EP0336092B1 - Procédé de protection d'un compresseur centrifuge contre le pompage par une valve d'échappement et le dispositif pour réaliser ce procédé - Google Patents

Procédé de protection d'un compresseur centrifuge contre le pompage par une valve d'échappement et le dispositif pour réaliser ce procédé Download PDF

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Publication number
EP0336092B1
EP0336092B1 EP89103059A EP89103059A EP0336092B1 EP 0336092 B1 EP0336092 B1 EP 0336092B1 EP 89103059 A EP89103059 A EP 89103059A EP 89103059 A EP89103059 A EP 89103059A EP 0336092 B1 EP0336092 B1 EP 0336092B1
Authority
EP
European Patent Office
Prior art keywords
valve
controller
blow
pressure medium
surge limit
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
EP89103059A
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German (de)
English (en)
Other versions
EP0336092A2 (fr
EP0336092A3 (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
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 MAN Gutehoffnungshutte GmbH filed Critical MAN Gutehoffnungshutte GmbH
Priority to AT89103059T priority Critical patent/ATE79927T1/de
Publication of EP0336092A2 publication Critical patent/EP0336092A2/fr
Publication of EP0336092A3 publication Critical patent/EP0336092A3/de
Application granted granted Critical
Publication of EP0336092B1 publication Critical patent/EP0336092B1/fr
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
    • 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
    • F04D27/0223—Control schemes therefor
    • 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
    • F04D27/023—Details or means for fluid extraction

Definitions

  • the invention relates to a method for protecting a turbocompressor against pumps by means of blow-off via a blow-off valve, wherein in the method a control parameter is determined from measured values at least for the compressor flow and compressor end pressure and from predetermined or predeterminable setpoints, on the basis of which a position-controlled adjustment of the by a surge limit controller Blow-off valve is carried out by means of a pneumatic or hydraulic actuating device with positioner via a pressure medium and, if a safety limit value is exceeded by the control parameter, the blow-off valve is actuated by a safety controller with maximum adjustment speed in the opening direction. Furthermore, the invention relates to a device for performing the method.
  • a known method of the type mentioned (see, for example, EP-A-230.009) consists of a parallel connection of a comparatively slow control with a fast safety control. Due to the slower control, which normally works on its own, the operating point of the compressor is kept in its permissible map area by means of position-controlled opening or closing of the relief valve - or also bypass valve. If you experience Sudden and / or major malfunctions, the safety control intervenes, which causes the relief valve to open at maximum actuating speed.
  • a disadvantage of the known methods is that either the maximum adjustment speed of this quick opening of the relief valve is limited by the positioner or that after the safety control has been triggered, there is always an unstoppable adjustment of the relief valve to its open end position. The former requires a large safety margin from the surge line; the latter has an unfavorable influence on a process downstream of the compressor, which manifests itself in particular as a pressure drop.
  • the solution to the first part of the task is achieved according to the invention by a method of the type mentioned at the outset, which is characterized in that when the safety controller responds, the pressure medium for the blow-off valve actuation is removed directly bypassing the positioner and that when the safety controller is reset, the discharge of the pressure medium ends and the control is again taken over solely by the surge limit controller with the downstream positioner.
  • the blow-off valve at a quick opening with its technically maximum possible adjustment speed independent of the positioner and only as far as required to be adjusted in the opening direction to compensate for a malfunction.
  • a delayed or excessively strong or long blowing or blowing of process air is thus avoided and disadvantageous effects, in particular pumping or pressure drops in the process, no longer occur or are only greatly damped.
  • the slower reaction of the process to processes in the compressor or process which require the blow-off valve to be closed is not a disadvantage, since these processes are always associated with a safe movement of the operating point away from the surge limit. Rather, the required stability of the control system is achieved in this way, ie disadvantageous "oscillation" is avoided. Due to the quick and appropriate response of the relief valve, this method also meets high demands for a regulation for the protection of the compressor against pumps.
  • the output of the surge limit controller is tracked practically without delay to a value corresponding to the current position of the relief valve during the immediate adjustment of the relief valve caused by the safety control. This ensures that the controller takes over the control after the quick opening of the relief valve caused by the safety controller without jumps and bumps, thereby avoiding a disturbing running-in and / or settling of the controller and the relief valve to their new stationary position.
  • a preferred embodiment of the method provides that, as a control parameter, the difference between the actual speed-location value of the compressor operating point and the associated target speed-location value according to a predeterminable speed-location target value curve, when it is reached, pumping is still prevented can be used, the distance of the working point from the surge limit being used as the location and the speed of movement of the working point relative to the surge limit in the compressor map being used as the speed.
  • This ensures that, in addition to the location of the operating point in the compressor map, the speed of movement of the operating point in the compressor map is also taken into account. It is thus possible to always open the relief valve even when the operating point approaches the surge limit at different speeds at the latest possible time at which pumping of the compressor is just prevented.
  • the compressor can therefore be operated very close to the surge line without pumping risk, which in particular enables cheaper partial load operation.
  • the valve may continue to run for a more or less long time after the safety control has been reset.
  • B based on energy storage effects of the printing medium.
  • the regulation by the surge limit controller is only carried out after a predefinable period of time after the safety control has been reset.
  • a device which has a surge limit controller for a position-controlled adjustment of a relief valve via a pressure medium by means of a pneumatic or hydraulic actuation device with a positioner and a piston-cylinder unit, and a safety control for actuating the relief valve as required has in the opening direction with maximum adjustment speed, and which is characterized in that a switching valve on the inlet side is connected to a branch that opens between the positioner and piston-cylinder unit in a pressure medium line connecting them, that the switching valve is connected on the outlet side to a pressure medium discharge line and that the switching valve via its switching input by the safety controller when it responds in the open position and at whose reset can be switched over in the closed position.
  • the device has a simple structure and is therefore inexpensive to manufacture and operate. It is also easy to maintain and is therefore particularly reliable.
  • the switching valve it is preferably provided that it is a solenoid valve. This ensures reliable function and very fast switching of the valve.
  • FIG. 1 A preferred embodiment of the invention is explained in more detail below with reference to a drawing.
  • the sole figure of the drawing shows a turbocompressor, which is equipped with a device according to the invention, in a schematic representation, on the basis of which the process sequence is also to be explained by way of example.
  • the turbocompressor 1 is connected on the intake side to an intake line 10.
  • the turbocompressor 1 On the discharge side, the turbocompressor 1 is connected to a discharge line 11, which conducts the medium compressed by the turbocompressor 1 to a downstream process via a non-return valve 12.
  • a blow-off line 20 branches off from the discharge line 11, into which a blow-off valve 2 with a pneumatic or hydraulic actuating device 21 is switched on.
  • a flow meter 61 connected to the intake line 10 leads to the compressor 1 flowing flow of the medium to be compressed is detected.
  • the compressor end pressure can be detected by means of a pressure meter 62 connected to the discharge line 11.
  • a function transmitter 63 is connected downstream of the pressure meter 62 and, on the basis of stored data, outputs the minimally permissible minimum flow value for the compressor 1 which in each case is associated with a specific pressure.
  • the actual flow value measured by the flow meter 61 and the desired flow value output by the function generator 62 are fed to a subtractor 64, in which the difference is formed by subtracting the actual value from the desired value.
  • a function generator 51 and a speedometer 52 are connected downstream of the subtractor 64.
  • a speed-location setpoint curve for the operating point of the compressor 1 is stored in the function generator 51.
  • the function values of this curve are those values at which pumping of the compressor can just be prevented, depending on the current actual position and actual speed of the operating point in the compressor map.
  • the speedometer 52 serves to determine the speed of movement of the operating point of the compressor in the compressor map relative to the surge limit. This can be done, for example, by differentiating or by forming a difference with subsequent division.
  • the speed of the operating point (actual value) determined in the speedometer 52 and the functional value (setpoint) output by the function generator 51 are subtracted from one another in a subsequent subtractor 53, the setpoint being here by definition subtracted from the actual value.
  • the difference that is generated in the subtractor 53 is the control parameter for the actuation of the relief valve 2.
  • control parameter generated in this way is passed in parallel to a safety controller 31 and a surge limit controller 41, which are connected downstream of the subtractor 53.
  • the safety controller 31 is designed so that it can only assume two switching states at its output, which occur depending on whether the control parameter exceeds a predetermined safety limit value according to a safety line in the compressor map or not.
  • the surge limit controller 41 ensures continuous regulation, i. H. a position-controlled adjustment of the relief valve 2 depending on the position of the working point in the map.
  • the output of the surge limit controller 41 acts via a control line 22 on the actuating device 21 of the blow-off valve 2.
  • a pressure medium line 23 leads to a piston-cylinder unit (not shown) for generating the force for the adjustment movement of the blow-off valve 2 in the closing direction.
  • the force for the adjustment movement of the relief valve 2 in the opening direction is generally for safety reasons by means of an energy storage element, for. B. a tensioned spring to ensure an automatic opening of the relief valve 2 in the event of failure of the control.
  • the output of the safety controller 31 acts via a control line 32 on a switching valve 3, more precisely its electromagnetic actuating device 30.
  • This switching valve 3 is connected at its inlet to a branch 23 'which goes from the pressure medium line 23.
  • the switching valve 3 is switched into its open position, whereby the pressure medium from the pressure medium line 23 and the associated piston-cylinder unit via the branch 23 'bypassing the actuating device 21 of the Blow-off valve 2 is discharged immediately.
  • the relief valve 2 is adjusted in the opening direction at an increased adjustment speed until the safety controller 31 is reset to the safe map area after the compressor operating point has returned and the switching valve 2 is thus switched back to its closed position. Furthermore, if necessary, the relief valve 2 is adjusted again from the last position reached by the controller 41 at the slower adjustment speed.
  • Known components can advantageously be used for the safety controller 31 and the surge limit controller 41, so that the implementation of the method and the manufacture of a device suitable for this purpose are comparatively simple and inexpensive.

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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)

Claims (6)

1.- Procédé pour protéger un turbocompresseur du pompage en le purgeant par l'intermédiaire d'une vanne de purge, procédé dans lequel, à partir de valeurs de mesure, tout au moins pour le débit du compresseur et la pression terminale du compresseur, ainsi qu'à partir de valeurs de consigne prédéfinies ou bien susceptibles d'être prédéfinies, un paramètre de réglage est déterminé, à l'aide duquel grâce à un régulateur de limite de pompage s'effectue par l'intermédiaire d'un fluide sous pression un réglage ajusté en position de la vanne de purge, par un moyen de manoeuvre pneumatique ou hydraulique avec régulateur de position, et dans lequel lorsqu'une valeur limite de sécurité est dépassée par le paramètre de réglage, la vanne de purge est actionnée par une commande de sécurité avec une vitesse de déplacement maximale dans le sens de l'ouverture,
procédé caractérisé en ce que lorsque la commande de sécurité réagit, le fluide sous pression pour la manoeuvre de la vanne de purge, est directement détourné en contournant le régulateur de position et en ce que lorsque la commande de sécurité revient à sa position initiale, ce détournement du fluide sous pression se termine et la régulation est à nouveau prise en charge uniquement par le régulateur de limite de pompage avec le régulateur de position branché à la suite.
2.- Procédé selon la revendication 1, caractérisé en ce que la sortie du régulateur de limite de pompage, pendant qu'il est contourné par le réglage de la vanne de purge assuré par la commande de sécurité, est ramenée pratiquement sans retard à une valeur correspondant à la position actuelle de la soupape de purge.
3.- Procédé selon la revendication 1 et la revendication 2, caractérisé en ce que, comme paramètre de réglage, on utilise la différence entre la valeur réelle locale de la vitesse du point de fonctionnement du compresseur et la valeur de consigne locale correspondante de la vitesse, selon une courbe de valeurs de consigne locales de la vitesse susceptible d'être prédéfinie, pour laquelle, lorsqu'elle est atteinte, un pompage peut encore être empêché de justesse, tandis qu'on utilise comme localisation la distance entre le point de fonctionnement et la limite de pompage et comme vitesse, la vitesse de déplacement du point de fonctionnement par rapport à la limite de pompage dans le champ caractéristique du compresseur.
4.- Procédé selon les revendications 1 à 3, caractérisé en ce que la prise en charge de la régulation par le régulateur de limite de pompage, après la remise à l'état initial de la commande de sécurité, ne s'effectue qu'après un laps de temps susceptible d'être prédéfini.
5.- Dispositif pour la mise en oeuvre du procédé selon les revendications 1 à 4, qui comporte un régulateur de limite de pompage pour un réglage ajusté en position d'une vanne de purge par un fluide sous pression et par un moyen de manoeuvre pneumatique ou hydraulique, avec un régulateur de position et une unité piston-cylindre, ainsi qu'avec une commande de sécurité pour actionner en cas de besoin la vanne de purge dans le sens de l'ouverture avec une vitesse de déplacement maximale,
dispositif caractérisé en ce qu'une vanne de commutation (3) est reliée côté entrée à une dérivation (23') qui débouche entre le régulateur de position et l'unité piston-cylindre dans une canalisation de fluide sous pression (23) les reliant, en ce que la vanne de commutation (3) est reliée côté sortie avec une canalisation de détournement du fluide sous pression, et en ce que la vanne de commutation (3) est susceptible d'être commutée par l'intermédiaire de son entrée de commutation dans la position d'ouverture par la commande de sécurité (31) lorsque celle-ci réagit et dans la position de fermeture lorsque la commande de sécurité revient à son état initial.
6.- Dispositif selon la revendication 5, caractérisé en ce que la vanne de commutation (3) est une vanne électromagnétique.
EP89103059A 1988-04-02 1989-02-22 Procédé de protection d'un compresseur centrifuge contre le pompage par une valve d'échappement et le dispositif pour réaliser ce procédé Expired - Lifetime EP0336092B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT89103059T ATE79927T1 (de) 1988-04-02 1989-02-22 Verfahren zum schuetzen eines turboverdichters vor pumpen mittels abblasens ueber ein abblaseventil sowie vorrichtung zur durchfuehrung des verfahrens.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3811230 1988-04-02
DE3811230A DE3811230A1 (de) 1988-04-02 1988-04-02 Verfahren zum schuetzen eines turboverdichters vor pumpen mittels abblasens ueber ein abblaseventil sowie vorrichtung zur durchfuehrung des verfahrens

Publications (3)

Publication Number Publication Date
EP0336092A2 EP0336092A2 (fr) 1989-10-11
EP0336092A3 EP0336092A3 (en) 1990-12-05
EP0336092B1 true EP0336092B1 (fr) 1992-08-26

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP89103059A Expired - Lifetime EP0336092B1 (fr) 1988-04-02 1989-02-22 Procédé de protection d'un compresseur centrifuge contre le pompage par une valve d'échappement et le dispositif pour réaliser ce procédé

Country Status (5)

Country Link
US (1) US4936740A (fr)
EP (1) EP0336092B1 (fr)
JP (1) JPH01285697A (fr)
AT (1) ATE79927T1 (fr)
DE (2) DE3811230A1 (fr)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2666854B1 (fr) * 1990-09-19 1992-12-18 Framatome Sa Dispositif de commande de moyens d'antipompage d'un compresseur.
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
US5993163A (en) * 1996-10-07 1999-11-30 Trilectron Industries, Inc. Demand system for pneumatic source with controller responsive to bypass air flow rate
US5951240A (en) * 1997-11-21 1999-09-14 Compressor Controls Corporation Method and apparatus for improving antisurge control of turbocompressors by reducing control valve response time
US6217288B1 (en) * 1998-01-20 2001-04-17 Compressor Controls Corporation Method and apparatus for limiting a critical variable of a group of compressors or an individual compressor
GB2448734A (en) * 2007-04-26 2008-10-29 Rolls Royce Plc Controlling operation of a compressor to avoid surge, stall or flutter
WO2012013530A1 (fr) * 2010-07-29 2012-02-02 Siemens Aktiengesellschaft Procédé pour faire fonctionner un compresseur
US8726628B2 (en) 2010-10-22 2014-05-20 General Electric Company Combined cycle power plant including a carbon dioxide collection system
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

Family Cites Families (12)

* Cited by examiner, † Cited by third party
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
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
DE3540087A1 (de) * 1985-11-12 1987-05-14 Gutehoffnungshuette Man Verfahren zum regeln von turbokompressoren
DE3540284A1 (de) * 1985-11-13 1987-05-14 Gutehoffnungshuette Man Einrichtung zum regeln eines turbokompressors zur verhinderung des pumpens
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

Also Published As

Publication number Publication date
EP0336092A2 (fr) 1989-10-11
EP0336092A3 (en) 1990-12-05
ATE79927T1 (de) 1992-09-15
JPH01285697A (ja) 1989-11-16
DE3811230C2 (fr) 1992-01-16
DE58902110D1 (de) 1992-10-01
DE3811230A1 (de) 1989-10-26
US4936740A (en) 1990-06-26

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