EP0335105A2 - Procédé pour éviter le pompage d'un compresseur centrifuge par le contrôle d'échappement - Google Patents

Procédé pour éviter le pompage d'un compresseur centrifuge par le contrôle d'échappement Download PDF

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Publication number
EP0335105A2
EP0335105A2 EP89103056A EP89103056A EP0335105A2 EP 0335105 A2 EP0335105 A2 EP 0335105A2 EP 89103056 A EP89103056 A EP 89103056A EP 89103056 A EP89103056 A EP 89103056A EP 0335105 A2 EP0335105 A2 EP 0335105A2
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EP
European Patent Office
Prior art keywords
flow
blow
control
discharge flow
minimum
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
EP89103056A
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German (de)
English (en)
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EP0335105A3 (en
EP0335105B1 (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.)
Everllence SE
Original Assignee
MAN Gutehoffnungshutte GmbH
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Application filed by MAN Gutehoffnungshutte GmbH filed Critical MAN Gutehoffnungshutte GmbH
Publication of EP0335105A2 publication Critical patent/EP0335105A2/fr
Publication of EP0335105A3 publication Critical patent/EP0335105A3/de
Application granted granted Critical
Publication of EP0335105B1 publication Critical patent/EP0335105B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • 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

Definitions

  • the invention relates to a method for avoiding the pumping of a turbocompressor supplying a downstream process with a gaseous pressure medium by means of blow-off control, in which the intake volume flow and the compressor end pressure are continuously recorded and in which when the intake volume flow decreases to or below a still permissible depending on the compressor end pressure, minimum suction volume flow above the surge limit volume flow is ensured by opening at least one bias valve that the volume flow through the compressor is kept above its surge limit.
  • a method of the type mentioned is known from DE-AS 26 23 899.
  • a special type of amplification of the control difference of the blow-off control which is dependent on the intake volume flow and compressor end pressure, is provided, the type of amplification depending on the respective position of the operating point of the compressor.
  • the position of the working point of the compressor is usually defined by the coordinates of the intake lumen flow and compressor end pressure in the characteristic map formed by these.
  • the surge limit of the compressor can be represented in the map as a line, the surge limit line, which should not be exceeded by the operating point during operation of the compressor. Moves the working point due to z. B. a decrease in the intake volume flow to the surge line, the blow-off valve is opened if a blow line parallel to the blow line is exceeded. to increase the intake volume flow again until the operating point is sufficiently far away from the surge limit again.
  • the discharge flow can either be measured directly by a corresponding measuring device in a pressure line for the pressure medium that is led to the process, or in a simulation from parameters of the downstream process, such as, for B. the position of one or more valves and / or the pressure at one or more points in the process can be calculated.
  • the first method variant is particularly expedient if, for other reasons, a flow measuring device is already available at a suitable point, the measurement results of which can be used for the new method.
  • the calculation of the flow is to be preferred if a flow measuring device would have to be installed especially for the method. This avoids unnecessarily high investment costs. Regardless of the type of recording of the discharge flow, be it by measurement or by calculation, it can be obtained in both ways with sufficient accuracy for the process.
  • the discharge flow is measured as a mass flow, ie as a mass per unit of time, a conversion must still be carried out in order to arrive at the same units for the intake volume flow and the discharge flow.
  • the mass flow is above the density of the compressed hare with the volume flow in a fixed relationship and the density in turn is a function of the pressure.
  • a pressure measurement at the input of the process and a subsequent conversion are required to calculate the discharge flow as volume flow.
  • the just admissible minimum intake volume flow is a function of the compressor end pressure.
  • the same minimum flow value which is supplied by a common function generator as a function of the compressor end pressure, is used for the minimum intake volume flow and for the minimum discharge flow.
  • Another, somewhat more complex process variant provides, in order to enable greater accuracy and greater influence on the process, that for the minimum intake volume flow and for the minimum discharge flow, independently calculated minimum flow values, each supplied by a separate function generator, are used, the minimum intake volume flow as a function of the compressor end pressure and Minimum discharge flow is determined as a function of pressure at the discharge flow detection point near the entrance to the process.
  • a safety control is superimposed in the blow-off control method, which triggers a quick opening of the blow-off valve while bypassing the blow-off control when the safety limit volume flow, which is dependent on the compressor end pressure and lies between the minimum suction volume flow and the pump limit volume flow, is provided that when the discharge flow rate falls below the safety limit volume flow the safety controller is triggered.
  • the flow values recorded on the discharge side act both on the blow-off control and on the safety control.
  • the minimum flow values corresponding to the respective safety limit flow rate are used for the minimum discharge flow rate and that when the discharge flow rate falls below the minimum discharge flow rate or safety limit volume flow rate, the relief valve is opened quickly by the safety controller bypassing the blow-off control. Disruptions in the discharge flow only affect the safety control, but not the normal blow-off control. In practice, this sub-form of the method does not constitute a restriction on the pump reliability of the compressor, since the normal blow-off control, which is controlled by the intake volume flow, can react sufficiently quickly in the case of relatively small and / or slow changes or disturbances in the discharge flow.
  • the baffle flow through the blow-off valve is additionally detected and added to the discharge flow.
  • the blow-off flow rate is recorded either by a measurement in the blow-off line upstream and downstream of the blow-off valve or by a calculation which saves on a separate measuring device.
  • One possibility of the calculation is that the blow-off flow is calculated by a simulation calculation from the position of the blow-off valve and the pressure upstream of the blow-off valve. This requires a position indicator on the relief valve, which is often already available in practice for other reasons.
  • the blow-off flow can also be calculated from a control variable for the adjustment of the blow-off valve generated in the blow-off control by simulating the dynamic behavior of the blow-off valve and from the pressure in front of the blow-off valve.
  • a simulation of the dynamic behavior of the valve is no problem with the electronic data processing options available today.
  • the temperature of the medium flowing through the blow-off valve and / or the pressure behind the blow-off valve are additionally measured and included in the calculation of the blow-off flow.
  • further variables influencing the flow through the relief valve can also be recorded and included in the calculation.
  • the blow-off valve would be primarily controlled by the changes in the blow-off flow or the sum of this and the discharge flow. This causes the compressor to operate at an unnecessarily large distance from the surge limit.
  • the discharge flow rate or the sum of this and the blow-off flow rate can be entered before entering the regulation or safety control are multiplied by a predeterminable factor that is greater than 1.
  • a predeterminable constant can be added to the discharge flow rate or to the sum of this and the blow-off flow rate before entry into the regulation or safety controller. The result of this is that an undesirable increase in the safety distance from the surge limit only occurs if the error in the discharge flow rate determination is greater than the predetermined factor which, for. B. 1.1, or as the added size.
  • Another embodiment of the method provides that a correction quantity is added to the discharge flow or the sum of discharge flow and blow-off flow in an additional device with a large time constant, which is changed until the sum of discharge flow and blow-off flow corresponds exactly to the intake flow.
  • the z. B. can be realized by an integrator, it can be ensured that the compensating effect takes place so slowly that temporary dynamic imbalances between intake volume flow and discharge flow rate or the sum of this and the blow-off flow rate and between the associated control differences can pass unhindered.
  • the integrator can be limited to certain values, in particular negative values, which prevents the setting of an excessively large safety distance from the surge limit.
  • a further embodiment of the method provides that the values for the discharge flow or the sum of this and the blow-off flow are given as an input signal to a yielding reference, the reference essentially consisting of an integrator with an adjustable time constant, the output signal of which with this time constant follows the input signal, and the temporary difference between the input and output signal occurring after sudden changes in the input signal is used as a correction variable for a control difference formed in the normal exhaust control and formed from the intake volume flow and the minimum intake volume flow.
  • the control difference can be changed directly or by applying the correcting variable with the correct sign to the setpoint or actual value for the calculation of the control difference.
  • Such an earlier reaction is not necessary in the event of disturbances in the direction of an increase in the discharge flow, which is why this regulation is expediently designed to act only in the first-mentioned direction of decrease by means of a yielding reference.
  • FIG. 1 A sequence example of the method according to the invention is explained below with reference to a drawing.
  • the single figure of the drawing shows a schematic representation of a turbocompressor along with associated lines, valves and the like elements together with a control scheme of the method.
  • a turbocompressor 1 is shown, which is connected on the suction side to an intake line 10 and on the pressure side to an output line 11.
  • a blow-off line 20 branches off from the discharge line 11, into which a blow-off valve 2 is switched on.
  • a part of the gaseous medium conveyed into the discharge line 11 by the compressor 1 can be blown off into the atmosphere by the blow-off line 20 when the blow-off valve 2 is open.
  • the relief valve 2 is adjustable for this purpose by means of a valve actuation device 21.
  • a check valve 3 is inserted into it, as usual. After this check valve 3, the discharge line 11 leads to a process downstream of the compressor 1, which is to be supplied with the compressed gaseous medium.
  • a measuring device 4 is used in the intake line 10, which serves to measure the intake volume flow V A flowing through the line 10 to the compressor 1.
  • a further measuring device 5 is arranged in the discharge line 11, which serves to measure the compressor end pressure P E.
  • Another measuring device 6 is finally inserted into the discharge line 11 before the process downstream of the compressor 1. This measuring device 6 is used to measure the discharge flow Vp to the process, with a conversion to volume per unit of time possibly taking place via the density of the medium at the measuring point if the discharge flow is measured as mass flow, ie as mass per unit of time.
  • x d1 is defined as the difference between the minimum flow rate, here the minimum intake volume flow V Amin, and the intake volume flow V A.
  • the measured values for the discharge flow Vp are used to calculate a second control difference Xd2 , where x d2 is defined as the difference between the minimum flow , in this case the minimum discharge flow V pmin and the measured discharge flow Vp. ie that the minimum intake volume flow V Amin is equal to the minimum discharge flow V Pmin . Alternatively, a separate minimum delivery flow can also be calculated.
  • the two control differences x d1 and Xd2 are fed to a maximum value selection .
  • the larger of the two control difference values is selected and fed to the blow-off control as the control difference ⁇ d .
  • the deflection control calculates a manipulated variable y from the control difference ⁇ d supplied to it, which is applied to the already mentioned valve actuation device 21 for adjusting the relief valve 2 and causes a corresponding adjustment of the relief valve 2 there.

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  • Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Positive-Displacement Air Blowers (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Control Of Non-Positive-Displacement Pumps (AREA)
EP89103056A 1988-03-30 1989-02-22 Procédé pour éviter le pompage d'un compresseur centrifuge par le contrôle d'échappement Expired - Lifetime EP0335105B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3810717A DE3810717A1 (de) 1988-03-30 1988-03-30 Verfahren zur vermeidung des pumpens eines turboverdichters mittels abblaseregelung
DE3810717 1988-03-30

Publications (3)

Publication Number Publication Date
EP0335105A2 true EP0335105A2 (fr) 1989-10-04
EP0335105A3 EP0335105A3 (en) 1990-08-22
EP0335105B1 EP0335105B1 (fr) 1994-11-09

Family

ID=6351007

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89103056A Expired - Lifetime EP0335105B1 (fr) 1988-03-30 1989-02-22 Procédé pour éviter le pompage d'un compresseur centrifuge par le contrôle d'échappement

Country Status (5)

Country Link
US (1) US4948332A (fr)
EP (1) EP0335105B1 (fr)
JP (1) JPH01300093A (fr)
AT (1) ATE114021T1 (fr)
DE (2) DE3810717A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0661426A1 (fr) * 1993-12-28 1995-07-05 Hitachi, Ltd. Turbine à gaz et procédé de functionnement
EP1134422A2 (fr) 2000-03-14 2001-09-19 MAN Turbomaschinen GmbH, GHH BORSIG Procédé pour le contrôle de pompage d' un turbo-compresseur

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5195875A (en) * 1991-12-05 1993-03-23 Dresser-Rand Company Antisurge control system for compressors
US5306116A (en) * 1992-04-10 1994-04-26 Ingersoll-Rand Company Surge control and recovery for a centrifugal compressor
DE19528253C2 (de) * 1995-08-01 1997-10-16 Gutehoffnungshuette Man Verfahren und Vorrichtung zur Vermeidung von Reglerinstabilitäten bei Pumpgrenzregelungen beim Betrieb von Strömungsmaschinen mit Reglern hoher Prportionalverstärkung
DE19726547A1 (de) * 1997-06-23 1999-01-28 Babcock Bsh Gmbh Verfahren zur Bestimmung des Betriebspunktes eines Ventilators und Ventilator
DE19828368C2 (de) * 1998-06-26 2001-10-18 Man Turbomasch Ag Ghh Borsig Verfahren und Vorrichtung zum Betreiben von zwei- oder mehrstufigen Verdichtern
CN100557249C (zh) * 2006-11-08 2009-11-04 财团法人工业技术研究院 压缩机喘振的预判方法
EP2101240B1 (fr) * 2008-03-10 2013-06-26 Karl Morgenbesser Organe de régulation pour liquides
IT1402481B1 (it) * 2010-10-27 2013-09-13 Nuovo Pignone Spa Metodo e dispositivo che effettua una compensazione del tempo morto di anti-pompaggio basata su modello
JP6501380B2 (ja) * 2014-07-01 2019-04-17 三菱重工コンプレッサ株式会社 多段圧縮機システム、制御装置、異常判定方法及びプログラム
RU2016112469A (ru) * 2016-04-01 2017-10-04 Фишер-Роузмаунт Системз, Инк. Способы и устройство для обнаружения и предотвращения помпажа компрессора
KR101989588B1 (ko) 2018-11-27 2019-06-14 터보윈 주식회사 서지 영역에서의 운전이 가능한 터보 블로어
CN117704286B (zh) * 2023-12-25 2024-06-14 玉得气体有限责任公司 一种中低压氮压机配合控制方法

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Publication number Priority date Publication date Assignee Title
DE1107887B (de) * 1957-04-16 1961-05-31 Power Jets Res & Dev Ltd Regler zur Pumpverhuetung bei Stroemungsverdichtern
US3276674A (en) * 1963-03-06 1966-10-04 Shell Oil Co Method for preventing surging of compressors
DE1428066A1 (de) * 1963-08-30 1968-11-28 Continental Elektro Ind Ag Grenzmengenregelung an Turboverdichtern
US3994623A (en) * 1975-02-11 1976-11-30 Compressor Controls Corporation Method and apparatus for controlling a dynamic compressor
DE2623899C3 (de) * 1976-05-28 1989-06-08 MAN Gutehoffnungshütte GmbH, 4200 Oberhausen Verfahren zum Betreiben von Turboverdichtern in der Nähe der Pumpgrenze
US4139328A (en) * 1977-05-25 1979-02-13 Gutehoffnungshitte Sterkrade Ag Method of operating large turbo compressors
DE2735246C2 (de) * 1977-08-04 1985-07-18 Siemens AG, 1000 Berlin und 8000 München Regeleinrichtung für einen Turboverdichter
US4486142A (en) * 1977-12-01 1984-12-04 Naum Staroselsky Method of automatic limitation for a controlled variable in a multivariable system
DE3105376C2 (de) * 1981-02-14 1984-08-23 M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 4200 Oberhausen Verfahren zum Betreiben von Turboverdichtern
US4464720A (en) * 1982-02-12 1984-08-07 The Babcock & Wilcox Company Centrifugal compressor surge control system
US4560319A (en) * 1983-08-01 1985-12-24 MAN Maschinenfabrik Unternehmensbereich GHH Sterkrade Method and apparatus for controlling at least two parallel-connected turbocompressors
US4697980A (en) * 1984-08-20 1987-10-06 The Babcock & Wilcox Company Adaptive gain compressor surge control system
DE3540088A1 (de) * 1985-11-12 1987-05-14 Gutehoffnungshuette Man Verfahren zur erfassung von pumpstoessen an turbokompressoren
DE3540285A1 (de) * 1985-11-13 1987-05-14 Gutehoffnungshuette Man Verfahren und einrichtung zum regeln von turbokompressoren
DE3544821A1 (de) * 1985-12-18 1987-06-19 Gutehoffnungshuette Man Verfahren zum regeln von turbokompressoren zur vermeidung des pumpens
DE3544822A1 (de) * 1985-12-18 1987-06-19 Gutehoffnungshuette Man Verfahren zur pumpgrenzregelung von turbokomporessoren
DE3620614A1 (de) * 1986-06-20 1987-12-23 Gutehoffnungshuette Man Verfahren zum filtern eines verrauschten signals
US4781524A (en) * 1987-02-12 1988-11-01 Man Gutehoffnungshuette Gmbh Method and apparatus for detecting pressure surges in a turbo-compressor
JP2585324B2 (ja) * 1987-12-09 1997-02-26 株式会社日立製作所 ガスタービンの制御方法及びその装置

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0661426A1 (fr) * 1993-12-28 1995-07-05 Hitachi, Ltd. Turbine à gaz et procédé de functionnement
EP1134422A2 (fr) 2000-03-14 2001-09-19 MAN Turbomaschinen GmbH, GHH BORSIG Procédé pour le contrôle de pompage d' un turbo-compresseur
EP1134422A3 (fr) * 2000-03-14 2002-06-19 MAN Turbomaschinen GmbH, GHH BORSIG Procédé pour le contrôle de pompage d' un turbo-compresseur
US6551068B2 (en) 2000-03-14 2003-04-22 Man Turbomaschinen Ag Ghh Borsig Process for protecting a turbocompressor from operating in the unstable working range

Also Published As

Publication number Publication date
ATE114021T1 (de) 1994-11-15
EP0335105A3 (en) 1990-08-22
DE3810717C2 (fr) 1992-06-04
JPH01300093A (ja) 1989-12-04
US4948332A (en) 1990-08-14
DE3810717A1 (de) 1989-10-19
DE58908615D1 (de) 1994-12-15
EP0335105B1 (fr) 1994-11-09

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