EP0132487A2 - Procédé de régulation d'au moins deux turbo-compresseurs branchés en parallèle - Google Patents

Procédé de régulation d'au moins deux turbo-compresseurs branchés en parallèle Download PDF

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Publication number
EP0132487A2
EP0132487A2 EP84100822A EP84100822A EP0132487A2 EP 0132487 A2 EP0132487 A2 EP 0132487A2 EP 84100822 A EP84100822 A EP 84100822A EP 84100822 A EP84100822 A EP 84100822A EP 0132487 A2 EP0132487 A2 EP 0132487A2
Authority
EP
European Patent Office
Prior art keywords
control
load distribution
compressors
blow
pressure
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
EP84100822A
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German (de)
English (en)
Other versions
EP0132487B1 (fr
EP0132487A3 (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 Energy Solutions SE
Original Assignee
MAN Gutehoffnungshutte GmbH
MAN Maschinenfabrik Augsburg Nuernberg AG
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, MAN Maschinenfabrik Augsburg Nuernberg AG filed Critical MAN Gutehoffnungshutte GmbH
Publication of EP0132487A2 publication Critical patent/EP0132487A2/fr
Publication of EP0132487A3 publication Critical patent/EP0132487A3/de
Application granted granted Critical
Publication of EP0132487B1 publication Critical patent/EP0132487B1/fr
Expired 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
    • F04D27/0253—Surge control by throttling
    • 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
    • F04D27/0269—Surge control by changing flow path between different stages or between a plurality of compressors; load distribution between compressors

Definitions

  • the invention relates to a method for operating at least two turbocompressors connected in parallel, each of which is provided with a surge limit control to prevent pumping, i. H. that before reaching the surge limit when a blow-off line running parallel to this is achieved, by opening blow-off or blow-off valves, it is ensured that pumping is avoided, and the turbocompressors are also controlled jointly by load distribution regulators and individually by a pressure regulator.
  • Each flow controller has the same setpoint (output of the pressure controller) and consequently leads each machine to the operating point at which it is operated with the same throughput as the parallel machine (s).
  • the parallel machine s
  • the surge limit control is initially set in a stable manner.
  • the flow control must then react much more slowly to avoid repercussions.
  • the pressure control as a superimposed master control must in turn react much more slowly.
  • the load distribution control has the task of preventing operating states in which one machine is blowing off while other machines or another machine are driving far in the map. A regulation for setting the same flow cannot fully fulfill this task. So z. B. asymmetries in the course of the characteristic curves or the blow-off lines, as described above, are compensated for just as little as the influence of different suction pressures or an asymmetrical flow course in the pipelines.
  • turbocompressors should be able to be operated under the most favorable conditions, taking into account their individual values, and they should be able to be adapted to possible pressures and flow fluctuations as quickly as possible, the entire control system being to be safe, insensitive to failure and economical. In particular, the entire regulation should be able to be implemented using commercially available components.
  • each compressor has its own Druok control, which acts directly on the throttle valve.
  • the pressure control can thus be made in the time behavior as quickly as in the known system of the flow controller.
  • the pressure regulators are interlocked in such a way that only a maximum of one pressure regulator can be switched to automatic.
  • the other or the other is or are switched to hand, i. H. passive as long as there is no manual intervention.
  • FC load distribution controller
  • This variable is identical to the control difference x d of the surge limit control (FSC) and is available there as a signal, so it does not need to be determined or measured separately.
  • the determination of such a signal goes z. B. from German patent application P 26 23 899.3, in which a corresponding pressure-flow diagram is shown, which contains a surge line and blow-off line and operating curves of turbo compressors. Otherwise, the terms mentioned are generally known to the person skilled in the art.
  • the control difference of one machine (xd (A)) is different than that of the other machine (xd (B)).
  • the difference between these two quantities is applied as a correction quantity (actual value) to the two load distribution controllers, with a different sign.
  • the setpoint of these controllers is usually set to zero, but it can also assume other values if an asymmetry is desired.
  • the output of the load distribution controller has an additive effect on the output of the pressure controller. If there is a different load on the machines, one load distribution controller continues to open the throttle valve, while the other closes the flap of the parallel machine (s) to the same extent. Assuming linear characteristics of the throttle valves, this control process does not affect the overall throughput of the machines and thus the final pressure. In a real system, the pressure regulator only needs the asymmetries of the Readjust throttle valves.
  • the pressure controller first tracks the machine that is set to automatic. The resulting asymmetry in the machine load is recorded by the load distribution controller, which then adjusts all machines until the symmetry is reached again.
  • FIG. 3 shows such a tracking circuit. Controllers are used whose output size can be limited to an externally adjustable value. Overdriving is prevented if the output of each controller is limited to a variable that corresponds to the difference between the other manipulated variable and 100%.
  • Another possibility is to always prevent the further increase in the two manipulated variables when the throttle valve has reached its end position.
  • this can be achieved either by appropriate wiring of the controllers, but also according to the circuit diagram corresponding to FIG. 4 by a maximum selection in front of each controller.
  • An amplifier is used in order to maintain sufficient controller dynamics even with manipulated variables close to 100% and to avoid impermissible limitation of the control differences for pressure regulators and load distribution regulators.
  • a fundamentally different route can be followed if the load distribution controller is designed as a three-point step controller in accordance with the circuit diagram in accordance with FIG. 5. If the correction value exceeds the switching threshold set in the step controller, the downstream integrator is moved in the respective direction until the threshold is undershot again.
  • the correction variable is added as an additional value to the control differential of the pressure regulator.
  • the output of the pressure regulator is also connected to the tracking input of the integrator, the output of the integrator to the tracking input of the controller.
  • the correction variable acts on the throttle valve through this regulator.
  • the pressure regulator continues its output signal until both the control difference and the correction quantity are zero.
  • the integrator is switched to tracking at the same time. The step controller is thus ineffective, the integrator follows the pressure controller output without delay.
  • the pressure regulator If the pressure regulator is switched off, its output is tracked to the integrator output.
  • the integrator is adjusted by the step controller, which thus has a direct influence on the throttle valve position.
  • Switching is bumpless, since only one controller or integrator is engaged and the non-leading component is tracked to the output of the other. This also prevents overdriving.
  • the pressure regulator is to be switched to automatic, but the load distribution regulator to be manual, the correction quantity must be made zero by a control intervention.
  • the time behavior of the load distribution controller can be set either by a clock generator in the output of the step generator or by an adjustable time constant of the integrator.
  • step controller instead of the step controller, two limit levels can also be used.
  • An asymmetry can be achieved by adding a fixed value to the correction variable.
  • inventive method described above can also be used when more than two machines are installed. If only two of a number of machines are in operation, all that has to be done by means of a selection logic is to ensure that the correction variable is the difference between the control differences of the two running machines and the respective controllers are switched.
  • Figure 6 shows a diagram for the re-handling of three existing machines.
  • the correction values for each possible machine combination are formed (xd (A) - xd (B); xd (B) - xd (C); xd (A) - xd (C)).
  • each pressure regulator is subjected to two correction values.
  • the selection logic must make the correction values of all impermissible combinations zero (switches A&B, B&C and A&C).
  • the correction quantity of the selected machine combination is applied in parallel to the two associated pressure regulators. Locking the pressure regulator must ensure that only one pressure regulator can be switched to automatic mode at a time.
  • the impermissible combinations are locked by logic stages in the inputs of the load distribution controller.
  • Switching can be dispensed with entirely if it can be determined at the planning stage which of the two machines in operation controls the pressure and which is to be adjusted. In this case, the respective analog correction quantity only needs to be switched to the corresponding controller.
  • each step controller is fed in parallel to the integrators of the two machines, whose control differences occur in the correction variable.
  • the number of control commands in the direction of rising control commands is also as large as that in the direction of decreasing for the step controller outputs.
  • An average value is also formed here, which exactly causes the desired actuating behavior.
  • FIG. 7 shows a circuit diagram for the operation of three machines, the selection circuit and the other machines which are out of operation not being shown.
  • PC Pressure regulator
  • Pressure regulator B receives and pressure regulator C Integrator A receives a + command, integrator B a + and a - command and integrator C a - command.
  • this method can also be used on more than three machines.
  • the method can also be used if multi-stage machines with intermediate infeed are connected in parallel and a load distribution is required for each infeed (stage).
  • FIGS. 8-10 A much simpler circuit than that shown in FIGS. 5 to 7 is shown in FIGS. 8-10.
  • a control difference "pressure control”, ie pressure setpoint minus actual pressure value and a control difference load distribution control (balance control) is formed for each pressure regulator.
  • the control difference "load distribution control” contains, analogous to the description, all correction values that are required for the task-related adjustment of the throttle valve. If pressure and load distribution control are switched on, the two control differences add up and the controller is calibrated until the sum of all differences is zero. If a controller is to be switched off, the corresponding input variable is switched to zero by a changeover contact. During such a switchover process, the controller is briefly switched to manual.
  • a manual intervention takes place through the manual adjustment input on the pressure regulator.
  • a lock must ensure that the balance controllers of all machines operated in parallel must always be switched on together, otherwise operating cases are conceivable in which the control difference of the pressure controller has the same amount but the opposite sign of the control difference of the balance controller. If only one controller is in operation, this can lead to a simulated quasi-adjustment. If the parallel load distribution regulator is also engaged, the pressure regulator of which must be switched off, this compensates and frees it from the quasi-adjustment.
  • control according to the invention enables the operation of two or even a larger number of turbo compressors in an improved manner and in particular more safely, without the control expenditure being considerable.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Positive-Displacement Air Blowers (AREA)
EP84100822A 1983-08-01 1984-01-26 Procédé de régulation d'au moins deux turbo-compresseurs branchés en parallèle Expired EP0132487B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US06/519,097 US4560319A (en) 1983-08-01 1983-08-01 Method and apparatus for controlling at least two parallel-connected turbocompressors
US519097 2000-03-06

Publications (3)

Publication Number Publication Date
EP0132487A2 true EP0132487A2 (fr) 1985-02-13
EP0132487A3 EP0132487A3 (en) 1986-04-09
EP0132487B1 EP0132487B1 (fr) 1988-11-09

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EP84100822A Expired EP0132487B1 (fr) 1983-08-01 1984-01-26 Procédé de régulation d'au moins deux turbo-compresseurs branchés en parallèle

Country Status (4)

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US (1) US4560319A (fr)
EP (1) EP0132487B1 (fr)
JP (1) JPS6045795A (fr)
DE (1) DE3475094D1 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3937152A1 (de) * 1989-11-08 1991-05-16 Gutehoffnungshuette Man Verfahren zum optimierten betreiben zweier oder mehrerer kompressoren im parallel- oder reihenbetrieb
EP0576238A1 (fr) * 1992-06-22 1993-12-29 Compressor Controls Corporation Méthode et appareil de partage de charge pour contrôler un paramètre principal d'une station compresseur avec plusieurs compresseurs dynamiques
EP0769624A1 (fr) * 1995-10-20 1997-04-23 Compressor Controls Corporation Procédé et appareil d'équilibrage de charge entre compresseurs multiples
DE19828368A1 (de) * 1998-06-26 2000-01-13 Ghh Borsig Turbomaschinen Gmbh Verfahren zum Betreiben von Turboverdichtern mit mehreren sich gegenseitig beeinflussenden Reglern
US6880900B2 (en) 2001-05-30 2005-04-19 Toyota Jidosha Kabushiki Kaisha Brake control system and method for vehicle
RU2660216C1 (ru) * 2017-07-06 2018-07-05 Общество с ограниченной ответственностью "ГАЗПРОМ ТРАНСГАЗ МОСКВА" Система автоматического управления газоперекачивающим агрегатом "квант-р"
RU2753097C1 (ru) * 2020-08-25 2021-08-11 Общество с ограниченной ответственностью "Газпром трансгаз Ухта" Способ заполнения контура агрегата воздушного охлаждения газа

Families Citing this family (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
DE3540087A1 (de) * 1985-11-12 1987-05-14 Gutehoffnungshuette Man Verfahren zum regeln von turbokompressoren
DE3540285A1 (de) * 1985-11-13 1987-05-14 Gutehoffnungshuette Man Verfahren und einrichtung zum regeln von turbokompressoren
DE3620614A1 (de) * 1986-06-20 1987-12-23 Gutehoffnungshuette Man Verfahren zum filtern eines verrauschten signals
DE3809881A1 (de) * 1988-03-24 1989-10-12 Gutehoffnungshuette Man Regelverfahren zur vermeidung des pumpens eines turbokompressors
DE3810717A1 (de) * 1988-03-30 1989-10-19 Gutehoffnungshuette Man Verfahren zur vermeidung des pumpens eines turboverdichters mittels abblaseregelung
DE3935958A1 (de) * 1989-10-27 1991-05-02 Mtu Muenchen Gmbh Analoger mehrkanalregler
US5306116A (en) * 1992-04-10 1994-04-26 Ingersoll-Rand Company Surge control and recovery for a centrifugal compressor
US5967761A (en) * 1997-07-15 1999-10-19 Ingersoll-Rand Company Method for modulation lag compressor in multiple compressor system
US20070187086A1 (en) * 2006-02-14 2007-08-16 Anatoly Nikolayevich Ivanov Device for cutting slot-shaped seats in wells by hydro-sandblasting method
US8192171B2 (en) * 2009-01-15 2012-06-05 Ingersoll-Rand Company Compressor system
US9217370B2 (en) 2011-02-18 2015-12-22 Dynamo Micropower Corporation Fluid flow devices with vertically simple geometry and methods of making the same
JP5738262B2 (ja) * 2012-12-04 2015-06-17 三菱重工コンプレッサ株式会社 圧縮機制御装置、圧縮機システムおよび圧縮機制御方法
KR102247596B1 (ko) * 2014-01-24 2021-05-03 한화파워시스템 주식회사 압축기 시스템 및 그 제어 방법
US10030580B2 (en) 2014-04-11 2018-07-24 Dynamo Micropower Corporation Micro gas turbine systems and uses thereof
DE102016011551B4 (de) 2016-09-23 2018-05-09 Mtu Friedrichshafen Gmbh Brennkraftmaschine
DE102017211061A1 (de) * 2017-06-29 2019-01-03 Siemens Aktiengesellschaft Synchronisierungsverfahren zum Synchronisieren einer Mehrzahl von Aktoren sowie Vorrichtungen zu dessen Durchführung
CN110778519B (zh) * 2019-11-11 2021-05-18 浙江中控技术股份有限公司 一种并联压缩机机组的控制系统

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Publication number Priority date Publication date Assignee Title
GB191126618A (en) * 1911-11-28 1912-07-18 Karl Baumann Improvements relating to Centrifugal Blowers.
US3527059A (en) * 1968-12-26 1970-09-08 Phillips Petroleum Co Method of controlling parallel-operating refrigeration compressors
FR2108039A1 (fr) * 1970-09-28 1972-05-12 Westinghouse Electric Corp
US4255089A (en) * 1979-03-22 1981-03-10 Dravo Corporation Method of controlling series fans driving a variable load

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US2993640A (en) * 1956-05-22 1961-07-25 Oerlikon Engineering Company Method of and apparatus for maintaining a constant pressure at varying capacity or a constant capacity at variable pressure in a turbo-compressor
SU727874A1 (ru) * 1973-11-27 1980-04-15 Специальное Конструкторское Бюро "Газприборавтоматика" Система автоматического регулировани давлени на выходе группы совместно работающих компрессоров
SU567849A1 (ru) * 1976-04-12 1977-08-05 Предприятие П/Я А-3513 Способ противопомпажной защиты группы компрессоров
US4139328A (en) * 1977-05-25 1979-02-13 Gutehoffnungshitte Sterkrade Ag Method of operating large turbo compressors
DE2828124C2 (de) * 1978-06-27 1981-11-19 M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 4200 Oberhausen Verfahren zur Verhinderung des Pumpens von Turboverdichtern
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

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB191126618A (en) * 1911-11-28 1912-07-18 Karl Baumann Improvements relating to Centrifugal Blowers.
US3527059A (en) * 1968-12-26 1970-09-08 Phillips Petroleum Co Method of controlling parallel-operating refrigeration compressors
FR2108039A1 (fr) * 1970-09-28 1972-05-12 Westinghouse Electric Corp
US4255089A (en) * 1979-03-22 1981-03-10 Dravo Corporation Method of controlling series fans driving a variable load

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Title
ADVANCES IN INSTRUMENTATION, Band 31, Nr. 1, 1976, Seiten 585.1-585.7, ISA AC; A.E. NISENFELD et al.: "Control of parallel compressors" *

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3937152A1 (de) * 1989-11-08 1991-05-16 Gutehoffnungshuette Man Verfahren zum optimierten betreiben zweier oder mehrerer kompressoren im parallel- oder reihenbetrieb
EP0431287A1 (fr) * 1989-11-08 1991-06-12 MAN Gutehoffnungshütte Aktiengesellschaft Procédé d'opération optimal de deux ou plusieurs compresseurs travaillant en parallèle ou en série
EP0576238A1 (fr) * 1992-06-22 1993-12-29 Compressor Controls Corporation Méthode et appareil de partage de charge pour contrôler un paramètre principal d'une station compresseur avec plusieurs compresseurs dynamiques
EP0769624A1 (fr) * 1995-10-20 1997-04-23 Compressor Controls Corporation Procédé et appareil d'équilibrage de charge entre compresseurs multiples
DE19828368A1 (de) * 1998-06-26 2000-01-13 Ghh Borsig Turbomaschinen Gmbh Verfahren zum Betreiben von Turboverdichtern mit mehreren sich gegenseitig beeinflussenden Reglern
US6164901A (en) * 1998-06-26 2000-12-26 Ghh Borsig Turbomaschinen Gmbh Method and device for operating turbocompressors with a plurality of controllers that interfere one with each other
DE19828368C2 (de) * 1998-06-26 2001-10-18 Man Turbomasch Ag Ghh Borsig Verfahren und Vorrichtung zum Betreiben von zwei- oder mehrstufigen Verdichtern
US6880900B2 (en) 2001-05-30 2005-04-19 Toyota Jidosha Kabushiki Kaisha Brake control system and method for vehicle
RU2660216C1 (ru) * 2017-07-06 2018-07-05 Общество с ограниченной ответственностью "ГАЗПРОМ ТРАНСГАЗ МОСКВА" Система автоматического управления газоперекачивающим агрегатом "квант-р"
RU2753097C1 (ru) * 2020-08-25 2021-08-11 Общество с ограниченной ответственностью "Газпром трансгаз Ухта" Способ заполнения контура агрегата воздушного охлаждения газа

Also Published As

Publication number Publication date
DE3475094D1 (en) 1988-12-15
JPS6045795A (ja) 1985-03-12
EP0132487B1 (fr) 1988-11-09
EP0132487A3 (en) 1986-04-09
US4560319A (en) 1985-12-24

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