination of the force representing value comprises at least one of i) rotor position data, ii) amount of current fed through magnetic bearing coils, iii) amplitude in magnetic flux generated in the magnetic bearings.
  • Rotor position data can be acquired from position sensors, such as inductive or eddy current sensors arranged about the rotor.
  • the amount of current supplied to the magnetic bearing coils can be acquired from the active magnetic bearing controller.
  • the amplitude in the magnetic flux can be acquired by means of dedicated sensors, such as a Hall-effect sensor e.g., or can be estimated by the AMB controller based on the magnetic bearing characteristics and a combination of: i) the current signal, ii) the position signal, iii) the power amplifier voltage.
  • a possible method for the magnetic flux estimation is described by Gerhard Schweitzer . Eric H. Maslen in the section 4.5.3 of the book Magnetic Bearings published by Springer Verlag, Berlin, 2009 .
  • the method foresees that the force representing value can be evaluated by detecting the low frequency (LF) harmonic content in at least one of: i) a rotor position signal, ii) a current signal, iii) a magnetic flux signal, iv) a magnetic flux estimation.
  • VSA anti-surge valve switching actuator
  • the valve switching actuator is further configured to evaluate the AMB controller command in accordance with the following condition: if the force representing value exceeds the threshold value, then AMB controller command is TRUE, else AMB controller command is FALSE.
  • the threshold value can be predetermined while running the compressor in calibration. For example, threshold values can be determined while mapping the performance of the compressor during commissioning. More precisely, a set of threshold values related to different compressor rotor speeds can be compiled in a compressor map.
  • the LF harmonic content threshold value can be predetermined in a calibration process.
  • the content of LF harmonic oscillation and amplitude in the position signal, current signal or magnetic flux signal can be recorded for a range of rotor speeds with the rotor levitated by the magnetic bearings.
  • the first mentioned object of the present invention is likewise met in a subsea compression system comprising a compressor having a compressor rotor supported for contact-free rotation by active magnetic bearings, and further comprising:
  • Embodiments of the compression system further comprises an anti-surge valve switching actuator (VSA) that is interposed between the anti-surge valve on the one hand and the active magnetic bearing and anti-surge controllers, respectively, on the other hand.
  • VSA anti-surge valve switching actuator
  • the valve switching actuator in turn comprises an evaluation unit configured to generate a valve switching command based on input from either of the active magnet bearing controller or the anti-surge controller.
  • the actuation of the anti-surge valve can be achieved through a quick opening function activated by the active magnetic bearing controller.
  • the actuation of the anti-surge valve can be achieved through a quick opening function activated by the active magnetic bearing controller which overrides the anti-surge controller.
  • Fig. 1 illustrates a compression system 1 situated on the seafloor.
  • the subsea compression system 1 comprises a compressor 2 having a rotor 3 driven in rotation by a drive means, such as a motor 4, via a rotor shaft 5.
  • the motor and compressor assembly 2-5 is operable for raising the pressure in gas recovered from a subsea hydrocarbon fluid deposit for transport to a topside, land based or floating station, in the drawings illustrated as a surface platform 6 by way of example, via pipeline sections 7 and 8.
  • the compressor 2 is connected to the pipeline through a compressor inlet 9 via which the fluid is sucked and through a compressor outlet 10 via which the fluid is discharged at higher pressure and elevated temperature.
  • the flow direction is illustrated through arrows F IN and F OUT .
  • Power and process control is supplied from the topside station and distributed via a power/control umbilical 11 which connects a topside umbilical termination unit (TUTU) 12 to a subsea umbilical termination assembly (UTA) 13.
  • TUTU topside umbilical termination unit
  • UTA umbilical termination assembly
  • power and process control is governed by the main control system (MCS) 14 that is arranged topside, and which communicates with a compression system control module (CSCM) 15 arranged subsea.
  • the CSCM 15 comprises control logic and communication capacity to the topside controls via the power/control umbilical 11.
  • CSCM 15 Through the CSCM 15, a number of process parameters can be monitored and controlled, either directly in the CSCM 15 or indirectly from the topside located MCS 14.
  • PDM 16 and VSD 17 units electrical power to the compressor motor and other subsea power consumers is supplied via a power distribution module (PDM) 16.
  • PDM 16 and VSD 17 units may entirely or in part be located in the CSCM 15, or located topside such as in the MCS 14, e.g.
  • the depth at which the compression system may be located typically is in the range of several hundred meters up to the order of kilometers, whereas the distance from the compression station to a land based receiving station 6 may amount to one hundred kilometers or more.
  • the compressor rotor 3 is supported by active magnetic bearings in which it is levitated for contact-free rotation.
  • the rotor position is monitored by position sensors 18 that continuously detect the rotor's position relative to electromagnets 19.
  • the rotor 3 is journalled in radial bearings 20 and 21 supporting the rotor and counteracting the weight of the rotor (in horizontal orientation) and the radial loads and forces acting on the rotor from the process load.
  • the rotor 3 is further levitated in thrust bcaring(s) 22 which hold(s) the rotor in levitation while compensating for and counteracting the weight of the rotor (in vertical orientation) and the axial load acting on the rotor from the processed medium.
  • the electromagnets 19 of the thrust bearing 22 are arranged on opposite sides of a radial disc 23 which is fixed onto the rotor shaft 5.
  • Auxiliary bearings will typically be arranged to protect the magnetic bearings from contact with the rotor during start and stop procedures or in case of excessive displacements of the rotor. Auxiliary bearings are omitted from the drawings of Figs. 1-3 for simplicity reasons.
  • an active magnetic bearing (AMB) controller 24 regulates and supplies the amount of current to the electromagnets 19 that is required to maintain the rotor in contact-free rotation, compensating and counteracting a change or deviation in the rotor's position relative to ideal positions in the electromagnet bearings 20-22.
  • AMB active magnetic bearing
  • valve 25 that controls the flow in a recycle line 26 connecting the outlet and inlet sides of the compressor.
  • the valve 25 is normally closed and shifted into an open state in case the compressor is about to go into surge. In open state the valve permits recirculation of fluid that is returned to the compressor via the compressor inlet 9, driven by the higher fluid pressure on the discharge side.
  • the valve 25 will be named an anti-surge valve 25 or ASV.
  • the state of the anti-surge valve 25 can be controlled by an anti-surge controller (ASC) 27.
  • the anti-surge controller 27 comprises control logic configured to process information on dedicated process parameters in order to generate an ASC command that determines the state of the anti-surge valve 25.
  • an ASC command is based on inputs received from pressure transmitters 28 and 29 monitoring the fluid pressure respectively at both suction and discharge of the compressor and based on input received from a flow transmitter 30 used to measure or to calculate the flow at the compressor inlet.
  • a flow transmitter 30 used to measure or to calculate the flow at the compressor inlet.
  • the temperature in the discharged fluid may be monitored and transmitted to the anti-surge controller 27.
  • the anti-surge valve 25 is closed or held in the closed state by a corresponding ASC command (or by the absence of an ASC command).
  • the anti-surge controller 27 produces an ASC command which results in opening of the anti-surge valve 25, thus permitting recirculation of process fluid in order to restore and maintain the relation between flow and pressure ratio which is required for stable compressor operation.
  • the anti-surge controller 27 may form an integrated part of the compression system control module 15 as illustrated in Fig. 1 .
  • the anti-surge controller 27 may alternatively be located topside in association with the main control system 14.
  • the anti-surge controller 27 can also alternatively be arranged as a separate module as illustrated in Fig. 3 .
  • the anti-surge controller 27 and its associated transmitters for flow, pressure or temperature may all be omitted in a method for anti-surge control described with reference to an embodiment of a subsea compression system100, illustrated in Fig. 2 .
  • the compression system 100 corresponds to the compression system 1 in respect of structural components and operation.
  • the AMB controller 24 is arranged to control the state of the anti-surge valve 25.
  • the AMB controller 24 comprises control logic configured to process information on compressor operation parameters in order to generate an AMB controller command which is communicated to the anti-surge valve 25 via communication line 31.
  • the compressor speed is adapted to the changed condition the compressor rotor will be subject to relative displacement and vibration in the form of axial and/or radial oscillation.
  • the magnitude of the displacement or vibration reflects the magnitude of change in the force or forces acting on the compressor rotor from the process load.
  • a rotor vibration can be recognized as low frequency (LF) harmonic oscillation that is superimposed on the position signal transmitted from the position sensors 18.
  • the amplitude of the LF harmonic oscillation reflects the magnitude in the forces acting on the compressor rotor.
  • the LF harmonic oscillation can be extracted from the position signal by commonly used signal processing techniques such as filtration/modulation/demodulation, e.g.
  • AMB controller command that controls the state of the anti-surge valve 25.
  • the amount of current that is required to maintain the rotor in the desired position can be an early indicator of an imminent surge condition.
  • variations in the current can be monitored to detect low frequency dynamic forces generated as the compressor approaches the surge zone.
  • Another alternative or supplementary input to the AMB controller can be the magnetic flux generated by the electromagnets. Variations in the magnetic flux can be detected through dedicated sensors, such as a Hall-effect sensor, or can be estimated by the AMB controller.
  • the anti-surge valve 25 is instantaneously reacting to a change in the compressor's operation that is processed in the AMB controller 24 and sent via communication line 31 as an AMB command which determines the state of the anti-surge valve 25.
  • the anti-surge valve 25 is actuated via an anti-surge valve switching actuator (VSA) 32.
  • VSA anti-surge valve switching actuator
  • the compression system 200 corresponds to the compression systems 1 and 100 in respect of structural components and operation.
  • valve switching actuator 32 is responsive to inputs transmitted from the anti-surge controller 27 via communication line 33.
  • valve switching actuator 32 is responsive also to inputs received from the AMB controller 24, transmitted via communication line 31.
  • the valve switching actuator 32 comprises an evaluation unit equipped with data processing capacity configured to evaluate the input received from the anti-surge controller 27 and from the AMB controller 24 respectively, to decide which input, the ASC command or the AMB controller command that shall be determinative for the state of the anti-surge valve 25.
  • the valve switching actuator 32 is arranged to overrule the ASC command under a certain condition at which the AMB controller command takes precedence over the ASC command.
  • the evaluation process performed by the valve switching actuator 32 is illustrated in the block diagrams of Figs. 4 and 5 .
  • Fig. 4 illustrates the parallel input of the AMB controller command and the ASC command to the valve switching actuator 32.
  • the valve switching actuator 32 generates a valve switching command based on the ASC command during stable operation.
  • the AMB controller command is repeatedly read and evaluated in a process loop through the steps of Fig. 5 , by which the valve switching actuator 32 is programmed and preset to permit the AMB controller command to take preference over the ASC command under the following condition: if the AMB controller command is found to be true, then the valve switching actuator 32 shifts the anti-surge valve 25 into open state (i.e. regardless of the valve status information contained in the ASC command), and if the AMB controller command is found to be false, the valve switching actuator 32 sets the valve position in accordance with the ASC command.
  • Fig. 6 illustrates the signal pathways for the process parameters which form the base for the AMB controller command.
  • the validity of the information contained in the AMB controller command is assessed in a process loop through the steps of Fig. 7 .
  • One input to the validity test of Fig. 7 is the AMB axial force, which is a value representing the axial force acting on the compressor rotor.
  • the AMB axial force can be calculated based on the rotor position data, the amount of current supplied to the electromagnets in the magnetic bearings and the amplitude in magnetic flux generated in the magnetic bearings.
  • the AMB axial force can be estimated by the amplitude of the position signal, the current signal, and the magnetic flux signal in the frequency domain especially at low frequency where the effect of the surge is noticeable.
  • the AMB controller command is accepted as a TRUE indicator of the operational status of the compressor if: the value representing the force acting on the compressor rotor exceeds a threshold value.
  • valve switching actuator 32 switches the anti-surge valve into the open state. If none of the above conditions is fulfilled, then the AMB controller command is considered as FALSE, in response to which the valve switching actuator 32 ignores the AMB controller generated command.
  • the axial force threshold value can be calculated or determined through running of the compressor in test or in calibration.
  • a set of threshold values for various rotor speeds can be compiled and memorized by the valve switching actuator 32 in the form of a compressor map while the operating point is approaching the surge area.
  • the LF harmonic content threshold value can be predetermined by running of the compressor in test or calibration.
  • a set of threshold values for various rotor speeds can be compiled and stored by the valve switching actuator 32 in the form of a compressor map while the operating point is approaching the surge area.
  • Actuation of the anti-surge valve 25 may be achieved through a quick opening function activated by the active magnetic bearing controller command. This function may be implemented by means of a power switch that controls the supply of power to the anti-surge valve.
  • the anti-surge valve 25 will be actuated on command from the anti-surge controller 27 based on the input from the flow and/or pressure and/or temperature transmitters 28, 29.
  • the AMB control can be expected to react just as rapid as the flow/pressure/temperature activated anti-surge control or even faster.
  • the embodiment 200 as shown in Fig. 3 , provides back up and redundancy in the anti-surge control of a subsea compression system.
  • the anti-surge valve 25 can be reset into its normally closed state once the processed flow has been reestablished or the risk for surge being removed or avoided. Reset of the anti-surge valve can follow an automatic procedure, relying for example on a valve body that is biased towards a closed position or a valve actuator biased towards a closing state, and can alternatively follow upon a closing command generated in a subsea control unit, such as the AMB controller, or from the topside control, e.g. Notwithstanding the obvious necessity to provide for reset of the anti-surge valve after an anti-surge operational mode, the invention is focused on the shift from stable operation towards surge which is the critical end of the process.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Control Of Positive-Displacement Air Blowers (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Control Of Non-Positive-Displacement Pumps (AREA)
  • Magnetic Bearings And Hydrostatic Bearings (AREA)
EP15716522.6A 2014-04-16 2015-04-14 Anti-surge control of a subsea compressor Active EP3132142B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL15716522T PL3132142T3 (pl) 2014-04-16 2015-04-14 Sterowanie przeciwdziałaniem pompowaniu sprężarki podmorskiej

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
NO20140516A NO337902B1 (no) 2014-04-16 2014-04-16 Styring av pumping i en undersjøisk kompressor
PCT/EP2015/058105 WO2015158734A1 (en) 2014-04-16 2015-04-14 Anti-surge control of a subsea compressor

Publications (2)

Publication Number Publication Date
EP3132142A1 EP3132142A1 (en) 2017-02-22
EP3132142B1 true EP3132142B1 (en) 2021-12-22

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EP15716522.6A Active EP3132142B1 (en) 2014-04-16 2015-04-14 Anti-surge control of a subsea compressor

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EP (1) EP3132142B1 (no)
AU (1) AU2015248926B2 (no)
BR (1) BR112016022609B1 (no)
NO (1) NO337902B1 (no)
PL (1) PL3132142T3 (no)
WO (1) WO2015158734A1 (no)

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DE102016225661A1 (de) * 2016-12-20 2018-06-21 Robert Bosch Gmbh Turboverdichtervorrichtung
GB2581467A (en) * 2018-08-31 2020-08-26 Equinor Energy As Combined system controller
US20200208509A1 (en) * 2018-12-28 2020-07-02 Upwing Energy, LLC Controlling downhole-type rotating machines
US11859628B2 (en) 2020-10-09 2024-01-02 Aker Solutions As Method of preventing damage to a pump
GB2599702A (en) * 2020-10-09 2022-04-13 Aker Solutions As Method of preventing damage to a pump
CN113847265A (zh) * 2021-10-29 2021-12-28 山信软件股份有限公司 一种稳定鼓风机转速的方法

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US2407925A (en) * 1943-03-27 1946-09-17 Chrysler Corp Apparatus for comparing pressures
US6092029A (en) * 1998-02-19 2000-07-18 Bently Nevada Corporation Method and apparatus for diagnosing and controlling rotating stall and surge in rotating machinery
NO323324B1 (no) * 2003-07-02 2007-03-19 Kvaerner Oilfield Prod As Fremgangsmate for regulering at trykket i en undervannskompressormodul
BE1017905A3 (nl) * 2007-10-29 2009-11-03 Atlas Copco Airpower Nv Werkwijze voor het vermijden van een onstabiele werkingstoestand bij centrifugaalcompressoren en centrifugaalcompressor voorzien van middelen waarmee zulke werkwijze automatisch wordt toegepast.
EP3141758B1 (en) * 2009-06-05 2019-08-28 Johnson Controls Technology Company Control system
CN103635697B (zh) * 2011-06-30 2016-08-17 开利公司 压缩机喘振检测

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EP3132142A1 (en) 2017-02-22
BR112016022609B1 (pt) 2022-08-16
WO2015158734A1 (en) 2015-10-22
PL3132142T3 (pl) 2022-02-07
BR112016022609A2 (no) 2017-08-15
NO337902B1 (no) 2016-07-04
NO20140516A1 (no) 2015-10-19
AU2015248926B2 (en) 2018-07-12
AU2015248926A1 (en) 2016-10-20

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