EP1016787A2 - Procédé d' opération d' un compresseur et système fonctionnant selon ce procédé - Google Patents

Procédé d' opération d' un compresseur et système fonctionnant selon ce procédé Download PDF

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Publication number
EP1016787A2
EP1016787A2 EP99121245A EP99121245A EP1016787A2 EP 1016787 A2 EP1016787 A2 EP 1016787A2 EP 99121245 A EP99121245 A EP 99121245A EP 99121245 A EP99121245 A EP 99121245A EP 1016787 A2 EP1016787 A2 EP 1016787A2
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EP
European Patent Office
Prior art keywords
compressor
gas
suction
consumer
pressure
Prior art date
Legal status (The legal status 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 status listed.)
Granted
Application number
EP99121245A
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German (de)
English (en)
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EP1016787A3 (fr
EP1016787B1 (fr
Inventor
Wilfried Dr.-Ing. Blotenberg
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
MAN Energy Solutions SE
Original Assignee
MAN Turbomaschinen AG GHH Borsig
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Application filed by MAN Turbomaschinen AG GHH Borsig filed Critical MAN Turbomaschinen AG GHH Borsig
Publication of EP1016787A2 publication Critical patent/EP1016787A2/fr
Publication of EP1016787A3 publication Critical patent/EP1016787A3/fr
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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
    • F04D27/0284—Conjoint control of two or more different functions

Definitions

  • the invention relates to a method for operating a compressor with downstream consumer with variable gas take-off according to the preamble of claim 1.
  • the invention also relates to a system that can be operated according to the method with a compressor and downstream consumer.
  • the Invention is preferably, but not exclusively, applicable with a fuel gas compressor system connected to a pipeline, which is a gas turbine with compressed fuel gas provided.
  • the compressor with at least three control loops.
  • Final pressure regulator usually acts on the guide vanes of the Compressor and / or on a speed adjustment device on.
  • a suction pressure regulator acts on the throttle element on the Compressor suction side.
  • a surge limit controller is also provided, the one on the outlet side with the suction side of the Compressor connecting bypass valve acts to low delivery rate of the compressor by blowing media a minimum flow rate from the pressure side to the suction side through the compressor.
  • control loops are in terms of their working points and their dynamic behavior to a normal value of the flow rate of the compressor and thus the gas flow rate on Compressor output designed. Occurs on the consumer side sudden change in the gas flow required, so the control loops are able to make such changes to follow the gas flow to some extent, but with a systemic sluggish timing that is quick Correction of changes or faults on the consumer side Gas withdrawal is insufficient and can also lead to that the control loops influence each other and in undesirable Interaction.
  • the invention has for its object a compressor to operate with downstream consumer so that its Regulation sufficiently fast to changes on the consumer side Gas removal can respond.
  • throttle element depending on the consumer side Controlled gas take-off preferably such that the throttle is proportional to a reduction of the gas flow through the consumer is that the pressure loss across the suction side throttle remains constant even with reduced flow. In order to will also have an undesirable interaction with the rest Control loops reduced to a minimum.
  • FIG. 1 An embodiment of the invention is based on the drawing explained in more detail.
  • the drawing shows schematically a flow and Control scheme of one connected to a gas pipeline Compressor with a downstream gas turbine.
  • the drawing shows a pipeline 1, in which combustible gas, especially natural gas.
  • combustible gas especially natural gas.
  • To the pipeline 1 is the suction side of a compressor 3 connected to the gas condensed. Via the outlet line 5 of the compressor the compressed combustible gas is fed to a gas turbine 7, the driving power by burning the compressed gas generated.
  • Throttle element 9 On the suction side of the compressor 3 is in the pipeline 1 Throttle element 9 arranged, the opening cross-section over an actuator 11 regulated by a suction pressure regulator 13 which is a control signal from a downstream of the throttle valve 9 arranged pressure sensor 15 receives the Pressure detected on the suction side of the compressor 3. Sensor 15, Regulator 13 and throttle element 9 form a suction pressure control circuit to keep the pressure on the suction side of the Compressor 3.
  • a pressure sensor 17 On the pressure-side outlet line 5 of the compressor 3 a pressure sensor 17 is arranged which measures the final pressure (outlet pressure) of the compressor 3 detected and a corresponding one Provides signal to a final pressure regulator 19. This creates an actuating signal for an actuator 21 for adjusting the Guide vanes 23 of the compressor and / or an actuating signal for an actuator 25 for changing the speed of the drive (not shown) of the compressor 3.
  • pressure sensor 17, Regulator 19 and actuator 21 and 25 form a final pressure control loop to keep the pressure on the outlet side constant the compressor 3.
  • the outlet line 5 of the compressor 3 is on the suction side the compressor via a blow-by line 27 with a Umlassventil 29 connected. This is via an actuator 31st controllable by a control signal from a pump limit controller 33 is controlled.
  • the surge limit controller 33 operates as a flow controller with a variable setpoint, the setpoint depending on the current delivery head (enthalpy difference) of the compressor 3 is performed.
  • the surge limit controller 33 receives signals for the suction side as input variables Pressure (from the pressure sensor 15) and the suction side Temperature (from a temperature sensor 14) and the outlet side Pressure (final pressure) from a pressure sensor 18 is detected, which of course with the pressure sensor 17th can be identical. From these input variables, the Pump limit controller 33, the enthalpy difference and those derived from it Setpoint.
  • the surge limit controller receives 33 as the input variable the actual value of the flow on the suction side from a flow sensor 16.
  • Gas turbine 7 At the inlet of the one connected to the compressor outlet line Gas turbine 7 is a fuel control valve (Throttle valve) 35, the actuator 37 of a fuel gas regulator 39 is controlled.
  • the fuel gas regulator 39 adjusts the fuel gas valve 35 so that exactly Amount of fuel gas flows into the combustion chamber of the gas turbine 7, those for generating the currently required turbine power is needed.
  • the fuel gas regulator 39 of the gas turbine 7 is primarily a speed controller that controls the speed of the gas turbine regulates to a predetermined setpoint. Often there are additional ones Protective functions integrated in the fuel gas controller, e.g. Protection against overheating, flow instability, underspeed and the same.
  • the control signal can also without being generated by the controller 39, directly from the position of the fuel gas valve 35 can be tapped.
  • Control signal is a via the control line 41
  • Link point 43 is supplied, where it with that of the suction pressure regulator 13 generated control signal for the suction-side throttle element 9 is linked.
  • the type of link can be one simple addition or multiplication, at least is a link with the same effect such that with increasing throttling of the fuel gas supply to the gas turbine 7 also the suction-side throttle element 9 is increasingly throttled.
  • the node 43 can be a be connected upstream non-linear member 45, which a non-linear computing element and / or a non-linear amplifying element can be and that over the line 41 Change control point 43 supplied control signal in this way can compensate for nonlinearities in the system.
  • the system according to the embodiment works as follows.
  • the controllers 13, 19, 33, 39 are at one design point designed, in which the pressure in the pipeline 1 the desired or the required suction pressure of the compressor 3, the compressor 3 is operated at the nominal speed and the guide vanes are in the nominal position.
  • the Throttle body 9 on the suction side is open in the nominal position.
  • the fuel control valve 37 at the inlet of the gas turbine 7 is also in the nominal position, which the Nominal power of the gas turbine corresponds. Because pressure fluctuations in pipeline 1 are relatively slow Regulating these fluctuations provided regulators 13 and 19 designed for a relatively slow time constant.
  • the delivery head must of the compressor 3 can be reduced so that the final pressure is constant is held.
  • the final pressure regulator 19 via the actuators 21 or 25 the position of the guide vanes 22 towards a more closed position changed and / or the speed of the compressor 3 lowered.
  • the differential pressure drops over the throttle element on the suction side 9, so that this close to the appropriate extent got to.
  • the delivery amount due to physical limits of the compressor 3 cannot be reduced arbitrarily, must also be above a certain pressure in pipeline 1 the suction pressure regulator 13 intervene and the suction side Throttle throttle body 9 so far that the compressor inlet pressure again corresponds to the nominal value.
  • the Link point 43 is assigned by the suction pressure regulator 13 generated control signal for the throttle element 9 (expressed in% of the total closing stroke from the fully open position out) with the control signal generated by the controller 39 for the Throttling the fuel gas control valve 35 (also expressed in% of the total closing stroke from the fully open position out) multiplied.
  • the result of the multiplication is an additional control signal that in node 43 is added to the signal of the suction pressure regulator 13 and one additional throttling of the suction-side throttling element 9 causes.
  • One or more nonlinear elements are to compensate for Nonlinearities of the system are provided.
  • the suction pressure regulator 13 is relative in its actuating behavior set sluggishly and with its parameters to the dynamic adapted to the pipeline 1. His slowly changing manipulated variable is in the node 43 from the position of Fuel gas control valve 35 derived control command added.
  • the system can work as follows. It is assumed that the overall system is close to the nominal operating point. Fuel gas control valve 35 and guide vanes 23 of the compressor are located yourself in the nominal position. The compressor 3 is at nominal speed operated. It is also assumed that in the pipeline 1 there is a relatively high pressure, and that is why the throttle element 9 throttled by the suction pressure regulator 13 by 10% is, i.e. that an opening cross-section 90% of full opening cross section.
  • the fuel gas control valve 35 is e.g. 30% throttled, i.e. after regulating the flow, its opening cross-section is 70% of the full opening cross-section.
  • the corresponding command from the fuel gas regulator 39 for the control valve 35 is the arithmetic circuit 47 fed and there with the signal from the controller 13 multiplied for the 10% throttling of the throttle body 9.
  • the result is an additional control signal for an additional closure of the throttle element 9 by more 3% (10% existing throttle position of the throttle element 9 multiplied by 30% load change of the turbine 7).
  • the throttle body 9 goes immediately from the 90% opening position in the 87% opening position.
EP99121245A 1998-12-29 1999-10-25 Procédé d' opération d' un compresseur et système fonctionnant selon ce procédé Expired - Lifetime EP1016787B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19860639A DE19860639A1 (de) 1998-12-29 1998-12-29 Verfahren zum Betreiben eines Kompressors mit nachgeschaltetem Verbraucher, und nach dem Verfahren arbeitende Anlage
DE19860639 1998-12-29

Publications (3)

Publication Number Publication Date
EP1016787A2 true EP1016787A2 (fr) 2000-07-05
EP1016787A3 EP1016787A3 (fr) 2001-02-21
EP1016787B1 EP1016787B1 (fr) 2003-12-10

Family

ID=7893065

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EP99121245A Expired - Lifetime EP1016787B1 (fr) 1998-12-29 1999-10-25 Procédé d' opération d' un compresseur et système fonctionnant selon ce procédé

Country Status (3)

Country Link
US (1) US6293766B1 (fr)
EP (1) EP1016787B1 (fr)
DE (2) DE19860639A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1635066A2 (fr) 2004-09-09 2006-03-15 ALSTOM Technology Ltd Installation d'alimentation en gaz et procédé d'utilisation associé pour une turbine à gaz
EP2530329A1 (fr) * 2011-05-30 2012-12-05 Siemens Aktiengesellschaft Système de collecte de gaz d'un champ de gaz comprenant un compresseur haute pression
WO2019162872A1 (fr) * 2018-02-23 2019-08-29 Atlas Copco Airpower, Naamloze Vennootschap Procédé d'actionnement d'un système de compresseur et système de compresseur
CN110195715A (zh) * 2019-04-19 2019-09-03 中国神华能源股份有限公司 机械设备的可调导叶的控制方法、装置以及机械设备

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10012380A1 (de) * 2000-03-14 2001-09-20 Man Turbomasch Ag Ghh Borsig Verfahren zum Schutz eines Turbokompressors vor Betrieb im instabilen Arbeitsbereich
US6622489B1 (en) * 2000-10-25 2003-09-23 Hybrid Power Generation Systems, Llc Integrated gas booster modulation control method
JP3854556B2 (ja) * 2002-09-11 2006-12-06 三菱重工業株式会社 ガスタービンプラント制御機構
EP2304358A2 (fr) * 2008-07-29 2011-04-06 Shell Internationale Research Maatschappij B.V. Procédé et appareil de commande d'un compresseur et procédé de refroidissement d'un flux d'hydrocarbure
BE1019299A3 (nl) 2010-04-20 2012-05-08 Atlas Copco Airpower Nv Wekwijze voor het aansturen van een compressor.
RU2504693C1 (ru) * 2012-06-04 2014-01-20 Федеральное государственное бюджетное образовательное учреждение высшего профессионального образования "Национальный минерально-сырьевой университет "Горный" Электроприводная перекачивающая станция на морской платформе
DE102013102879B4 (de) * 2013-03-21 2019-02-07 Gpi Gesellschaft Für Prüfstanduntersuchungen Und Ingenieurdienstleistungen Mbh Kompressor mit Anpassung der Gaseintrittstemperatur und Verfahren zum Betreiben dieses Kompressors
KR102488575B1 (ko) * 2016-03-11 2023-01-16 한화파워시스템 주식회사 압축기 제어 시스템 및 압축기의 제어 방법
RU178571U1 (ru) * 2016-09-22 2018-04-11 Открытое акционерное общество "Севернефтегазпром" Приспособление для установки сменной проточной части крышки компрессора газоперекачивающего агрегата
JP6623318B1 (ja) * 2019-05-13 2019-12-18 三菱日立パワーシステムズ株式会社 燃料ガス供給装置および方法
CN115618652B (zh) * 2022-11-28 2023-03-10 成都秦川物联网科技股份有限公司 智慧燃气压缩机运行优化方法、物联网系统、装置及介质
CN116221191B (zh) * 2023-05-06 2023-08-01 西门子能源有限公司 控制流体压缩系统的方法

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CH397135A (de) * 1960-01-27 1965-08-15 Gutehoffnungshuette Sterkrade Einrichtung zum Regeln von Kreiselverdichtern
US4212599A (en) * 1977-08-20 1980-07-15 Gutehoffnungshutte Sterkrade Aktiengesellschaft Method and device for regulating the output quantity of compressed medium of single and multi-stage screw and turbo compressor systems
US4273514A (en) * 1978-10-06 1981-06-16 Ferakarn Limited Waste gas recovery systems
GB2115110A (en) * 1982-01-21 1983-09-01 Hoerbiger Ventilwerke Ag Improvements in or relating to arrangements for controlling starting of screw-type compressor

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US4212599A (en) * 1977-08-20 1980-07-15 Gutehoffnungshutte Sterkrade Aktiengesellschaft Method and device for regulating the output quantity of compressed medium of single and multi-stage screw and turbo compressor systems
US4273514A (en) * 1978-10-06 1981-06-16 Ferakarn Limited Waste gas recovery systems
GB2115110A (en) * 1982-01-21 1983-09-01 Hoerbiger Ventilwerke Ag Improvements in or relating to arrangements for controlling starting of screw-type compressor

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1635066A2 (fr) 2004-09-09 2006-03-15 ALSTOM Technology Ltd Installation d'alimentation en gaz et procédé d'utilisation associé pour une turbine à gaz
US7497668B2 (en) 2004-09-09 2009-03-03 Alstom Technology Limited Gas supply arrangement and associated method, particularly for a gas turbine
EP1635066A3 (fr) * 2004-09-09 2012-10-31 Alstom Technology Ltd Installation d'alimentation en gaz et procédé d'utilisation associé pour une turbine à gaz
EP2530329A1 (fr) * 2011-05-30 2012-12-05 Siemens Aktiengesellschaft Système de collecte de gaz d'un champ de gaz comprenant un compresseur haute pression
WO2012163715A3 (fr) * 2011-05-30 2013-05-10 Siemens Aktiengesellschaft Système de collecte de gaz depuis un champ de gaz comprenant un compresseur haute-pression à efficacité élevée
US20140178208A1 (en) * 2011-05-30 2014-06-26 Bob Okhuijsen System for gathering gas from a gas field comprising a high efficient high pressure compressor
WO2019162872A1 (fr) * 2018-02-23 2019-08-29 Atlas Copco Airpower, Naamloze Vennootschap Procédé d'actionnement d'un système de compresseur et système de compresseur
BE1026036B1 (nl) * 2018-02-23 2019-09-20 Atlas Copco Airpower Nv Werkwijze voor het aansturen van een compressorinrichting en compressorinrichting
CN111699321A (zh) * 2018-02-23 2020-09-22 阿特拉斯·科普柯空气动力股份有限公司 用于致动压缩机系统的方法以及压缩机系统
CN111699321B (zh) * 2018-02-23 2022-03-01 阿特拉斯·科普柯空气动力股份有限公司 用于致动压缩机系统的方法以及压缩机系统
CN110195715A (zh) * 2019-04-19 2019-09-03 中国神华能源股份有限公司 机械设备的可调导叶的控制方法、装置以及机械设备

Also Published As

Publication number Publication date
EP1016787A3 (fr) 2001-02-21
DE19860639A1 (de) 2000-07-06
US6293766B1 (en) 2001-09-25
DE59908016D1 (de) 2004-01-22
EP1016787B1 (fr) 2003-12-10

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