EP0222382A2 - Procédé de réglage de turbocompresseurs - Google Patents

Procédé de réglage de turbocompresseurs Download PDF

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Publication number
EP0222382A2
EP0222382A2 EP86115702A EP86115702A EP0222382A2 EP 0222382 A2 EP0222382 A2 EP 0222382A2 EP 86115702 A EP86115702 A EP 86115702A EP 86115702 A EP86115702 A EP 86115702A EP 0222382 A2 EP0222382 A2 EP 0222382A2
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EP
European Patent Office
Prior art keywords
controller
blow
differential
changed
signal
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP86115702A
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German (de)
English (en)
Other versions
EP0222382B1 (fr
EP0222382A3 (en
Inventor
Wilfried Dipl.-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 Turbo AG
Original Assignee
MAN Gutehoffnungshutte GmbH
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Publication date
Application filed by MAN Gutehoffnungshutte GmbH filed Critical MAN Gutehoffnungshutte GmbH
Publication of EP0222382A2 publication Critical patent/EP0222382A2/fr
Publication of EP0222382A3 publication Critical patent/EP0222382A3/de
Application granted granted Critical
Publication of EP0222382B1 publication Critical patent/EP0222382B1/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

Definitions

  • the invention relates to a method for regulating turbo compressors of the type specified in the preamble of claim 1.
  • the method according to the invention is particularly suitable for the so-called point limit control for preventing the pumping of a compressor. But this can also apply to other regulations such as Anti-choke control, turbine speed control, etc. can be used.
  • a method of the type mentioned for the surge limit control is known from the publication "Turbolog- the electronic control system for GHH turbomachinery” in News for Mechanical Engineering No. 3, May 82 and also from US-PS 41 42 838.
  • a method of the type mentioned, in which the differentiation is realized by subtracting the delayed signal from the undelayed signal, is also known from DE-PS 28 28 124.
  • Pumps are understood to mean an unstable behavior of a turbo compressor in which intermittent or periodically the fluid flows back from the pressure side to the suction side. This behavior occurs when the throughput is too low or the pressure ratio between the compressor inlet and outlet is too high.
  • the so-called surge limit line separates the stable from the unstable area in the map of the compressor.
  • the surge limit control ensures that when the instantaneous operating point approaches the surge limit line or a blow-off line running parallel to this at a safety distance, a blow-off or blow-by valve is opened at the compressor outlet.
  • this method it is also known to change the control behavior of the controller which generates the control signal for the blow-off valve as a function of the position of the operating point in that the control gain is increased non-linearly when the blow-off line is exceeded.
  • controllers With controls of this type, the use of controllers with a control component that differentiates the input signal encounters various difficulties.
  • One of these difficulties is the fact that an actual signal, which is derived from the flow, has a very high superimposed noise level and is therefore difficult to differentiate. This difficulty is less pronounced if the actual value signal is derived from the final pressure.
  • the invention is based on the object of developing a method of the type specified so that it offers the possibility of a control with differential behavior which is effective and precisely in the vicinity of the surge line and is as insensitive as possible to noise.
  • the advantage is achieved that the differentiating effect can be increased in a targeted manner when the working point is close to the surge line, so that even small changes in the actual value signal can lead to a rapid response of the controller.
  • the advantage is achieved that the differentiating effect can be used selectively when the working point approaches the surge limit line, that is to say in the “dangerous” direction.
  • the pressure difference in front of and behind a throttle orifice is detected on the intake side of a compressor K by a first actual value transmitter 1, which pressure is simultaneously a measure of the intake volume flow or the compressor throughput. From a second actual value transmitter 3, the final pressure P2 is detected at the compressor outlet.
  • a computer 11 with associated memory 13 forms the coordinates of the working point in the map determined by the throughput and the final pressure / suction pressure ratio from the actual values and compares them with a stored blow-off line A specified in the map.
  • end and Suction pressure can be detected. To simplify matters, however, it can be assumed that the suction pressure is constant and is therefore not measured continuously.
  • a setpoint signal for the flow is generated, which is compared with the actual value in the subtractor 5 and an input signal for a controller 7 is formed therefrom.
  • the controller 7 has a proportional part 7a, a differential part 7b and an integral part 7c.
  • the controller output variable serves as a control signal for a relief valve 9 at the compressor outlet.
  • a control element In the memory 13 there is also the slope of the compressor characteristic curve K of constant speed and / or constant blade position or constant throttle for each operating point flap position stored in the entrance.
  • a control element At the value of the slope of the compressor characteristic curve belonging to the current operating point, a control element generates a control signal by means of which the time constant T D effective for the differentiation in the differential part 7b is changed in such a way that the differentiating effect of the time constant is proportional to the increase in the compressor characteristic curve. This ensures that the differential portion of the controller 7 has approximately the same effectiveness in the entire characteristic.
  • the differentiating time constant T D can also be varied depending on the distance of the current working point from the blow-off line, again in such a way that the differentiating effect is increased with a decreasing distance between the blow-off line and the working point and vice versa.
  • the size of the differentiating effect ie the proportion of the differential part 7b
  • the size of the differentiating effect can be changed in comparison to the proportional part 7a and integral part 7c of the controller.
  • the size of the differentiating effect can be adjusted depending on the slope of the blow-off line or the value of the final pressure. It is also possible to switch the differential component 7b on or off depending on a limit value in the controller output. For example, the differential component 7b can be switched off when the controller output signal is 100% or Control difference reaches another predetermined value that corresponds to a certain distance from the blow-off line.
  • the differential portion 7b of the controller can also be designed to move in one direction, e.g. is effective when the input signal rises, that is to say can only emit a positive but not a negative output signal.
  • the differentiation time constant does not need to be controlled exactly in accordance with the actual slope of the characteristic curve. Rather, simplifications are possible.
  • a simplification results when the slope of the characteristic curves depends on one of the map coordinates, that is to say on the pressure or on the flow, and the characteristic curves are only shifted parallel to larger flows or pressures. This is the case when the characteristic curves 2 open relatively steeply into the surge limit in the area of lower speeds or guide vane positions, but flatter in the upper area. Even if the characteristic curves are not completely congruent, in many cases an approximation by parallel displacement of a characteristic curve is permitted.
  • the slope of the characteristic curve and thus the size of the differentiation time constant T D only depends on the pressure P or pressure flow Vab.
  • the course of the characteristic curve can either be stored in a digital memory or else can be predetermined analogously in a function generator 14, which is indicated by dashed lines in the drawing. The entrance of this The function generator is the pressure, the output directly the size T D.
  • the function is not ideally simulated in the function generator, but in an approximation by straight line sections.
  • the simplest case is a straight line consisting of two sections. This can be realized very simply by switching the value for T D to another value from a predetermined pressure.
  • the function generator 14 delivering the quantity T D can be adjusted depending on the control difference applied to the subtractor 5.
  • simplifications are also possible for this function generator, starting with a simple switchover of the size T D between two values over several straight line sections up to a polygon.
  • the location of the working point by detecting the final pressure and of the throughput is determined, other variables such as the pressure ratio between the final and suction pressure, the speed, the guide vane position, the power, the input signal of the controller or the output signal of a process controller can be used for the detection of the operating point or for the definition of the map will.
  • the map can be determined by other parameters, such as the adiabatic delivery head and the intake volume flow. In any case, the surge line has a clear course in the map.
  • a variant is described below in which the differentiating effect of the controller is also influenced, but not by changing the time constant, but by adding further function blocks.
  • the variant described here is particularly suitable for controls in which one of the input signals has signal noise, i.e. a high-frequency, low-amplitude noise signal is superimposed on the input signal. A direct differentiation of this input signal could therefore under certain circumstances result in the noise signal being amplified considerably.
  • FIG. 2 shows a modified PID controller in which the suppression of the differentiating effect in the undesired direction is achieved by introducing a limiter 19 at the output of the differentiating element 7b.
  • the limiter 19 is designed in such a way that only the signals of the differentiating element which cause the operating point to be shifted in the direction of the stability range are passed.
  • a one-way retarder 17 can be inserted in front of the differentiating element.
  • Fig. 3 the operation of the delay 17 is shown based on a possible input signal and the resulting output signal.
  • the one-way retarder is a component whose output signal falls in one direction (eg in one direction) of the signals) initially follows the input signal without delay until the input signal reaches a relative minimum. A subsequent rise in the input signal, even if it occurs quickly, leads to a relatively slow rise in the output signal, the rate of rise being determined by a predetermined, possibly adjustable time constant.
  • the output signal of the delay 17 follows the input signal in this direction only with a delay. As soon as the input signal reaches the signal level of the output signal again, the output signal follows the input signal until a new minimum value is assumed.
  • the output signal of the delay 17 thus always remains at or in the vicinity of the smallest input value.
  • the remaining noise component is significantly reduced by this arrangement, since only brief signal changes, which always occur when the input variable takes on a new, even smaller minimum value, are passed on to the differentiating circuit.
  • the delay 17 has a finite time constant in the direction of increasing signals in order to give the system the opportunity to return to normal after reaching an extreme minimum value once or to track the output of the delay 17 as the useful signal increases.
  • the slight influence of the rising edge of the off To avoid the output signal of the delay 17, which is registered by the differentiator 7b, on the manipulated variable, the limiter 19 already mentioned can be connected downstream of the differentiator 7b.
  • the dead time element 17 has the effect that only the signals whose signal lengths exceed the dead time are passed on.
  • Two alternatives are provided for the design of the dead time element 21: In the first alternative, the signal is blocked for the duration of the dead time and only then passed on to the output without delay. In the second alternative, the signal is passed on delayed by the dead time if it has been present at the input during the entire dead time. This has the advantage that the signal curve of the differentiating element is not lost during the dead time, but is added to the manipulated variable delayed by the dead time.

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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)
EP86115702A 1985-11-12 1986-11-12 Procédé de réglage de turbocompresseurs Expired - Lifetime EP0222382B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19853540087 DE3540087A1 (de) 1985-11-12 1985-11-12 Verfahren zum regeln von turbokompressoren
DE3540087 1985-11-12

Publications (3)

Publication Number Publication Date
EP0222382A2 true EP0222382A2 (fr) 1987-05-20
EP0222382A3 EP0222382A3 (en) 1988-01-13
EP0222382B1 EP0222382B1 (fr) 1990-09-26

Family

ID=6285760

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86115702A Expired - Lifetime EP0222382B1 (fr) 1985-11-12 1986-11-12 Procédé de réglage de turbocompresseurs

Country Status (4)

Country Link
US (1) US4810163A (fr)
EP (1) EP0222382B1 (fr)
JP (1) JPS62113890A (fr)
DE (2) DE3540087A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0328729A2 (fr) * 1988-02-18 1989-08-23 MAN Gutehoffnungshütte Aktiengesellschaft Procédé et dispositif pour contrôler les compresseurs centrifuges

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3809070A1 (de) * 1988-03-18 1989-10-26 Gutehoffnungshuette Man Verfahren zum sicheren betreiben von turbo-kompressoren
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
IT1255836B (it) * 1991-10-01 1995-11-17 Procedimento per la sorveglianza del limite di pompaggio di turbocompressori a piu' stadi e refrigerazione intermedia
US5599161A (en) * 1995-11-03 1997-02-04 Compressor Controls Corporation Method and apparatus for antisurge control of multistage compressors with sidestreams
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
DE10001365A1 (de) * 2000-01-14 2001-07-19 Man Turbomasch Ag Ghh Borsig Verfahren und Einrichtung zum Regeln eines Turbokompressors zur Verhinderung des Pumpens
DE10144018A1 (de) * 2001-09-07 2003-03-27 Linde Ag Verfahren zum Regeln eines Verdichtersatzes
DE10304063A1 (de) 2003-01-31 2004-08-12 Man Turbomaschinen Ag Verfahren zum sicheren Betreiben von Turbokompressoren mit einer Pumpgrenzregelung und einem Pumpgrenzregelventil

Citations (2)

* 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
DE2828124A1 (de) * 1978-06-27 1980-01-10 Gutehoffnungshuette Sterkrade Verfahren zur verhinderung des pumpens von turboverdichtern

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2623899B2 (de) * 1976-05-28 1979-11-29 Gutehoffnungshuette Sterkrade Ag, 4200 Oberhausen Verfahren zum Betreiben von Turboverdichtern in der Nähe der Pumpgrenze
US4139328A (en) * 1977-05-25 1979-02-13 Gutehoffnungshitte Sterkrade Ag Method of operating large turbo compressors
DE2735246C2 (de) * 1977-08-04 1985-07-18 Siemens AG, 1000 Berlin und 8000 München Regeleinrichtung für einen Turboverdichter
DE2739229C3 (de) * 1977-08-31 1980-07-10 Siemens Ag, 1000 Berlin Und 8000 Muenchen Regeleinrichtung für einen Turboverdichter
DE2812820C2 (de) * 1978-01-31 1986-04-03 BBC Aktiengesellschaft Brown, Boveri & Cie., Baden, Aargau Regeleinrichtung für eine Dampfturbine
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
DE3105376C2 (de) * 1981-02-14 1984-08-23 M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 4200 Oberhausen Verfahren zum Betreiben von Turboverdichtern
US4640665A (en) * 1982-09-15 1987-02-03 Compressor Controls Corp. Method for controlling a multicompressor station
US4560319A (en) * 1983-08-01 1985-12-24 MAN Maschinenfabrik Unternehmensbereich GHH Sterkrade Method and apparatus for controlling at least two parallel-connected turbocompressors
US4562531A (en) * 1983-10-07 1985-12-31 The Babcock & Wilcox Company Integrated control of output and surge for a dynamic compressor control system
US4627788A (en) * 1984-08-20 1986-12-09 The Babcock & Wilcox Company Adaptive gain compressor surge control system
US4586870A (en) * 1984-05-11 1986-05-06 Elliott Turbomachinery Co., Inc. Method and apparatus for regulating power consumption while controlling surge in a centrifugal compressor

Patent Citations (2)

* 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
DE2828124A1 (de) * 1978-06-27 1980-01-10 Gutehoffnungshuette Sterkrade Verfahren zur verhinderung des pumpens von turboverdichtern

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
DE-Publikation "Turbolog- Das elektronische Regelsystem für GHH- Turbomaschinen"- Sonderdruck aus Nachrichten für den Maschinenbau 5/82 *
PROCEEDINGS OF THE 6TH CRANFIELD FLUIDICS CONFERENCE, Cambridge, 26.-28. Mai 1974, Seiten H6/57-H6/68, BHRA Fluid Engineering, Granfield, GB; R. RIMMER: "Fluidic surge prevention unit for jet engines" *

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0328729A2 (fr) * 1988-02-18 1989-08-23 MAN Gutehoffnungshütte Aktiengesellschaft Procédé et dispositif pour contrôler les compresseurs centrifuges
EP0328729A3 (en) * 1988-02-18 1990-07-18 Man Gutehoffnungshutte Aktiengesellschaft Method and system to control centrifugal compressors

Also Published As

Publication number Publication date
EP0222382B1 (fr) 1990-09-26
US4810163A (en) 1989-03-07
DE3674540D1 (de) 1990-10-31
EP0222382A3 (en) 1988-01-13
JPS62113890A (ja) 1987-05-25
DE3540087A1 (de) 1987-05-14

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