EP0223207B1 - Procédé et dispositif de réglage d'un turbocompresseur pour empêcher le pompage - Google Patents

Procédé et dispositif de réglage d'un turbocompresseur pour empêcher le pompage Download PDF

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Publication number
EP0223207B1
EP0223207B1 EP86115791A EP86115791A EP0223207B1 EP 0223207 B1 EP0223207 B1 EP 0223207B1 EP 86115791 A EP86115791 A EP 86115791A EP 86115791 A EP86115791 A EP 86115791A EP 0223207 B1 EP0223207 B1 EP 0223207B1
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EP
European Patent Office
Prior art keywords
blow
controller
curve
signal
correction signal
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Expired - Lifetime
Application number
EP86115791A
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German (de)
English (en)
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EP0223207A3 (en
EP0223207A2 (fr
Inventor
Wilfried Dipl.-Ing. Blotenberg
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Everllence SE
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MAN Gutehoffnungshutte GmbH
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Publication of EP0223207B1 publication Critical patent/EP0223207B1/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 device for regulating a turbo compressor, of the type specified in the preamble of claim 1.
  • a device of this type is known from US-A 4142 838.
  • Pumping is the term for an unstable state of a turbo compressor, in which the pumping medium flows back intermittently or periodically from the pressure side to the suction side.
  • a pump limit line can be defined in the characteristic diagram of the compressor, which separates the stable from the unstable area.
  • a blow-off line is defined in the map, which runs at a safety distance from the surge limit line. The current operating point of the compressor in the map is recorded, and when the operating point approaches the blow-off line, the regulator opens a blow-off or blow-off valve connected to the compressor output more or less in order to lower the final pressure before the operating point approaches the unstable area.
  • this regulation does not respond quickly enough, however, so that the operating point can cross the blow-off line and possibly reach the surge limit line.
  • a safety line which may be identical to the blow-off line or may lie between this and the surge line, an additional signal is generated which controls a rapid, complete or partial opening of the blow-off valve.
  • the invention has for its object to develop a device of the type mentioned so that a delay-free action of the correction signal on the relief valve is achieved with simple means, without special measures for subsequent compensation of the correction signal are necessary, and without the operating point unnecessarily long beyond the blow-off line.
  • the correction signal By applying the correction signal directly to the integral part of the controller, the correction signal is passed on to the controller output without delay in order to bring about a quick opening of the relief valve.
  • the controller output signal immediately assumes at least approximately the value that it must have after the fault has ended, i.e. there is no longer a compensation time during which the controller has to readjust to the new value via the compressor system working beyond the blow-off line.
  • the correction signal is fed to the integral part as a control signal and the integration time constant (readjustment time) is changed as a function of the position of the operating point. This ensures that the controller responds quickly in critical operating situations, since the reset time of the controller is reduced when the safety line is exceeded.
  • the output signal Y of an integral proportional controller is a function of the integration time constant (reset time) T N , the proportional gain KP and the control difference X d :
  • control difference X d ie the distance between the working point and the blow-off line, is relatively small in the vicinity of the blow-off line and consequently the change in the controller output signal Y takes place only slowly. However, this contradicts the requirement that the controller should react quickly when the blow-off line is exceeded.
  • a correction variable is therefore switched to the integral part of the controller when the blow-off line is exceeded, so that the output of the controller changes quickly and the downstream blow-off valve is triggered accordingly quickly.
  • the pressure difference in front of and behind a throttle orifice is measured by sensors 3, 5 and an actual value for the suction-side throughput V is formed therefrom in a transmitter 7.
  • a sensor 9 with transmitter 11 detects the final pressure P of the compressor.
  • the computer 13 determines the distance of the working point defined by P and V from the blow-off line A and generates a desired value signal according to this distance, which is compared in a difference element 17 with the actual value signal by an input signal for the controller 10 form.
  • This comprises at least a proportional part 10a and an integral part 10b and can also have a differential part 10c.
  • the output signal of the controller 10 controls a relief valve 19 branching off from the compressor output.
  • the computer 13 additionally generates a signal which in a signal shaping stage 21 generates a correction signal, e.g. in the form of one or more pulses which are input as an input signal into the integral part 10b of the controller.
  • a correction signal e.g. in the form of one or more pulses which are input as an input signal into the integral part 10b of the controller.
  • the signal shaping part 21 can be designed such that it generates the correction signal as long as the working point is to the left of the safety or blow-off line. However, it is also possible for the signal shaping stage 21 to generate a correction pulse of a defined, adjustable duration. Several pulses can also be generated one after the other, which bring about a change in the integrator content in several stages of adjustable height at adjustable time intervals.
  • the influence of the correction signal can thus be made dependent not only on whether the safety line is exceeded, but also on how far and / or at what speed it is exceeded. This influence can in particular be non-linear and can also be limited to changes with only one sign.
  • the pulse height, the pulse width, the pulse spacing or the pulse-pause ratio and / or the time constant of the correction signal can be varied depending on the position of the operating point in the characteristic diagram.
  • the correction signal is not additionally applied to the integral part of the controller, but rather serves as a control signal for changing the reset time T N.
  • the reset time T N is always adapted to the requirements so that there is always an optimal adjustment of the controller output signal Y.
  • the adjustment time T N is adjusted by means of a control unit 25 and can be carried out in various ways.
  • a shorter reset time is reached when a limit line (safety line) is reached near the blow-off line. If the operating point crosses this line in the opposite direction (towards the safe map area), the system switches back to the original reset time, whereby it may be necessary to provide a hysteresis for switching back.
  • a limit line safety line
  • the reset time can also be changed in another way, for example in several stages or continuously.
  • the reset time T N is a function of the control difference X d
  • f (X d ) should be zero, ie the reset time is constant in this range and has the value T i .
  • the readjustment time can either decrease with increasing control difference in order to increase the effect of the surge limit control with increasing danger for the compressor, or decrease abruptly when a limit is exceeded and increase again with increasing control difference in order to not impermissibly the controller with increasing control difference to design quickly.
  • a combination of both methods can also be used are applied, ie with increasing control difference, the reset time initially decreases and increases again above a limit.
  • PI controller proportional and integral controller
  • FIG. 2 shows a proportional and integral controller (PI controller) as a parallel connection of a proportional controller 10a and an integral controller 10b.
  • PI controller can be represented in this way, even if the controller is implemented in a different form, e.g. as a software algorithm in a digital controller.
  • a limiter can also be provided in the control unit 25, which has the effect that the reset time can neither be greater than that of the stably set controller, nor can it be so short that the relief valve can no longer follow due to its finite actuating speed.
  • the methods can also be used with other control algorithms with time-dependent changes.
  • control device 3 to 7 show further exemplary embodiments of the control device according to the invention.
  • the entire control loop is not shown here, but only the section between the formation of the control difference X d (from the setpoint W and the actual value X) and the controller output y.
  • the limit value stage 27 is set to the distance between the blow-off line and the safety line. If the limit value is reached, the relay 29 switches to the other time constant T N2 .
  • the time constant is adapted as an expression T N / X d to the input signal of the controller.
  • the limiter 31 ensures that certain limits are neither exceeded nor undershot.
  • a switch is made from T N1 to T N2 when the switching threshold is reached. If the control difference X d continues to increase, the effective reset time T N becomes dependent on the output of the function generator again larger. Alternatively, the reset time T N2 can also be omitted; the function generator is then set so that T N first decreases and then increases again.
  • FIG. 6 shows an arrangement in which the limit value stage 27 drives a pulse element 35 when a limit value is exceeded.
  • the pulse element 35 then outputs a larger or more smaller pulses or a ramp to the integrator 37.
  • Fig. 7 An arrangement in which instead of reducing the size T N, the term is multiplied is provided with a constant K is shown in Fig. 7.
  • the relay 41 can also be followed by a time limiter 39, which limits the influence of c on a fixed period of time or dependent on another parameter.
  • the position of the working point is determined by the detection of the final pressure and the throughput in the described embodiments
  • other variables such as the pressure ratio between the final and suction pressure can also be used for the detection of the working point or the definition of the characteristic map in a manner known per se.
  • the speed, the vane position, the power, the input signal of the controller 10 or the output signal of a process controller are used.
  • the map can be determined by other parameters, such as the adiabatic delivery head (instead of the final pressure) and the intake volume flow (instead of the suction-side pressure difference) are determined.
  • the surge line has a clear course in the map, so that the blow-off and safety line can also be clearly defined with respect to the surge line.

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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)

Claims (12)

1. Dispositif de réglage d'un turbocompresseur pour empêcher le pompage, comportant des capteurs pour déterminer la valeur réelle d'une ou plusieurs grandeurs de fonctionnement caractéristiques du point de fonctionnement du compresseur, notamment la pression à la sortie et le débit, des transmetteurs de valeur de consigne donnant le tracé prédétermine d'au moins une ligne de purge dans le champ de caractéristiques du compresseur, un régulateur produisant en fonction de la valeur réelle et de la valeur de consigne un signal de manoeuvre continu pour l'ouverture d'une soupape de purge, ce régulateur comportant au moins une partie proportionnelle et une partie intégrale ainsi que, le cas échéant, une partie différentielle, ainsi qu'un dispositif produisant un signal de correction pour l'ouverture rapide de la soupape de purge lors du franchissement de la ligne de purge ou d'une ligne de sécurité dans le champ de caractéristiques, caractérisé en ce que le signal de correction peut être envoyé à la partie intégrale (10b) du régulateur (10) en tant que signal d'entrée ou en tant que signal de commande agissant sur le temps de compensation de la partie intégrale.
2. Dispositif selon la revendication 1, caractérisé en ce que le signal de correction est envoyé à la partie intégrale (10b) par l'intermédiaire d'un organe de temporisation (23) à constante de temps réglable.
3. Dispositif selon la revendication 1 ou 2, caractérisé en ce que le signal de correction est appliqué tant que le point de fonctionnement est au-dessus de la ligne de purge ou de la ligne de sécurité.
4. Dispositif selon la revendication 1 ou 2, caractérisé en ce que le signal de correction a une durée prédéterminée, réglable.
5. Dispositif selon la revendication 1, caractérisé en ce que le signal de correction provoque une variation du contenu de la partie intégrale (10b) en plusieurs étages de hauteur réglable à des intervalles de temps réglables.
6. Dispositif selon l'une des revendications 1 à 5, caractérisé en ce que la grandeur du signal de correction ou l'intervalle des impulsions de correction ou encore la constante de temps dépendent du signal d'entrée du régulateur (10).
7. Dispositif selon la revendication 6, caractérisé en ce que le signal de correction est une fonction non linéaire du signal d'entrée du régulateur (10).
8. Dispositif suivant l'une des revendications 1 à 5, caractérisé en ce que la grandeur du signal de correction, le tracé en fonction du temps de la suite d'impulsions, la hauteur des impulsions individuelles ou la constante de temps dépendent de la position du point de fonctionnement dans le champ de caractéristiques.
9. Procédé de réglage d'un turbocompresseur pour empêcher le pompage, dans lequel on détermine la position du point de fonctionnement du compresseur par rapport à une ligne de purge définie dans le champ de caractéristiques et on règle une soupape de purge ou de soufflage en fonction de l'approche du point de fonctionnement par rapport à la ligne de purge au moyen d'un régulateur comportant une partie intégrale, un signal supplémentaire pour l'ouverture rapide de la soupape étant produit lors du franchissement de la ligne de purge ou d'une ligne de sécurité qui lui est associée, caractérisé en ce que le signal supplémentaire est envoyé à la partie intégrale du régulateur en tant que signal d'entrée ou en tant que signal de commande agissant sur le temps de compensation de la partie intégrale et en ce que l'ouverture rapide de la soupape est provoquée par le signal de sortie du régulateur.
10. Procédé selon la revendication 9, caractérisé en ce que le temps de compensation est une fonction de l'écart de réglage si le point de fonctionnement se trouve au-dessus de la ligne de sécurité.
11. Procédé selon la revendication 9 ou 10, caractérisé en ce que la variation du temps de compensation au voisinage de la ligne de sécurité a lieu avec une hystérésis.
12. Procédé selon la revendication 9, caractérisé en ce que le temps de compensation est limité à un domaine compris entre une valeur minimale et une valeur maximale.
EP86115791A 1985-11-13 1986-11-13 Procédé et dispositif de réglage d'un turbocompresseur pour empêcher le pompage Expired - Lifetime EP0223207B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3540284 1985-11-13
DE19853540284 DE3540284A1 (de) 1985-11-13 1985-11-13 Einrichtung zum regeln eines turbokompressors zur verhinderung des pumpens

Publications (3)

Publication Number Publication Date
EP0223207A2 EP0223207A2 (fr) 1987-05-27
EP0223207A3 EP0223207A3 (en) 1988-01-13
EP0223207B1 true EP0223207B1 (fr) 1990-10-03

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EP86115791A Expired - Lifetime EP0223207B1 (fr) 1985-11-13 1986-11-13 Procédé et dispositif de réglage d'un turbocompresseur pour empêcher le pompage

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Country Link
US (1) US4968215A (fr)
EP (1) EP0223207B1 (fr)
JP (1) JPS62247200A (fr)
DE (2) DE3540284A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19812159A1 (de) * 1998-03-20 1999-09-23 Ruhrgas Ag Verfahren zum Regeln des Volumenstroms von Gas, insbesondere Erdgas, durch einen Turboverdichter

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3805119A1 (de) * 1988-02-18 1989-08-31 Gutehoffnungshuette Man Verfahren und einrichtung zum regeln von turbokompressoren
DE3809881A1 (de) * 1988-03-24 1989-10-12 Gutehoffnungshuette Man Regelverfahren zur vermeidung des pumpens eines turbokompressors
DE3811230A1 (de) * 1988-04-02 1989-10-26 Gutehoffnungshuette Man Verfahren zum schuetzen eines turboverdichters vor pumpen mittels abblasens ueber ein abblaseventil sowie vorrichtung zur durchfuehrung des verfahrens
DE3811232A1 (de) * 1988-04-02 1989-10-26 Gutehoffnungshuette Man Regelverfahren zum vermeiden des pumpens eines turboverdichters mittels bedarfsweisen abblasens
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
US6059522A (en) * 1996-04-17 2000-05-09 United Technologies Corporation Compressor stall diagnostics and avoidance
DE19828368C2 (de) * 1998-06-26 2001-10-18 Man Turbomasch Ag Ghh Borsig Verfahren und Vorrichtung zum Betreiben von zwei- oder mehrstufigen Verdichtern
DE10001365A1 (de) * 2000-01-14 2001-07-19 Man Turbomasch Ag Ghh Borsig Verfahren und Einrichtung zum Regeln eines Turbokompressors zur Verhinderung des Pumpens
JP5871157B2 (ja) * 2011-10-03 2016-03-01 株式会社Ihi 遠心圧縮設備のサージング防止方法

Citations (1)

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US4142838A (en) * 1977-12-01 1979-03-06 Compressor Controls Corporation Method and apparatus for preventing surge in a dynamic compressor

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US3276674A (en) * 1963-03-06 1966-10-04 Shell Oil Co Method for preventing surging of compressors
US4046490A (en) * 1975-12-01 1977-09-06 Compressor Controls Corporation Method and apparatus for antisurge protection of a dynamic compressor
US4139328A (en) * 1977-05-25 1979-02-13 Gutehoffnungshitte Sterkrade Ag Method of operating large turbo compressors
US4164034A (en) * 1977-09-14 1979-08-07 Sundstrand Corporation Compressor surge control with pressure rate of change control
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
US4442667A (en) * 1981-01-14 1984-04-17 Aviation Electric Ltd. Acceleration limit reset
DE3105376C2 (de) * 1981-02-14 1984-08-23 M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 4200 Oberhausen Verfahren zum Betreiben von Turboverdichtern
US4428194A (en) * 1981-02-19 1984-01-31 The Garrett Corporation Compressor bleed air control apparatus and methods
US4627788A (en) * 1984-08-20 1986-12-09 The Babcock & Wilcox Company Adaptive gain compressor surge control system

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4142838A (en) * 1977-12-01 1979-03-06 Compressor Controls Corporation Method and apparatus for preventing surge in a dynamic compressor

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19812159A1 (de) * 1998-03-20 1999-09-23 Ruhrgas Ag Verfahren zum Regeln des Volumenstroms von Gas, insbesondere Erdgas, durch einen Turboverdichter

Also Published As

Publication number Publication date
EP0223207A3 (en) 1988-01-13
DE3540284A1 (de) 1987-05-14
DE3674723D1 (de) 1990-11-08
EP0223207A2 (fr) 1987-05-27
JPS62247200A (ja) 1987-10-28
US4968215A (en) 1990-11-06

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