EP0336092B1 - Method to protect a centrifugal compressor against surge by venting via a vent valve and system to realize the method - Google Patents

Method to protect a centrifugal compressor against surge by venting via a vent valve and system to realize the method 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
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EP
European Patent Office
Prior art keywords
valve
controller
blow
pressure medium
surge limit
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EP89103059A
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German (de)
French (fr)
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EP0336092A2 (en
EP0336092A3 (en
Inventor
Wilfried Dr.-Ing. Blotenberg
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MAN Energy Solutions SE
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MAN Gutehoffnungshutte GmbH
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Priority to AT89103059T priority Critical patent/ATE79927T1/en
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Publication of EP0336092A3 publication Critical patent/EP0336092A3/en
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    • 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)

Abstract

In the case of known methods of the type stated a continuous surge limit control and a safety control, intervening in an emergency, are operated in parallel. When the safety control responds, this results either in complete opening of the venting valve which cannot be maintained, resulting in a fall in pressure in the downstream process, or the rate of opening of the venting valve is limited by the actuating device of the venting valve, which leads to slower reaction in the case of a malfunction. The new method is intended to rectify this drawback. <??>The new method is characterised in that, when the safety control responds, the pressure medium for actuating the venting valve is led off directly, avoiding the position regulator, and that when the safety control returns leading-off of the pressure medium ceases and the control is again taken over solely by the surge limit controller and the downstream position regulator. The new method means that, in the event of rapid opening, the venting valve is adjusted at its technically maximum possible rate of adjustment, independent of the position regulator, and only as far as necessary in the opening direction in order to catch any disturbance occurring. Delayed or excessive or prolonged venting with its detrimental consequences is thereby avoided. <??>The new method is suitable for turbocompressors in various spheres of application, in particular for large compressors. <IMAGE>

Description

Die Erfindung betrifft ein Verfahren zum Schützen eines Turboverdichters vor Pumpen mittels Abblasens über ein Abblaseventil, wobei in dem Verfahren aus Meßwerten zumindest für den Verdichterdurchfluß und Verdichterenddruck sowie aus vorgegebenen bzw. vorgebbaren Sollwerten ein Regelparameter bestimmt wird, anhand dessen durch einen Pumpgrenzregler eine stellungsgeregelte Verstellung des Abblaseventils mittels einer pneumatischen oder hydraulischen Betätigungseinrichtung mit Stellungsregler über ein Druckmedium erfolgt und wobei bei Überschreiten eines Sicherheits-Grenzwertes durch den Regelparameter das Abblaseventil durch eine Sicherheitssteuerung mit maximaler Verstellgeschwindigkeit in Öffnungsrichtung betätigt wird. Weiterhin betrifft die Erfindung eine Vorrichtung zur Durchführung des Verfahrens.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.

Ein bekanntes Verfahren der genannten Art (siche z.B. EP-A-230.009) besteht aus einer Parallelschaltung einer vergleichsweise langsamen Regelung mit einer schnellen Sicherheitssteuerung. Durch die langsamere Regelung, die im Normalfall allein arbeitet, wird bei Bedarf durch stellungsgeregeltes Öffnen oder Schließen des Abblaseventils - oder auch Umblaseventils - der Arbeitspunkt des Verdichters in dessen zulässigem Kennfeldbereich gehalten. Bei einem Auftreten von plötzlichen und/oder großen Störungen greift die Sicherheitssteuerung ein, die eine Öffnung des Abblaseventils mit maximaler Stellgeschwindigkeit bewirkt. Nachteilig ist bei den bekannten Verfahren, daß entweder die maximale Verstellgeschwindigkeit dieser Schnellöffnung des Abblaseventils durch den Stellungsregler begrenzt ist oder daß es, nachdem die Sicherheitssteuerung einmal ausgelöst ist, stets zu einem nicht mehr aufzuhaltenden Verstellen des Abblaseventils bis zu seiner Öffnungsendstellung kommt. Ersteres erfordert einen großen Sicherheitsabstand von der Pumpgrenze; letzteres hat auf einen dem Verdichter nachgeschalteten Prozeß einen ungünstigen Einfluß, der sich insbesondere als Druckeinbruch äußert.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.

Es stellt sich daher die Aufgabe, ein Verfahren der eingangs genannten Art zu schaffen, das die aufgeführten Nachteile vermeidet und das insbesondere einfach arbeitet und zugleich nachteilige Einflüsse auf den nachgeschalteten Prozeß vermeidet oder wenigstens vermindert. Außerdem soll ein Vorrichtung zur Durchführung des Verfahrens geschaffen werden.It is therefore the task of creating a method of the type mentioned at the outset which avoids the disadvantages mentioned and which in particular works simply and at the same time avoids or at least reduces adverse influences on the downstream process. In addition, a device for performing the method is to be created.

Die Lösung des ersten Teils der Aufgabe gelingt erfindungsgemäß durch ein Verfahren der eingangs genannten Art, welches dadurch gekennzeichnet ist, daß bei Ansprechen der Sicherheitssteuerung das Druckmedium für die Abblaseventilbetätigung unter Umgehung des Stellungsreglers unmittelbar abgeführt wird und daß bei Rücksetzen der Sicherheitssteuerung das Abführen des Druckmediums beendet und die Regelung wieder allein vom Pumpgrenzregler mit dem nachgeschalteten Stellungsregler übernommen wird.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.

Mit dem erfindungsgemäßen Verfahren wird erreicht, daß das Abblaseventil bei einer Schnellöffnung mit seiner technisch maximal möglichen, vom Stellungsregler unabhängigen Verstellgeschwindigkeit und nur noch so weit wie erforderlich in Öffnungsrichtung verstellt wird, um eine auftretende Störung aufzufangen. Ein verspätetes oder übermäßig starkes oder langes Abblasen oder Umblasen von Prozeßluft wird so vermieden und nachteilige Auswirkungen, insbesondere ein Pumpen oder Druckeinbrüche im Prozeß, treten nicht mehr bzw. nur noch stark gedämpft auf. Das langsamere Reagieren des Verfahrens auf Vorgänge im Verdichter oder Prozeß, die ein Schließen des Abblaseventils erfordern, ist in der Praxis kein Nachteil, da diese Vorgänge stets mit einer ungefährlichen Bewegung des Arbeitspunktes von der Pumpgrenze weg verbunden sind. Vielmehr wird hierdurch die erforderliche Stabilität der Regelung erreicht, d. h. es wird ein nachteiliges "Schwingen" vermieden. Aufgrund der so erreichten schnellen und zugleich angemessenen Reaktion des Abblaseventils genügt dieses Verfahren auch hohen Ansprüchen an eine Regelung für den Schutz des Verdichters vor Pumpen.With the method according to the invention it is achieved that 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. In practice, 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.

In einer vorteilhaften Weiterbildung des Verfahrens ist vorgesehen, daß der Ausgang des Pumpgrenzreglers während der ihn umgehenden, durch die Sicherheitssteuerung bewirkten Verstellung des Abblaseventils praktisch verzögerungsfrei auf einen der aktuellen Stellung des Abblaseventils entsprechenden Wert nachgeführt wird. Hiermit wird erreicht, daß die Übernahme der Regelung durch den Regler nach der von der Sicherheitssteuerung bewirkten Schnellöffnung des Abblaseventils sprung- und stoßfrei erfolgt, wodurch ein störendes Einlaufen und/oder Einschwingen des Reglers und des Abblaseventils auf ihre neue stationäre Stellung vermieden werden.In an advantageous development of the method it is provided that 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.

Eine bevorzugte Ausgestaltung des Verfahrens sieht vor, daß als Regelparameter die Differenz zwischen dem Geschwindigkeits-Orts-Istwert des Verdichterarbeitspunktes und dem zugehörigen Geschwindigkeits-Orts-Sollwert gemäß einer vorgebbaren Geschwindigkeits-Orts-Sollwertkurve, bei deren Erreichen ein Pumpen noch gerade verhindert werden kann, verwendet wird, wobei als Ort der Abstand des Arbeitspunktes von der Pumpgrenze und als Geschwindigkeit die Bewegungsgeschwindigkeit des Arbeitspunktes relativ zur Pumpgrenze im Verdichterkennfeld verwendet wird. Hiermit wird erreicht, daß außer dem Ort des Arbeitspunktes im Verdichterkennfeld auch die Bewegungsgeschwindigkeit des Arbeitspunktes im Verdichterkennfeld berücksichtigt wird. Somit ist es möglich, die Öffnung des Abblaseventils auch bei unterschiedlich schneller Annäherung des Arbeitspunktes an die Pumpgrenze stets zum spätestmöglichen Zeitpunkt vorzunehmen, an dem ein Pumpen des Verdichters gerade noch verhindert wird. Der Verdichter kann deshalb ohne Pumprisiko sehr dicht an der Pumpgrenze betrieben werden, was insbesondere einen günstigeren Teillastbetrieb ermöglicht.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.

Je nach Ausgestaltung des Abblaseventils und seiner Betätigungseinrichtung kann es zu einem mehr oder weniger langen Weiterlaufen des Ventils nach dem Rücksetzen der Sicherheitssteuerung kommen, was z. B. auf Energiespeichereffekten des Druckmediums beruht. Um dem Abblaseventil ausreichend Zeit zu geben, seine stationäre Position sicher zu erreichen, ist vorgesehen, daß die Übernahme der Regelung durch den Pumpgrenzregler nach dem Rücksetzen der Sicherheitssteuerung erst nach einer vorgebbaren Zeitspanne erfolgt.Depending on the design of the relief valve and its actuating device, 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. In order to give the relief valve sufficient time to safely reach its stationary position, it is provided that the regulation by the surge limit controller is only carried out after a predefinable period of time after the safety control has been reset.

Die Lösung des zweiten Teils der Aufgabe gelingt erfindungsgemäß durch eine Vorrichtung, welche einen Pumpgrenzregler für eine stellungsgeregelte Verstellung eines Abblaseventils über ein Druckmedium mittels einer pneumatischen oder hydraulischen Betätigungseinrichtung mit einem Stellungsregler und einer Kolben-Zylinder-Einheit sowie eine Sicherheitssteuerung für eine bedarfsweise Betätigung des Abblaseventils in Öffnungsrichtung mit maximaler Verstellgeschwindigkeit aufweist, und welche dadurch gekennzeichnet ist, daß ein Schaltventil einlaßseitig mit einem Abzweig verbunden ist, der zwischen Stellungsregler und Kolben-Zylinder-Einheit in eine diese verbindende Druckmediumleitung mündet, daß das Schaltventil auslaßseitig mit einer Druckmedium-Abführleitung verbunden ist und daß das Schaltventil über seinen Schalteingang durch die Sicherheitssteuerung bei deren Ansprechen in Öffnungsstellung und bei deren Rücksetzen in Schließstellung umschaltbar ist. Die Vorrichtung ist einfach aufgebaut und damit kostengünstig herstellbar und betreibbar. Zudem ist sie leicht zu warten und damit besonders betriebssicher.According to the invention, the solution to the second part of the problem is achieved by 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.

Für das Schaltventil ist bevorzugt vorgesehen, daß es ein Magnetventil ist. Hiermit werden eine zuverlässige Funktion und ein sehr schnelles Schalten des Ventils gewährleistet.For the switching valve it is preferably provided that it is a solenoid valve. This ensures reliable function and very fast switching of the valve.

Ein bevorzugtes Ausführungsbeispiel der Erfindung wird im folgenden anhand einer Zeichnung näher erläutert. Die einzige Figur der Zeichnung zeigt einen Turboverdichter, der mit einer Vorrichtung gemäß Erfindung ausgestattet ist, in einer Schema-Darstellung, anhand derer auch der Verfahrensablauf beispielhaft erläutert werden soll.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.

Wie die Figur zeigt, ist der Turboverdichter 1 ansaugseitig mit einer Ansaugleitung 10 verbunden. Abgabeseitig ist der Turboverdichter 1 mit einer Abgabeleitung 11 verbunden, die über eine Rückschlagklappe 12 das von dem Turboverdichter 1 verdichtete Medium zu einem nachgeschalteten Prozeß leitet. Vor der Rückschlagklappe 12 zweigt von der Abgabeleitung 11 eine Abblaseleitung 20 ab, in welche ein Abblaseventil 2 mit einer pneumatischen oder hydraulischen Betätigungseinrichtung 21 eingeschaltet ist.As the figure shows, the turbocompressor 1 is connected on the intake side to an intake line 10. 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. In front of the 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.

Ansaugseitig wird mittels eines mit der Ansaugleitung 10 verbundenen Durchflußmessers 61 der zum Verdichter 1 strömende Durchfluß des zu verdichtenden Mediums erfaßt. Mittels eines mit der Abgabeleitung 11 verbundenen Druckmessers 62 ist der Verdichterenddruck erfaßbar. Dem Druckmesser 62 ist ein Funktionsgeber 63 nachgeschaltet, der anhand von gespeicherten Daten den jeweils einem bestimmten Druck zugeordneten, gerade noch zulässigen Minimaldurchflußwert für den Verdichter 1 ausgibt. Der vom Durchflußmesser 61 aktuell gemessene Durchfluß-Istwert und der vom Funktionsgeber 62 ausgegebene Durchfluß-Sollwert werden einem Subtrahierer 64 zugeführt, in welchem die Differenz aus diesen durch Subtrahieren des Istwertes vom Sollwert gebildet wird.On the intake side, 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.

Dem Subtrahierer 64 sind ein Funktionsgeber 51 und ein Geschwindigkeitsmesser 52 nachgeschaltet. Im Funktionsgeber 51 ist eine Geschwindigkeits-Orts-Sollwertkurve für den Arbeitspunkt des Verdichters 1 gespeichert. Die Funktionswerte dieser Kurve sind diejenigen Werte, bei welchen in Abhängigkeit von der jeweiligen akutellen Ist-Lage und Ist-Geschwindigkeit des Arbeitspunktes im Verdichterkennfeld gerade noch ein Pumpen des Verdichters verhindert werden kann. Der Geschwindigkeitsmesser 52 dient dazu, die Bewegungsgeschwindigkeit des Arbeitspunktes des Verdichters im Verdichterkennfeld relativ zur Pumpgrenze zu bestimmen. Dies kann beispielsweise durch Differenzieren oder auch durch Differenzbildung mit anschließender Division erfolgen. Die im Geschwindigkeitsmesser 52 bestimmte Geschwindigkeit des Arbeitspunktes (Istwert) und der vom Funktionsgeber 51 ausgegebene Funktionswert (Sollwert) werden in einem nachfolgenden Subtrahierer 53 voneinander subtrahiert, wobei hier definitionsgemäß der Sollwert vom Istwert subtrahiert wird. Die Differenz, die in dem Subtrahierer 53 erzeugt wird, ist der Regelparameter für die Betätigung des Abblaseventils 2.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.

Der so erzeugte Regelparameter wird zu diesem Zweck parallel auf eine Sicherheitssteuerung 31 und einen Pumpgrenzregler 41 gegeben, die dem Subtrahierer 53 nachgeschaltet sind.For this purpose, the 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.

Die Sicherheitssteuerung 31 ist so ausgelegt, daß sie an ihrem Ausgang nur zwei Schaltzustände annehmen kann, die abhängig davon auftreten, ob der Regelparameter einen vorgegebenen Sicherheitsgrenzwert entsprechend einer Sicherheitslinie im Verdichterkennfeld überschreitet oder nicht. Der Pumpgrenzregler 41 sorgt im Unterschied dazu für eine kontinuierliche Regelung, d. h. eine stellungsgeregelte Verstellung des Abblaseventils 2 in Abhängigkeit von der Lage des Arbeitspunktes im Kennfeld. Hierzu wirkt der Ausgang des Pumpgrenzreglers 41 über eine Steuerleitung 22 auf die Betätigungseinrichtung 21 des Abblaseventils 2. Von der Betätigungseinrichtung 21 mit einem Stellungsregler führt eine Druckmediumleitung 23 zu einer nicht eigens dargestellten Kolben-Zylinder-Einheit für die Erzeugung der Kraft für die Verstellbewegung des Abblaseventils 2 in Schließrichtung. Die Kraft für die Verstellbewegung des Abblaseventils 2 in Öffnungsrichtung wird aus Sicherheitsgründen allgemein mittels eines Kraftspeicherelementes, z. B. einer gespannten Feder erzeugt, um bei Ausfall der Regelung ein selbsttätiges Öffnen des Abblaseventils 2 sicherzustellen.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. In contrast, 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. For this purpose, 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. From the actuating device 21 with a positioner, 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.

Der Ausgang der Sicherheitssteuerung 31 wirkt über eine Steuerleitung 32 auf ein Schaltventil 3, genauer dessen elektromagnetische Betätigungseinrichtung 30. Dieses Schaltventil 3 ist mit seinem Einlaß mit einem Abzweig 23′ verbunden, der von der Druckmediumleitung 23 abgeht. Bei Ansprechen der Sicherheitssteuerung 31 wird das Schaltventil 3 in seine Öffnungsstellung umgeschaltet, wodurch das Druckmedium aus der Druckmediumleitung 23 und der zugehörigen Kolben-Zylinder-Einheit über den Abzweig 23′ unter Umgehung der Betätigungseinrichtung 21 des Abblaseventils 2 unmittelbar abgeführt wird. Hierdurch wird das Abblaseventil 2 mit erhöhter Verstellgeschwindigkeit in Öffnungsrichtung verstellt, bis die Sicherheitssteuerung 31 nach Rückkehr des Verdichter-Arbeitspunktes in den sicheren Kennfeldbereich wieder zurückgesetzt wird und damit das Schaltventil 2 wieder in seine Schließstellung umgeschaltet wird. Im weiteren erfolgt dann die bedarfsweise Verstellung des Abblaseventils 2 aus der zuletzt erreichten Stellung wieder durch den Regler 41 mit der langsameren Verstellgeschwindigkeit.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. When the safety controller 31 responds, 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. As a result, 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.

Für die Sicherheitssteuerung 31 und den Pumpgrenzregler 41 können vorteilhaft an sich bekannte Komponenten verwendet werden, so daß die Durchführung des Verfahrens und die Herstellung einer hierfür geeigneten Vorrichtung vergleichsweise einfach und kostengünstig sind.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.

Claims (6)

  1. Method of protecting a turbocompressor against surge by blowing off via a blow-off valve, in which a control parameter is determined from measured values at least for the compressor flow rate and the compressor discharge pressure and from predetermined or preselectable desired values, by means of which position-controlled adjustment of the blow-off valve is effected by a surge limit controller via a pressure medium by means of a pneumatic or hydraulic actuating means with a position controller, and in which the blow-off valve is moved in the opening direction at the maximum rate of adjustment by a safety means when the control parameter exceeds a safety limit value, characterised in that, upon operation of the safety means, the pressure medium for actuating the blow-off valve is discharged directly, by-passing the position controller, and that, upon resetting of the safety means, discharge of the pressure medium terminates and control is once again taken over solely by the surge limit controller and the downstream position controller.
  2. Method according to claim 1, characterised in that the output of the surge limit controller is adjusted virtually instantaneously to a value corresponding to the actual position of the blow-off valve during the adjustment of the blow-off valve effected by the safety means and by-passing the surge limit controller.
  3. Method according to claims 1 and 2, characterised in that the difference between the actual speed and position value of the compressor operating point and the associated desired speed and position value according to a preselectable desired value speed and position curve representing the limit at which surge can still be prevented is used as the control parameter, the distance of the operating point from the surge limit being used as the position and the speed of movement of the operating point relative to the surge limit in the performance field of the compressor being used as the speed.
  4. Method according to one of claims 1 to 3, characterised in that, after resetting of the safety means, control is not taken over by the surge limit controller until after a preselectable period of time.
  5. Device for carrying out the method according to claims 1 to 4, wherein the device has a surge limit controller for position-controlled adjustment of a blow-off valve via a pressure medium by means of a pneumatic or hydraulic actuating means with a position controller and a piston and cylinder unit and a safety means for moving the blow-off valve in the opening direction at the maximum rate of adjustment when necessary, characterised in that a control valve (3) is connected at the inlet side to a branch (23') which opens between the position controller and the piston and cylinder unit into a pressure medium line (23) connecting them, that the control valve (3) is connected at the outlet side to a pressure medium discharge line and that the control valve (3) can be switched into the opening position via its switch input by the safety means (31) upon operation thereof and into the closing position upon resetting thereof.
  6. Device according to claim 5, characterised in that the control valve (3) is a magnetic valve.
EP89103059A 1988-04-02 1989-02-22 Method to protect a centrifugal compressor against surge by venting via a vent valve and system to realize the method Expired - Lifetime EP0336092B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT89103059T ATE79927T1 (en) 1988-04-02 1989-02-22 METHOD OF PROTECTING A TURBOCOMPRESSOR FROM PUMPING BY MEANS OF BLOW-DOWN VIA A BLOW-OFF VALVE AND DEVICE FOR CARRYING OUT THE METHOD.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3811230 1988-04-02
DE3811230A DE3811230A1 (en) 1988-04-02 1988-04-02 METHOD FOR PROTECTING A TURBO COMPRESSOR FROM PUMPS BY BLOW-OFF WITH A BLOW-OFF VALVE, AND DEVICE FOR CARRYING OUT THE METHOD

Publications (3)

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

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EP89103059A Expired - Lifetime EP0336092B1 (en) 1988-04-02 1989-02-22 Method to protect a centrifugal compressor against surge by venting via a vent valve and system to realize the method

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US (1) US4936740A (en)
EP (1) EP0336092B1 (en)
JP (1) JPH01285697A (en)
AT (1) ATE79927T1 (en)
DE (2) DE3811230A1 (en)

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FR2666854B1 (en) * 1990-09-19 1992-12-18 Framatome Sa DEVICE FOR CONTROLLING ANTI-PUMPING MEANS OF A COMPRESSOR.
US5306116A (en) * 1992-04-10 1994-04-26 Ingersoll-Rand Company Surge control and recovery for a centrifugal compressor
DE19528253C2 (en) * 1995-08-01 1997-10-16 Gutehoffnungshuette Man Method and device for avoiding controller instabilities in surge limit controls when operating turbomachines with controllers with high proportional gain
DE19541192C2 (en) * 1995-11-04 1999-02-04 Ghh Borsig Turbomaschinen Gmbh Process for protecting a turbo compressor from operation in an unstable working area by means of a blow-off device
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
CN103038516B (en) * 2010-07-29 2015-04-01 西门子公司 Method for operating a compressor
US8726628B2 (en) 2010-10-22 2014-05-20 General Electric Company Combined cycle power plant including a carbon dioxide collection system
IT1402481B1 (en) * 2010-10-27 2013-09-13 Nuovo Pignone Spa METHOD AND DEVICE THAT PERFORM AN COMPENSATION OF THE DEAD TIME OF ANTI-PUMPING BASED ON MODEL

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Also Published As

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

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