EP1069314A1 - Commande d'une unité-compresseur - Google Patents

Commande d'une unité-compresseur Download PDF

Info

Publication number
EP1069314A1
EP1069314A1 EP99810642A EP99810642A EP1069314A1 EP 1069314 A1 EP1069314 A1 EP 1069314A1 EP 99810642 A EP99810642 A EP 99810642A EP 99810642 A EP99810642 A EP 99810642A EP 1069314 A1 EP1069314 A1 EP 1069314A1
Authority
EP
European Patent Office
Prior art keywords
compressor
valve
setpoint
value
total flow
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.)
Withdrawn
Application number
EP99810642A
Other languages
German (de)
English (en)
Inventor
Andrew Paice
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.)
ABB Research Ltd Switzerland
ABB Research Ltd Sweden
Original Assignee
ABB Research Ltd Switzerland
ABB Research Ltd Sweden
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 ABB Research Ltd Switzerland, ABB Research Ltd Sweden filed Critical ABB Research Ltd Switzerland
Priority to EP99810642A priority Critical patent/EP1069314A1/fr
Priority to US09/617,915 priority patent/US6406268B1/en
Publication of EP1069314A1 publication Critical patent/EP1069314A1/fr
Withdrawn legal-status Critical Current

Links

Images

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
    • 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 the field of control engineering. It relates relates to a method and a device for regulating a compressor unit according to the preamble of claims 1 and 7.
  • a turbo compressor is inherently stable in normal operation: due to and outlet pressure and parameters of the compressor Mass flow of a working fluid through the compressor.
  • This Flow which can be considered as a volume or mass flow, decreases with increasing pressure difference, so that the pressures and the Move flow to an equilibrium state.
  • Pumping limit limited The mass flow decreases with increasing outlet pressure to a certain minimum. After exceeding the surge limit the mass flow flows backwards through the compressor. Thereby the outlet pressure drops until the mass flow flows forward again.
  • This Cycle called pumping, repeats itself and can mechanically compress the compressor damage or destroy. So it's a job of a compressor controller in addition to a regulation of an outlet pressure or Flow to avoid pumping.
  • the return valve is opened before it is exceeded the surge limit opened.
  • a corresponding safety limit should be possible are far from the surge line.
  • the security limit is as close as possible to the Pumping limit set. This requires security precautions which add complexity of the control loops increase.
  • a combination of a compressor with a recirculation valve is as follows Called compressor unit.
  • a compressor unit which one Gas turbine supplied with gaseous fuel has high demands pressure control are sufficient. For example, in the event of abrupt changes in load the gas turbine and in the event of an associated change an outlet pressure of the compressor of a gas consumption, without a flame from the gas turbine extinguishing and without lines damaged by excessive pressures. In normal operation none Oscillations occur in gas production.
  • Gas turbine it is also possible for a compressor unit to have a predetermined one Mass flow must deliver. This is opposed to hydraulic systems regulation to a given volume flow of interest.
  • Axial or radial compressors are used to vary the flow rate equipped with adjustable guide lines.
  • Another way of varying the Flow rate uses a variable speed drive of the compressor. In both cases, the mass flow, with constant entry and exit conditions, from a leading row angle or from one Speed dependent.
  • a corresponding controller for a compressor unit controls at least two manipulated variables, for example a guide row angle and return valve.
  • the existing controller structures are complex, and have decoupled controllers for the two manipulated variables, which is a systematic Controller design mostly impossible. By switching between The dynamics of the controller and different operating states thus the compressor is unmanageable and therefore even more difficult to design and put into operation.
  • a parameter for one delivering total flow is determined, and based on this parameter by means of static functions, a first setpoint for a preliminary series or a Inlet valve or a speed of the compressor and a second setpoint generated for a return valve.
  • the total flow to be supplied is preferably a mass flow but also be a volume flow.
  • Parameters of the static functions are advantageously related to an operating state of the compressor adjusted.
  • a major advantage of the invention is that the controller dynamics are very simple and that this enables quick regulation. Through the simple controller dynamics also becomes the overall dynamics of the compressor unit no more complicated, and the scheme remains simple to design, commission and maintain.
  • FIG. 1 shows a compressor unit 10 to which a regulation according to the invention relates.
  • a working fluid for example air, a gas or a hydraulic oil
  • a mixer 11 from a generator or a store, in which the working fluid has an inlet pressure p 1 and an inlet temperature T 1 .
  • the working fluid passes from the mixer through an inlet 12 into a compressor 13.
  • the compressor 13 has a signal input for a first target value u 1 .
  • a map parameter of the compressor 13 is adjusted, for example via a subordinate control loop, for example a leading row angle or a position of an input valve or a speed of the compressor.
  • a compressor flow w C flows into a branch 15, in which the working fluid has an outlet pressure p 2 .
  • a total flow w T flows from the branch 15 to a consumer, and a return flow w R through a return flow line 16 and a controllable return valve 17 back into the mixer 11.
  • the return valve 17 has a signal input for a second setpoint u 2 . With this second setpoint, a valve lift of the return valve 17 is adjusted, for example via a subordinate control loop.
  • the working fluid arrives through the return valve 17 not to the compressor inlet but is in blown off the environment.
  • the return valve 17 is used as a blow-off valve designated.
  • the regulation according to the invention is as follows presented using a feedback valve 17, but is for both types of use of valves applicable.
  • FIG. 2 schematically shows a typical map of the compressor 13.
  • a pressure ratio p 2 / p 1 between the outlet and inlet pressure is plotted along an ordinate.
  • the compressor flow wc is plotted along an abscissa, which is considered to be a mass flow (for example in kg / second) for the following explanations. Wc this compressor flow is usually scaled by the inlet temperature T 1 and at a given operating condition T 0, p 0 normalized so that the same graph of the characteristic map for various inlet temperatures T can be used. 1
  • Characteristic curves denoted by u 1.1 to u 1.3 represent the behavior of the compressor for different values of the characteristic map parameter determined by u 1 .
  • a value of the compressor flow rate w C is obtained which lies on the line corresponding to u 1 . It can be seen that with an increase in the pressure ratio p 2 / p 1 , for example due to an increase in the outlet pressure p 2 , the compressor flow wc decreases. If the compressor flow wc falls below the surge limit, that is, the line labeled PG, the pumping described at the beginning occurs.
  • the surge limit PG is determined experimentally, for example during commissioning and / or theoretically.
  • a security limit SG is introduced for security reasons. A regulation should intervene when the compressor flow wc falls below the safety limit SG, so that the pump limit PG is guaranteed never to be fallen below.
  • FIG. 3 shows a block diagram of a control system according to the invention.
  • This includes the compressor unit 10 already described with its input and output sizes.
  • a value of a measurement of the outlet pressure p 2 of the compressor unit 10 leads, with a negative sign, together with an outlet pressure setpoint p 2S to a first summation node 21.
  • a difference or control difference formed in the first summation node 21 leads to a preferably dynamic controller 22 which, for example, is a PI - (Proportional-integral) controller, a PID (proportional-integral-differential) or a non-linear controller.
  • An output of the controller 22 has a value z and leads to the input of a static setpoint generator 23.
  • the method according to the invention functions as follows:
  • the first summation node 21 forms a control deviation p 2S -p 2 .
  • v * is a modified first static parameter and k is a second static parameter.
  • FIG. 4 shows, by way of example, the relationships described above between the characteristic variable z, the target values u 1 and u 2 and the total flow w T.
  • the setpoints u 1 and u 2 formed in the static setpoint generator 23 are transmitted to the compressor unit 10.
  • a map parameter of the compressor 13 is adjusted in the compressor unit 10, for example via a subordinate control loop, in particular a leading row angle or a position of an input valve or a speed of the compressor.
  • a characteristic curve of the compressor 13 in FIG. 2 shifts for increasing values of u 1 from that with u 1.1 to that with u 1.2 to the characteristic marked with u 1.3 .
  • This increase in u1 corresponds to an opening of the feed line or an opening of the inlet valve or an increase in the speed of the compressor 13.
  • the considerations and the control are also readily applicable to an adjustable input valve or a variable-speed compressor 13.
  • the valve stroke of the recirculation valve 17 is adjusted in the compressor unit 10, for example via a subordinate control loop.
  • An increase in u 2 corresponds to an opening of the return valve 17 and an increase in the return flow W R.
  • a total flow w T and an outlet pressure p 2 are established . If this outlet pressure p 2 is, for example, higher than the outlet pressure setpoint p 2S , the control difference becomes negative and the dynamic controller 22 leads to a decrease in the parameter z.
  • the resulting change in the setpoints u 1 and u 2 is explained with reference to FIG. 2:
  • the compressor is in a state labeled S1 in a normal operating range of the compressor, that is to say the compressor flow rate wc is greater than at a point on the safety limit SG with the same pressure ratio.
  • the total flow w T is equal to the compressor flow w c and is regulated by the first setpoint u 1 and adjustment of the preliminary line.
  • the decrease in z leads via u 1 to a closure of the pilot line and to a reduction in the total flow w T.
  • u 1 v * and thus the state of the compressor at point S2 remains at the safety limit.
  • the value of k is chosen such that a gradient of the total flow w T as a function of z remains at least approximately constant at the transition to the opening of the return valve 17, that is to say it is
  • the dashed lines indicate the course of the total flow w T if k is not selected as described above.
  • k is adapted to the operating state of the compressor by means of a compressor characteristic.
  • the controller according to the invention has the advantage that the essential controller dynamics can be determined by the dynamic controller 22 and that this controller acts on only one parameter z. This eliminates the problems of coordinating dynamic processes during design and operation with dynamic multivariable controllers. This is made possible by the inventive consideration and regulation of the compressor unit as a whole and by the static determination of the setpoints u 1 and u 2 from the individual parameter z.
  • the above equations for describing the compressor characteristics and the pump error are implicit in the compressor characteristics 24, 25 and correspond to a static model of the compressor behavior.
  • the equations are determined by measurements and / or theoretical analyzes. They are advantageously scaled, standardized and stored in tabular form.
  • U 1 and v are determined, for example, by numerically solving the equation for the pump error s E , or by calculating and tabulating solutions of the equation in advance.
  • a real compressor 13 will behave differently from the modeled, expected compressor characteristics.
  • the first static parameter v is corrected on the basis of a measurement, so that the transition between the regulation by the preliminary series and the regulation by the return valve 17 remains at the safety limit SG, and in particular not shifted towards the surge limit.
  • the compressor flow w C is selected as the measurement.
  • the modeled compressor flow w CM is determined according to the equation already shown above. The measured compressor flow w C is subtracted from this modeled compressor flow w CM in summation block 21.
  • K is a constant.
  • a non-linear and / or a dynamic dependence of v * on the difference w CM -w C is also used, for example.
  • a warning signal is advantageously output and the control is continued with a last measured value of w C. Since a relevant deviation of the real from the modeled compressor behavior develops over the course of days to weeks, this is not critical.
  • the total flow w T is specified instead of the outlet pressure p 2 .
  • the same structure as in FIG. 3 is used, but with different coefficients of the dynamic controller 22.
  • the regulated total flow W T is either a mass flow or a volume flow.
  • the dynamic controller 22 is a combined feedforward / feedback controller with p 2S and w TS as inputs, or a controller cascade for p 2 and w T.
  • Other controller variants are also possible, all of which are based on the idea of a common parameter for a map parameter and the feedback valve 17.
  • the regulation according to the invention becomes a regulation in a preferred variant of a radially acting gas compressor for supplying fuel to a Gas turbine used.
  • the first setpoint ui gives values for one adjustable front row.
  • This regulation of a gas compressor was in Simulations tested, the gas requirement of the gas turbine within 4 seconds decreased from 100% to 10%.
  • the regulation behaves at least just as good as conventional, much more complicated control structures.
  • control according to the invention it is used to control axial compressors, turbochargers, or to control the speed of variable-speed compressors via the first setpoint u 1 .

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Positive-Displacement Air Blowers (AREA)
EP99810642A 1999-07-16 1999-07-16 Commande d'une unité-compresseur Withdrawn EP1069314A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP99810642A EP1069314A1 (fr) 1999-07-16 1999-07-16 Commande d'une unité-compresseur
US09/617,915 US6406268B1 (en) 1999-07-16 2000-07-17 Control of a compressor unit

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP99810642A EP1069314A1 (fr) 1999-07-16 1999-07-16 Commande d'une unité-compresseur

Publications (1)

Publication Number Publication Date
EP1069314A1 true EP1069314A1 (fr) 2001-01-17

Family

ID=8242926

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99810642A Withdrawn EP1069314A1 (fr) 1999-07-16 1999-07-16 Commande d'une unité-compresseur

Country Status (2)

Country Link
US (1) US6406268B1 (fr)
EP (1) EP1069314A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010040734A1 (fr) * 2008-10-07 2010-04-15 Shell Internationale Research Maatschappij B.V. Procédé de commande d'un compresseur et son appareil
DE102010040503A1 (de) * 2010-09-09 2012-03-15 Siemens Aktiengesellschaft Verfahren zur Steuerung eines Verdichters
CN110878759A (zh) * 2018-09-06 2020-03-13 新特能源股份有限公司 一种高转速离心式压缩机防喘振控制方法

Families Citing this family (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10151032A1 (de) * 2001-10-16 2003-04-30 Siemens Ag Verfahren zur Optimierung des Betriebs mehrerer Verdichteraggregate einer Erdgasverdichtungsstation
US20050276702A1 (en) * 2004-06-10 2005-12-15 Reisinger Paul G Compressor inlet pressure control system
US7841825B2 (en) * 2006-10-26 2010-11-30 Industrial Technology Research Institute Method for predicting surge in compressor
BRPI0622194A2 (pt) * 2006-12-11 2012-01-03 Dytech Ensa S L aparelho egr para motor de combustço interna
US9568894B2 (en) * 2007-06-12 2017-02-14 Ford Global Technologies, Llc Method and control system for a compressor that is operable with a climate system
US20090140444A1 (en) * 2007-11-29 2009-06-04 Total Separation Solutions, Llc Compressed gas system useful for producing light weight drilling fluids
DE102008006739A1 (de) * 2008-01-30 2009-08-13 Daimler Ag Verdichtersystem für eine Brennstoffzellenanordnung, Brennstoffzellenanordnung und Verfahren zur Kontrolle
DE102008039407A1 (de) * 2008-08-22 2010-02-25 Daimler Ag Verfahren zum Betrieb eines Brennstoffzellensystems mit einer Brennstoffzelle und einem elektrisch antreibbaren Turbolader
US8291720B2 (en) * 2009-02-02 2012-10-23 Optimum Energy, Llc Sequencing of variable speed compressors in a chilled liquid cooling system for improved energy efficiency
DE102011105917A1 (de) * 2011-06-21 2012-12-27 GM Global Technology Operations LLC (n. d. Gesetzen des Staates Delaware) Verdichtervorrichtung für den Turbolader eines Kolbenmotors, insbesondere für den Einsatz in einem Kraftfahrzeug, und Verfahren zu dessen Betrieb
US10584645B2 (en) * 2014-07-31 2020-03-10 Mitsubishi Heavy Industries Compressor Corporation Compressor control device, compressor control system, and compressor control method
KR102488575B1 (ko) * 2016-03-11 2023-01-16 한화파워시스템 주식회사 압축기 제어 시스템 및 압축기의 제어 방법
CN106368975B (zh) * 2016-11-25 2017-12-01 沈阳鼓风机集团股份有限公司 一种pcl压缩机性能控制方法及装置
EP3818259A4 (fr) * 2018-07-02 2022-04-06 Cummins, Inc. Régulation de pompage de compresseur
JP7214613B2 (ja) * 2019-12-03 2023-01-30 株式会社神戸製鋼所 圧縮システムの制御方法、圧縮システム及び水素ステーション
US12044245B2 (en) * 2021-04-29 2024-07-23 Copeland Lp Mass flow interpolation systems and methods for dynamic compressors

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3979655A (en) * 1975-03-31 1976-09-07 Compressor Controls Corporation Control system for controlling a dynamic compressor
DE2739229A1 (de) * 1977-08-31 1979-03-15 Siemens Ag Regeleinrichtung fuer einen turboverdichter
US4807150A (en) * 1986-10-02 1989-02-21 Phillips Petroleum Company Constraint control for a compressor system
EP0368557A2 (fr) * 1988-11-07 1990-05-16 Eaton Corporation Système de compresseur comprenant un système de détection d'emballement du compresseur
EP0398436A1 (fr) * 1989-05-15 1990-11-22 Elliott Turbomachinery Company, Inc. Système de réglage de compresseur pour améliorer le refoulement minimal et pour diminuer le pompage
US5306116A (en) * 1992-04-10 1994-04-26 Ingersoll-Rand Company Surge control and recovery for a centrifugal compressor

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3979665A (en) * 1975-02-05 1976-09-07 Baxter Laboratories, Inc. Conductivity monitoring system
US4046490A (en) * 1975-12-01 1977-09-06 Compressor Controls Corporation Method and apparatus for antisurge protection of a dynamic compressor
US4971516A (en) * 1988-05-04 1990-11-20 Exxon Research & Engineering Company Surge control in compressors
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

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3979655A (en) * 1975-03-31 1976-09-07 Compressor Controls Corporation Control system for controlling a dynamic compressor
DE2739229A1 (de) * 1977-08-31 1979-03-15 Siemens Ag Regeleinrichtung fuer einen turboverdichter
US4807150A (en) * 1986-10-02 1989-02-21 Phillips Petroleum Company Constraint control for a compressor system
EP0368557A2 (fr) * 1988-11-07 1990-05-16 Eaton Corporation Système de compresseur comprenant un système de détection d'emballement du compresseur
EP0398436A1 (fr) * 1989-05-15 1990-11-22 Elliott Turbomachinery Company, Inc. Système de réglage de compresseur pour améliorer le refoulement minimal et pour diminuer le pompage
US5306116A (en) * 1992-04-10 1994-04-26 Ingersoll-Rand Company Surge control and recovery for a centrifugal compressor

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010040734A1 (fr) * 2008-10-07 2010-04-15 Shell Internationale Research Maatschappij B.V. Procédé de commande d'un compresseur et son appareil
US8840358B2 (en) 2008-10-07 2014-09-23 Shell Oil Company Method of controlling a compressor and apparatus therefor
DE102010040503A1 (de) * 2010-09-09 2012-03-15 Siemens Aktiengesellschaft Verfahren zur Steuerung eines Verdichters
WO2012032164A1 (fr) 2010-09-09 2012-03-15 Siemens Aktiengesellschaft Procéder pour commander un compresseur
DE102010040503B4 (de) * 2010-09-09 2012-05-10 Siemens Aktiengesellschaft Verfahren zur Steuerung eines Verdichters
CN103097737A (zh) * 2010-09-09 2013-05-08 西门子公司 用于控制压缩机的方法
CN103097737B (zh) * 2010-09-09 2015-06-03 西门子公司 用于控制压缩机的方法
CN110878759A (zh) * 2018-09-06 2020-03-13 新特能源股份有限公司 一种高转速离心式压缩机防喘振控制方法
CN110878759B (zh) * 2018-09-06 2021-01-22 新特能源股份有限公司 一种高转速离心式压缩机防喘振控制方法

Also Published As

Publication number Publication date
US6406268B1 (en) 2002-06-18

Similar Documents

Publication Publication Date Title
EP1069314A1 (fr) Commande d'une unité-compresseur
DE69727044T2 (de) Regelsystem zur überspannungsverhütung bei dynamischen kompressoren
EP1134422B1 (fr) Procédé pour le contrôle de pompage d' un turbo-compresseur
DE68910467T2 (de) Modus und Gerät zur Vermeidung des Pumpens in einem dynamischen Verdichter.
DE69728254T2 (de) Regelsystem für dynamische kompressoren zur verhinderung des wiederauftretens des pumpens
EP1592870B1 (fr) Procede pour faire fonctionner un ensemble turbine a gaz
DE69313529T2 (de) Lastverteilungsverfahren und Gerät für Steuerung eines Hauptgasparameters einer Verdichterstation mit mehrfachen Kreiselverdichter
DE3023550C2 (fr)
EP2033057B1 (fr) Dispositif et procédé pour réaliser un essai de fonction d'organe de réglage sur une turbomachine
EP1016787B1 (fr) Procédé d' opération d' un compresseur et système fonctionnant selon ce procédé
DE3105376C2 (de) Verfahren zum Betreiben von Turboverdichtern
CH661320A5 (de) Regelanordnung fuer eine dampfturbine mit zwischenueberhitzung und umleitstationen.
DE102010040503B4 (de) Verfahren zur Steuerung eines Verdichters
DE3040139A1 (de) Regelsystem fuer eine gasturbine
EP0335105B1 (fr) Procédé pour éviter le pompage d'un compresseur centrifuge par le contrôle d'échappement
DE2025528B2 (de) Regeleinrichtung für eine Dampfturbinen-Kraftanlage
DE2214338A1 (de) Drehmoment-Regelsystem für eine Gasturbine
CH621855A5 (en) Method for regulating turbo-compressors
DE3540284A1 (de) Einrichtung zum regeln eines turbokompressors zur verhinderung des pumpens
EP0334034B1 (fr) Procédé de commande pour éviter le pompage d'un compresseur centrifuge
EP0757180B1 (fr) Procédé et dispositif d'opération des turbomachines avec régulateurs à gain proportionnel élevé
DE3830805C2 (fr)
DE4316202C2 (de) Verfahren zur Überwachung der Pumpgrenze eines Turboverdichters mit Vorleitapparat und Nachleitapparat
EP0822332B1 (fr) Générateur hydraulique
EP3167196B1 (fr) Procédé de régulation de la vitesse de rotation de compresseurs cryogéniques connectés en série

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE

AX Request for extension of the european patent

Free format text: AL;LT;LV;MK;RO;SI

17P Request for examination filed

Effective date: 20010608

AKX Designation fees paid

Free format text: AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20041208