EP0336095B1 - Regelverfahren zum Vermeiden des Pumpens eines Turboverdichters mittels bedarfsweisen Abblasens - Google Patents

Regelverfahren zum Vermeiden des Pumpens eines Turboverdichters mittels bedarfsweisen Abblasens Download PDF

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Publication number
EP0336095B1
EP0336095B1 EP89103134A EP89103134A EP0336095B1 EP 0336095 B1 EP0336095 B1 EP 0336095B1 EP 89103134 A EP89103134 A EP 89103134A EP 89103134 A EP89103134 A EP 89103134A EP 0336095 B1 EP0336095 B1 EP 0336095B1
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EP
European Patent Office
Prior art keywords
controller
control
valve
variable
control difference
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.)
Expired - Lifetime
Application number
EP89103134A
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German (de)
English (en)
French (fr)
Other versions
EP0336095A2 (de
EP0336095A3 (en
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 Gutehoffnungshutte GmbH
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Publication date
Application filed by MAN Gutehoffnungshutte GmbH filed Critical MAN Gutehoffnungshutte GmbH
Priority to AT89103134T priority Critical patent/ATE82045T1/de
Publication of EP0336095A2 publication Critical patent/EP0336095A2/de
Publication of EP0336095A3 publication Critical patent/EP0336095A3/de
Application granted granted Critical
Publication of EP0336095B1 publication Critical patent/EP0336095B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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 control method for avoiding the pumping of a turbocompressor by means of blowing as required, the flow to the compressor and the compressor end pressure being continuously recorded and used to calculate a first control difference, which is given as an input variable to a controller which is used as an output variable for a control variable controlled adjustment of the relief valve to this, and wherein a safety control triggers a rapid opening of the relief valve in the event of large and / or rapid disturbances overwhelming the limited reaction speed of the regulator.
  • the normal control by the controller is deliberately limited in the reaction speed or rate of change of the manipulated variable for the blow-off valve in order to obtain stable, vibration-free control and to avoid constant back and forth movement of the blow-off valve.
  • This interpretation of the regulation makes it necessary that the safety control mentioned is also provided, which opens the blow-off valve quickly in the event of rapid and / or major malfunctions.
  • the measured values are used to monitor whether the operating point of the compressor is in the compressor map exceeds a safety line running parallel to the surge limit. If this is the case, actuating a switching valve triggers a complete quick opening of the relief valve, which is caused by spring force.
  • a method of the type mentioned at the outset which is characterized in that a second control difference (x '), which may indicate the need for a quick opening of the relief valve, from the measured values or the first control difference (x) and predefinable target values is calculated and supplied to a limit value step and that this limit value step outputs a quick opening variable (z) on the output side when a limit value which can be predetermined therein is exceeded by the second control difference (x ′), which is applied to the controller (4) and in this valve actuation by means of additive superimposition Changes in the valve control variable (y) in the opening direction are generated with an increased rate of change.
  • the new method has the advantage that it can be used in addition to known control methods and thereby increases the limited reaction speed inherent in the adjustment of the relief valve, if necessary, so that timely opening of the relief valve is ensured even in the event of large and / or rapid faults is.
  • the quick opening variable is only pending as long as the second control difference exceeds the associated limit value, the quick opening variable is no longer output after the second control difference has dropped below the limit value.
  • the adjustment of the relief valve is again carried out solely under the influence of the slower normal regulation.
  • a quick opening movement of the relief valve is therefore only just as far and as long as necessary to avoid pumping the compressor.
  • no special technical additional devices are required to carry out the method, since it makes use of the existing means for adjusting the relief valve.
  • the actual movement speed of the working point in the characteristic map is calculated from the control difference (x) representing the location of the compressor operating point in the compressor map and that this is based on this actual speed and a target speed assigned to it a specifiable position-speed function, when reaching a pumping can just be prevented by the operating point, the difference is formed and that this difference is used as a second control difference (x ').
  • This ensures that, in addition to the distance of the compressor operating point from the surge limit, its speed of approach to the surge limit in the compressor map is also used for the decision on the rapid opening of the relief valve.
  • the definable The position-speed function represents a curve, the course of which is to be selected such that if the curve is only slightly exceeded, the compressor does not pump.
  • This curve is reached, the rapid opening of the blow-off valve is triggered immediately, but until the blow-off valve reacts and its opening has an influence on the position of the working point, the working point will still exceed the curve by a certain amount.
  • a sufficient safety margin for the surge limit is maintained when specifying the curve, but this can be relatively small.
  • the method provides that the quick opening variable is output in the form of a time-dependent increasing or decreasing ramp function, step function, step function or pulse sequence function.
  • the selection of the function depends on the individual requirements, in particular on the mode of operation of the relief valve and its associated actuating device.
  • the slope of the function is expediently adapted to the maximum actuating speed of the relief valve, which is determined by technical properties, and which is always greater than the maximum rate of change of the controller with regard to the valve actuating variable.
  • Figures 1 to 3 of the drawing show three versions of the method in the form of control schemes.
  • FIG. 1 shows a turbocompressor 1 with an intake line 10 and an output line 11, in which a non-return valve 13 is installed.
  • a blow-off line 12 branches off from the discharge line 11 in front of the non-return flap 13, into which a blow-off valve 2 is switched on.
  • the flow of the medium to be compressed e.g. B. air detected.
  • the compressor end pressure is continuously detected by a pressure meter 32 connected to the discharge line 11.
  • a function transmitter 33 connected downstream of the pressure meter, the minimum flow value that is just permissible for this is determined as a function of the pressure determined.
  • This minimum flow value which is output by the function generator 33, serves as the desired value, while the flow value determined by the flow meter 31 serves as the actual value.
  • This actual value is supplied with a negative sign to an adder 34, in which a first control difference x is defined as the difference between the setpoint and the actual value.
  • the control difference x is fed to the input of a proportional-integral controller (PI controller) 4, which in turn emits a manipulated variable y at its output, which is fed to the relief valve 2 and causes its regulated adjustment.
  • PI controller proportional-integral controller
  • the first control difference x is additionally fed to a safety controller 5.
  • the speed of change of the control difference x ie the speed of movement of the working point
  • a speedometer 51 of the compressor 1 calculated in its map.
  • the control difference x is fed to a further function generator 52, in which a predetermined position-speed function is stored.
  • This function represents a curve when it can be just prevented from being pumped by the operating point of the compressor 1. At the same time, this means that as long as the operating point has not yet reached the curve, intervention by the safety controller to protect the compressor 1 is not yet necessary.
  • the curve itself designates the points at which a valve opening must begin at the latest in order to be able to prevent the surge limit from being reached.
  • the shape of this curve and its distance from the surge line are largely determined by the properties of the relief valve, such as actuating behavior, non-linearities and the like.
  • the function generator 52 On the output side, the function generator 52 in each case outputs the desired speed value belonging to the control difference x that has been given up. In a further adder 53, the difference is formed from the actual speed emitted by the speedometer 51 and the desired speed emitted by the function generator 52 and provided with a negative sign. This is fed as a second control difference x 'to a limit value stage 54.
  • This limit value level 54 compares the given second control difference x 'with a predetermined limit value stored in the limit value level 54, which corresponds to the previously mentioned safety margin. If the second control difference x 'exceeds this limit value, the limit value stage 54 outputs a so-called quick opening variable z on the output side.
  • the quick opening variable z is generated by a function generator 55, which in this case emits a ramp function that rises continuously as a function of time.
  • the function generator 55 can be designed in such a way that the slope of the function that is emitted is exactly the same depending on the time changes that the relief valve 2 is adjusted with its maximum adjustment speed.
  • the position of the relief valve 2 can be given as a feedback variable to the function generator 55, thereby ensuring that the actuating speed of the relief valve is always adapted to the current valve position.
  • This quick opening variable z is given to the output of the PI controller 4 and added there in an adder 43 to the manipulated variable y generated by the PI controller 4 to form a changed manipulated variable y. Since by definition the blow-off valve 2 opens in the present example (and also in the examples to be described below) when the manipulated variable y becomes smaller, the addition of the quick-opening variable z to the manipulated variable y results in a rapid adjustment of the relief valve 2 in the opening direction.
  • the steepness of the ramp function of the function generator 55 is adapted to the maximum possible actuating speed of the relief valve 2.
  • the rate of change thus achieved for the manipulated variable y is greater than the rate of change for the manipulated variable y that can be generated by the PI controller 4 alone.
  • the output of the limit value stage 54 can also be passed directly to the adder 43, ie the function generator 55 can be omitted here.
  • the size of the output signal of the limit value stage 54 must be such that it causes such a large change in the manipulated variable y during the addition in the adder 43 that the relief valve 2 receives a command to open it completely.
  • the relief valve 2 follows the manipulated variable y as quickly as possible. This variant of the method is particularly simple, however, there may be a temporary difference between the manipulated variable y and the current valve position.
  • Figure 2 of the drawing also shows the turbocompressor 1 with intake line 10 and discharge line 11, in which the non-return valve 13 is inserted again.
  • the blow-off line 12 branches off from the discharge line 11 with the blow-off valve 2 switched on.
  • the first control difference x is also determined here in the manner already described with reference to FIG. 1 by means of measured values and setpoints, which are determined using a flow meter 31, a pressure meter 32 and a function transmitter 33 with a downstream adder 34.
  • the controller used here is a PI controller 4.
  • the proportional part 41 and the integral part 42 of the PI controller 4 are followed by an adder 43, in which the outputs of the proportional part 41 and the integral part 42 are added to form the manipulated variable y for the adjustment of the relief valve 2.
  • FIG. 3 shows a third advantageous embodiment of the method, the compressor 1 with the intake line 10 and the discharge line 11 and the non-return flap 13 inserted therein and the blow-off line 12 branching off the line 11 with the blow-off valve 2 also shown in the illustration.
  • the first control difference x is determined here in the same way as described above with reference to FIGS. 1 and 2.
  • the determination of the quick opening variable z by the safety controller 5 also takes place here exactly in the manner described with reference to FIG. 2.
  • a PI controller 4 which has a proportional part 41 and an integral part 42, is again used as the controller.
  • the proportional part 41 is again fed only the first control difference x, while the integral part 42 receives both the control difference x and the quick opening variable z on the input side.
  • the integral part 42 of the PI controller 4 has two separate integrator inputs 42 'and 42 ′.
  • the first input 42 ' is assigned the first control difference x, while the second input 42 ⁇ the quick opening variable z is applied.
  • This version has the advantage that the two inputs 42 'and 42 ⁇ different integration behavior, for. B. different integration time constants can be assigned.
  • the output of the integral part 42 can be influenced without influencing depending on the quick opening variable z be influenced by the first control difference x in an effective manner.

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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)
  • Control Of Positive-Displacement Pumps (AREA)
  • Non-Positive Displacement Air Blowers (AREA)
EP89103134A 1988-04-02 1989-02-23 Regelverfahren zum Vermeiden des Pumpens eines Turboverdichters mittels bedarfsweisen Abblasens Expired - Lifetime EP0336095B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT89103134T ATE82045T1 (de) 1988-04-02 1989-02-23 Regelverfahren zum vermeiden des pumpens eines turboverdichters mittels bedarfsweisen abblasens.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3811232A DE3811232A1 (de) 1988-04-02 1988-04-02 Regelverfahren zum vermeiden des pumpens eines turboverdichters mittels bedarfsweisen abblasens
DE3811232 1988-04-02

Publications (3)

Publication Number Publication Date
EP0336095A2 EP0336095A2 (de) 1989-10-11
EP0336095A3 EP0336095A3 (en) 1990-12-05
EP0336095B1 true EP0336095B1 (de) 1992-11-04

Family

ID=6351295

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89103134A Expired - Lifetime EP0336095B1 (de) 1988-04-02 1989-02-23 Regelverfahren zum Vermeiden des Pumpens eines Turboverdichters mittels bedarfsweisen Abblasens

Country Status (5)

Country Link
US (1) US4936741A (enrdf_load_stackoverflow)
EP (1) EP0336095B1 (enrdf_load_stackoverflow)
JP (1) JPH01285698A (enrdf_load_stackoverflow)
AT (1) ATE82045T1 (enrdf_load_stackoverflow)
DE (2) DE3811232A1 (enrdf_load_stackoverflow)

Families Citing this family (16)

* 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
US5235801A (en) * 1991-12-12 1993-08-17 Allied-Signal Inc. On/off surge prevention control for a variable geometry diffuser
US5222356A (en) * 1991-12-12 1993-06-29 Allied-Signal Inc. Modulating surge prevention control for a variable geometry diffuser
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
DE19541192C2 (de) * 1995-11-04 1999-02-04 Ghh Borsig Turbomaschinen Gmbh Verfahren zum Schutz eines Turbokompressors vor Betrieb im instabilen Arbeitsbereich mittels einer Abblaseeinrichtung
US5709526A (en) * 1996-01-02 1998-01-20 Woodward Governor Company Surge recurrence prevention control system for dynamic compressors
WO1997044719A1 (en) * 1996-05-22 1997-11-27 Ingersoll-Rand Company Method for detecting the occurrence of surge in a centrifugal compressor
JP3751208B2 (ja) * 2001-02-23 2006-03-01 株式会社神戸製鋼所 多段可変速圧縮機の制御方法
DE102009041222A1 (de) 2009-09-11 2011-03-24 Man Diesel & Turbo Se Turbomaschine mit überwachter selbsttätiger Rückschlagarmatur
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
US10436208B2 (en) * 2011-06-27 2019-10-08 Energy Control Technologies, Inc. Surge estimator
JP6431244B2 (ja) * 2016-03-08 2018-11-28 三菱重工エンジン＆ターボチャージャ株式会社 排気タービン過給機のサージ回避制御方法、サージ回避制御装置
RU2016112469A (ru) * 2016-04-01 2017-10-04 Фишер-Роузмаунт Системз, Инк. Способы и устройство для обнаружения и предотвращения помпажа компрессора
CN111379725B (zh) * 2018-12-28 2021-06-25 新疆八一钢铁股份有限公司 离心式气体压缩机控制方法
US11421582B2 (en) * 2020-12-02 2022-08-23 Ford Global Technologies, Llc Method of controlling a turbocharger

Family Cites Families (9)

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Publication number Priority date Publication date Assignee Title
US3276674A (en) * 1963-03-06 1966-10-04 Shell Oil Co Method for preventing surging of compressors
US4139328A (en) * 1977-05-25 1979-02-13 Gutehoffnungshitte Sterkrade Ag Method of operating large turbo compressors
DE2852717C2 (de) * 1978-12-06 1982-02-11 M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 4200 Oberhausen Verfahren zur Enddruckbegrenzung für Turbo-Verdichter mittels Abblaseregelung
US4464720A (en) * 1982-02-12 1984-08-07 The Babcock & Wilcox Company Centrifugal compressor surge control system
DE3540285A1 (de) * 1985-11-13 1987-05-14 Gutehoffnungshuette Man Verfahren und einrichtung zum regeln von turbokompressoren
DE3540284A1 (de) * 1985-11-13 1987-05-14 Gutehoffnungshuette Man Einrichtung zum regeln eines turbokompressors zur verhinderung des pumpens
DE3544821A1 (de) * 1985-12-18 1987-06-19 Gutehoffnungshuette Man Verfahren zum regeln von turbokompressoren zur vermeidung des pumpens
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

Also Published As

Publication number Publication date
EP0336095A2 (de) 1989-10-11
DE3811232C2 (enrdf_load_stackoverflow) 1991-12-19
DE3811232A1 (de) 1989-10-26
JPH01285698A (ja) 1989-11-16
DE58902589D1 (de) 1992-12-10
US4936741A (en) 1990-06-26
EP0336095A3 (en) 1990-12-05
ATE82045T1 (de) 1992-11-15

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