EP3482081B1 - Pumpschutz für verdichter unter feuchten gasbedingungen - Google Patents

Pumpschutz für verdichter unter feuchten gasbedingungen Download PDF

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Publication number
EP3482081B1
EP3482081B1 EP17734763.0A EP17734763A EP3482081B1 EP 3482081 B1 EP3482081 B1 EP 3482081B1 EP 17734763 A EP17734763 A EP 17734763A EP 3482081 B1 EP3482081 B1 EP 3482081B1
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Prior art keywords
compressor
gas
surge
suction side
suction
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EP17734763.0A
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English (en)
French (fr)
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EP3482081A1 (de
Inventor
Daniele Galeotti
David Rossi
Alessio CACITTI
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Nuovo Pignone Technologie SRL
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Nuovo Pignone Technologie SRL
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    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D31/00—Pumping liquids and elastic fluids at the same time
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2210/00—Working fluids
    • F05D2210/10—Kind or type
    • F05D2210/13—Kind or type mixed, e.g. two-phase fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2270/00—Control
    • F05D2270/01—Purpose of the control system
    • F05D2270/10—Purpose of the control system to cope with, or avoid, compressor flow instabilities
    • F05D2270/101—Compressor surge or stall

Definitions

  • Embodiments disclosed herein specifically relate to wet gas compressors, in particular centrifugal wet gas compressors, which process gas that can contain a liquid phase, e.g. heavy hydrocarbons, water or the like.
  • a liquid phase e.g. heavy hydrocarbons, water or the like.
  • WO 2012/007553 A1 discloses a method for composition-based compressor control where the compressor inlet gas may contain water and/or non-aqueous liquid. The method comprises measuring individual volume fractions of gas water and non-aqueous liquid and determining individual flow rates of a gas, water and non-aqueous liquid based on the measurements and controlling recirculation valve.
  • Centrifugal compressors have been designed to process a so-called wet gas, i.e. gas that can contain a certain percentage of a liquid phase.
  • Wet gas processing is often required in the oil and gas industry, where gas extracted from a well, such as a subsea well, can contain a liquid hydrocarbon phase, or water.
  • the presence and percentage amount of a liquid phase in a gas may affect the operation of the compressor and in particular may have an impact on the surge limit, which determines the range of safe operation of the compressor.
  • the liquid volume fraction in the gas flow at the suction side of the compressor is not known. Flowmeters capable of determining the liquid volume fraction are cumbersome and expensive and might not be suitable in certain applications in extreme environmental conditions.
  • a method for anti-surge protection of a compressor under wet gas conditions comprises a suction side and a delivery side.
  • An anti-surge system is arranged between the delivery side and the suction side of the compressor. The method comprises the following steps:
  • a wet gas compressor system comprising: a compressor having a suction side and a delivery side; an anti-surge control arrangement; a control unit, functionally coupled to the anti-surge control arrangement.
  • the control unit is configured and arranged for performing a method as above defined.
  • the compression ratio vs. corrected power diagram is a diagram wherein the compressor performances are represented as a function of the relationship between the compression ratio over the compressor and the corrected power of the compressor.
  • Fig.1 schematically illustrates a system 1 comprising a driver 3 and a load 5.
  • the load 5 includes a compressor 7, for instance a centrifugal compressor.
  • a shaft 9 drivingly connects the driver 3 to the load 5.
  • the driver 3 can be an electric motor, a gas turbine engine, a steam turbine or any other suitable driver.
  • the compressor 7 comprises a compressor suction side 7S and a compressor delivery side 7D.
  • the compressor 7 is further provided with an anti-surge system.
  • the anti-surge system is comprised of a line or duct 11 that is fluidly coupled to the delivery side 7D and to the suction side 7S.
  • the anti-surge system comprises an anti-surge valve 13 arranged on the anti-surge line 11.
  • the anti-surge valve 13 can be controllably opened to recirculate gas from the delivery side 7D to the suction side 7S of compressor 7, to prevent surge phenomena in the compressor, if the operating point of the compressor approaches a surge limit line.
  • a pressure transducer 15 and a temperature transducer 17 are arranged at the suction side 7S of compressor 7, to measure the gas suction pressure Ps and the gas suction temperature Ts of the gas at the suction side 7S.
  • a further pressure transducer 19 and a further temperature transducer 21 are arranged at the delivery side 7D of compressor 7, to measure the gas delivery pressure Pd and the gas delivery temperature Td.
  • the system 1 further comprises a control unit 23, which can be functionally coupled to the pressure and temperature transducers 15, 17, 19, 21 to collect measured values of the gas temperature and pressure at the delivery side 7D and suction side 7S of compressor 7.
  • the control unit 23 can be further functionally coupled to an actuator 13A configured and arranged for selectively opening and closing the anti-surge valve 13.
  • Reference number 25 generally designates storage memory resources for the control unit 23, which can store data useful for an anti-surge control of the compressor 7, as will be explained in greater detail herein after.
  • the control unit 23 can be configured and arranged for receiving further input information, such as data on the gas processed by compressor 7.
  • Block 27 schematically represents a data input, for instance providing information on the mean molar mass Mw of the gas being processed by compressor 7.
  • Reference number 29 schematically designates one or several further process parameter transducers, which provide additional information to the control unit 23, such as for instance the rotational speed N of compressor 7, the driving power W required to drive the compressor 7 into rotation and any additional information which may be useful or necessary for controlling the system 1.
  • Anti-surge control of the compressor 7 can be performed using the diagram of Fig.2 .
  • the compression ratio, or pressure ratio, PR of compressor 7 is plotted on the vertical axis of the diagram of Fig. 2 .
  • a dimensionless parameter depending upon the absorbed power, i.e. the power required to drive the compressor 7 into rotation, is plotted on the horizontal axis of the diagram of Fig. 2 .
  • the dimensionless parameter is a function of the actual driving power W, the suction pressure Ps and the suction temperature Ts of the gas, and can further depend upon parameters of the gas being processed and of characteristics of the compressor.
  • a suction limit line SLL can be plotted on the diagram of Fig. 2 , which allows anti-surge control of the compressor 7 without requiring knowledge of the actual liquid mass fraction (LMF) or liquid volume fraction (LVF) of the gas, i.e. the mass or volumetric percentage of liquid phase in the wet gas.
  • LMF liquid mass fraction
  • LVF liquid volume fraction
  • the SLL is a function of the gas conditions at the suction side 7S of compressor 7, i.e. of the suction temperature Ts and the suction pressure Ps. Additionally, the SLL is a function of the rotational speed of compressor 7, as well as of the mean molar mass Mw of the gas and of the compressibility Zs of the gas at the suction side 7S of compressor 7.
  • the chemical composition of the gas processed by compressor 7 usually varies very slowly during time and can be considered quasi-constant over relatively long time spans, e.g. 24 hours.
  • the chemical composition of the gas can be analyzed in-line by flowing a portion of gas through a gas chromatograph. In other embodiments, the gas composition can be analyzed offline, e.g. by taking a gas sample from the gas duct. Irrespective of how the gas is analyzed, the mean molar mass and the compressibility of the gas can be determined.
  • the remaining parameters can be detected by the transducers of system 1 during operation of the compressor 7.
  • the current SLL can be determined, based on features of the compressor, parameters of the gas being processed and operating parameters of the system 1, which are detected by the transducers functionally coupled to the control unit 23. Based upon the detected values of suction pressure (Ps), suction temperature (Ts), angular speed (N), mean molar mass (Mw) and compressibility (Zs), the control unit 33 calculates the current surge limit line SLL, based on store data, e.g. in table form, and/or by interpolation. The data for the calculation of the SLL can be stored in the storage memory resources 25. Additionally, based on the above mentioned data and on the actual power W currently absorbed by compressor 7, the corrected power Wcorr is calculated with formula (1).
  • the distance between the actual operating point and the calculated SLL is then determined. Based on said distance, an anti-surge control routine is started, if needed, to control the opening of the anti-surge valve.
  • the anti-surge valve can be controlled according to current art methods. In general, if the distance is less than a safety value, the anti-surge valve 13 is opened. If the distance is equal to or greater than a safety value, the anti-surge valve 13 is maintained in the closed condition.
  • the control method described so far is summarized in the flow chart of Fig.3 . The last block of the flow chart represents an anti-surge valve control.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Control Of Positive-Displacement Air Blowers (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Claims (9)

  1. Verfahren für eine Pumpschutzabsicherung eines Verdichters (7) unter Nassgasbedingungen, der Verdichter (7) umfassend eine Saugseite (7S), eine Abgabeseite (7D) und ein Pumpschutzsystem (11,13); das Verfahren umfassend:
    Berechnen einer Pumpgrenzlinie in einem Diagramm eines Verdichtungsverhältnisses im Vergleich zu einer korrigierten Leistung;
    Bestimmen eines Verdichterbetriebspunkts in dem Diagramm des Verdichtungsverhältnisses im Vergleich zu der korrigierten Leistung;
    Erfassen eines Abstands zwischen dem Betriebspunkt und der Pumpgrenzlinie; und
    Einwirken auf das Pumpschutzsystem (11,13) des Verdichters (7), falls der Abstand unter einem minimalen Sicherheitsabstand ist;
    wobei sich die Pumpgrenzlinie von einem ersten Endpunkt, der einem Trockengaszustand entspricht, zu einem zweiten Endpunkt erstreckt, der einem maximalen Flüssigkeitsgehalt entspricht.
  2. Verfahren nach Anspruch 1, wobei die korrigierte Leistung ein dimensionsloser Parameter ist, der von der Leistung abhängt, die erforderlich ist, um den Verdichter (7) anzutreiben.
  3. Verfahren nach einem oder mehreren der vorstehenden Ansprüche, ferner umfassend die Schritte:
    Bestimmen einer Drehzahl des Verdichters (7);
    Bestimmen einer Saugtemperatur und eines Saugdrucks des Gases an der Verdichtersaugseite;
    wobei die Pumpgrenzlinie basierend auf der Drehzahl, der Saugtemperatur und dem Saugdruck des Gases berechnet wird.
  4. Verfahren nach Anspruch 3, ferner umfassend die Schritte:
    Bestimmen einer mittleren Molmasse des Gases;
    Bestimmen der Verdichtbarkeit des Gases;
    wobei die Pumpgrenzlinie in Abhängigkeit von der mittleren Molmasse und der Verdichtbarkeit des Gases berechnet wird.
  5. Verfahren nach einem oder mehreren der vorstehenden Ansprüche, wobei die korrigierte Leistung ein dimensionsloser Parameter ist.
  6. Verfahren nach einem oder mehreren der vorstehenden Ansprüche, wobei die korrigierte Leistung von einer tatsächlichen Verdichterantriebsleistung, dem Gasdruck an der Verdichtersaugseite, der Gastemperatur an der Verdichtersaugseite und chemischen Parametern des Gases abhängig ist.
  7. Verfahren nach Anspruch 6, wobei die korrigierte Leistung wie folgt berechnet wird: W corr = W P s ∗ Z S RT S M w 0,5 ∗ K vs 1,5 ∗ ΠD 2 4
    Figure imgb0004
     wobei
    W die tatsächliche gemessene Leistung ist, die durch den Verdichter absorbiert wird;
    Ps, Ts der Gasdruck und die Temperatur an der Saugseite des Verdichters sind;
    Mw die mittlere Molmasse des Gases ist, das durch den Verdichter verarbeitet wird;
    Zs die Verdichtbarkeit des Gases an der Verdichtersaugseite ist;
    R die Gaskonstante ist;
    kvs der isenotrope Volumenexponent des Gases an der Verdichtersaugseite ist;
    D der Laufraddurchmesser ist.
  8. Verfahren nach einem oder mehreren der vorstehenden Ansprüche, wobei das Pumpschutzsystem ein Pumpschutzventil (13) umfasst, das geöffnet wird, wenn der Schritt des Einwirkens auf das Pumpschutzsystem durchgeführt wird, um Gas von der Abgabeseite zu der Saugseite des Verdichters umzuwälzen.
  9. Nassgasverdichtersystem (1), umfassend:
    einen Verdichter (7), der eine Saugseite (7S) und eine Abgabeseite (7D) aufweist;
    ein Pumpschutzsystem (11,13);
    eine Steuereinheit (23), die mit dem Pumpschutzsystem (11,13) funktionell gekoppelt ist;
    wobei die Steuereinheit (23) konfiguriert ist und zum Durchführen eines Verfahrens nach einem oder mehreren der vorstehenden Ansprüche angeordnet ist.
EP17734763.0A 2016-07-07 2017-07-06 Pumpschutz für verdichter unter feuchten gasbedingungen Active EP3482081B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
IT102016000070852A IT201600070852A1 (it) 2016-07-07 2016-07-07 Protezione anti-pompaggio di compressore in condizioni di gas umido
PCT/EP2017/066909 WO2018007509A1 (en) 2016-07-07 2017-07-06 Compressor anti-surge protection under wet gas conditions

Publications (2)

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EP3482081A1 EP3482081A1 (de) 2019-05-15
EP3482081B1 true EP3482081B1 (de) 2023-11-22

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US (1) US20190301478A1 (de)
EP (1) EP3482081B1 (de)
JP (1) JP6979977B2 (de)
KR (1) KR102371876B1 (de)
DK (1) DK3482081T3 (de)
IT (1) IT201600070852A1 (de)
WO (1) WO2018007509A1 (de)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT201600070842A1 (it) * 2016-07-07 2018-01-07 Nuovo Pignone Tecnologie Srl Metodo e sistema di controllo anti-pompaggio adattivo
US20180163736A1 (en) * 2016-12-09 2018-06-14 General Electric Company Systems and methods for operating a compression system
CN114725445B (zh) * 2022-03-25 2023-01-03 湖南大学 一种燃料电池空压机流量控制方法

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2325494A1 (de) * 2009-11-19 2011-05-25 General Electric Company Auf Drehmoment basierender Sensor und Steuerverfahren zur Veränderung von Gas-Flüssigkeits-Fraktionen von Fluiden für Turbomaschinen

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US5508943A (en) * 1994-04-07 1996-04-16 Compressor Controls Corporation Method and apparatus for measuring the distance of a turbocompressor's operating point to the surge limit interface
US5908462A (en) * 1996-12-06 1999-06-01 Compressor Controls Corporation Method and apparatus for antisurge control of turbocompressors having surge limit lines with small slopes
US6332336B1 (en) * 1999-02-26 2001-12-25 Compressor Controls Corporation Method and apparatus for maximizing the productivity of a natural gas liquids production plant
US6364602B1 (en) * 2000-01-06 2002-04-02 General Electric Company Method of air-flow measurement and active operating limit line management for compressor surge avoidance
NO333438B1 (no) * 2010-07-14 2013-06-03 Statoil Asa Fremgangsmate og apparat for sammensetningsbasert kompressorkontroll og ytelsesovervaking.
US9133850B2 (en) * 2011-01-13 2015-09-15 Energy Control Technologies, Inc. Method for preventing surge in a dynamic compressor using adaptive preventer control system and adaptive safety margin
NO337108B1 (no) * 2012-08-14 2016-01-25 Aker Subsea As Flerfase trykkforsterkningspumpe
ITFI20130064A1 (it) * 2013-03-26 2014-09-27 Nuovo Pignone Srl "methods and systems for controlling turbocompressors"
EP3037668B1 (de) * 2014-12-18 2018-12-05 Sulzer Management AG Betriebsverfahren für eine pumpe, insbesondere eine multiphasenpumpe sowie pumpe

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2325494A1 (de) * 2009-11-19 2011-05-25 General Electric Company Auf Drehmoment basierender Sensor und Steuerverfahren zur Veränderung von Gas-Flüssigkeits-Fraktionen von Fluiden für Turbomaschinen

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US20190301478A1 (en) 2019-10-03
JP6979977B2 (ja) 2021-12-15
WO2018007509A1 (en) 2018-01-11
KR102371876B1 (ko) 2022-03-08
IT201600070852A1 (it) 2018-01-07
EP3482081A1 (de) 2019-05-15
DK3482081T3 (da) 2024-01-29
JP2020500270A (ja) 2020-01-09
KR20190022818A (ko) 2019-03-06

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