EP0332888B1 - Verfahren zum sicheren Betreiben von Turbo-Kompressoren - Google Patents

Verfahren zum sicheren Betreiben von Turbo-Kompressoren Download PDF

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Publication number
EP0332888B1
EP0332888B1 EP89103021A EP89103021A EP0332888B1 EP 0332888 B1 EP0332888 B1 EP 0332888B1 EP 89103021 A EP89103021 A EP 89103021A EP 89103021 A EP89103021 A EP 89103021A EP 0332888 B1 EP0332888 B1 EP 0332888B1
Authority
EP
European Patent Office
Prior art keywords
blow
working point
valve
compressor
velocity
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP89103021A
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German (de)
English (en)
French (fr)
Other versions
EP0332888A3 (en
EP0332888A2 (de
Inventor
Wilfried Dr.-Ing. Blotenberg
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
MAN Energy Solutions SE
Original Assignee
MAN Gutehoffnungshutte GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by MAN Gutehoffnungshutte GmbH filed Critical MAN Gutehoffnungshutte GmbH
Priority to AT89103021T priority Critical patent/ATE72304T1/de
Publication of EP0332888A2 publication Critical patent/EP0332888A2/de
Publication of EP0332888A3 publication Critical patent/EP0332888A3/de
Application granted granted Critical
Publication of EP0332888B1 publication Critical patent/EP0332888B1/de
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 the safe operation of turbo-compressors, in which the flow and delivery pressure defining the operating point of the compressor are measured continuously, whereby to prevent pumping before reaching the surge limit through the operating point of the compressor when reaching a blow-off line parallel to the surge limit by means of a blow-off control controlled opening of at least one blow-off or blow-off valve ensures that the flow does not fall below a minimum flow dependent on the delivery pressure.
  • a method of the type mentioned is known from DE-PS 2623899.
  • a safety control is superimposed on a continuous blow-off control.
  • this method has proven itself in practice, in particular with regard to protecting the compressor from pumps, it still has disadvantages.
  • the safety controller responds, ie when a static safety line running between the blow-off line and surge line through the working point is exceeded, the blow-off or blow-off valve is always fully opened, since in the known method the associated control value for the movement control of the valve jumps to the value "zero""is set.
  • the valve Even if the operating point is before the valve reaches the opening end position, the blow-off line has again exceeded the safe characteristic field area, the valve opens further since its manipulated variable is at the value "zero" and from there it can only rise slowly under the influence of the normal blow-off control. This often results in a very disadvantageous drop in pressure in the consumer network fed by the compressor.
  • the second disadvantage is that the safety line runs at a fixed distance parallel to the blow-off line or surge line and therefore only has a static effect. In order to reliably rule out that the surge point is exceeded by the working point for every conceivable operating case, the distance of the safety line from the surge limit must be relatively large. In most safety control responses, this leads to the blow-off valve opening being triggered earlier than is actually necessary, which in turn leads to energy losses and thus higher operating costs of the compressor in part-load operation.
  • a method of the type mentioned at the outset which is characterized in that the speed of the movement of the working point relative to the blow-off line or surge line is continuously determined, that when a speed-dependent minimum distance of the working point from the blow-off line or is reached or exceeded Rapid opening line, which represents the surge limit, is an opening of the relief or blow-off valve superimposed on the normal blow-off control with maximum adjustment speed and that when the operating point returns via the quick-release line, the opening movement of the valve ends and its further adjustment, starting from the last position reached, again by the normal blow-off control is taken over.
  • the opening of the blow-off valve or blow-off valve is triggered at the latest possible time, taking into account the speed of movement of the working point. This means that if the operating point continues to move after this point in time, the surge limit has not just been reached and is never exceeded. It is of course the case that at a higher speed of the operating point in the direction of the surge limit, the opening of the relief valve is triggered earlier and correspondingly at a lower speed of the operating point later.
  • the quick-opening line runs parallel to the blow-off line with a distance from the surge limit that varies depending on the current operating point speed.
  • the controller is adjusted to the current position of the relief valve and that the controller takes over the further adjustment of the relief valve essentially without jumps and bumps. This ensures that a longer settling of the control, as is the case in known control methods due to larger differences between the position of the relief valve and the control variable for the relief valve at the controller output is largely avoided. As a result, the pressure curve in the consumer network becomes much more uniform, ie the effects of disturbances are greatly dampened.
  • the determination of the speed of the working point is carried out by differentiating in time the location coordinates of the working point which vary depending on the time.
  • This method delivers the current speed of the operating point in the map with practically no delay, on the basis of which, in conjunction with the current position of the operating point in the map, a decision is made as to whether the relief valve is opened quickly or not.
  • a second possibility for determining the speed of the operating point in the characteristic diagram consists in forming a difference between the current location coordinates and location coordinates delayed by a predeterminable time period with the following division of the difference by the time period.
  • This variant requires less effort in processing the data, but has a slightly lower response speed than the variant described above.
  • a low-pass filtering of the position coordinates of the operating point which varies in position depending on the time in the characteristic diagram, is expediently carried out before the speed determination, as a result of the flow measurement values mentioned and Pressure measurements are defined.
  • the noise leads to small, brief shifts in the operating point in the Map without actual changes in the operating state of the compressor. With the filtering, these short-term fluctuations in the speed value are switched off and unnecessary triggering of the quick opening of the relief valve is avoided.
  • At least one additional operating parameter of the compressor such as speed, vane position or compressor end pressure
  • the relief valve is opened at maximum adjustment speed only if at least one of the additionally detected parameters is one Approximation of the working point to the surge limit.
  • the working point is shifted to the surge line or blow-off line is associated with a decrease in the compressor speed and / or with guide vane-regulated compressors with a closing movement of the guide vanes and with an increase in the final pressure.
  • the relief valve is opened at the maximum adjustment speed only after a predeterminable speed limit value and / or a predeterminable displacement amount by the operating point in the characteristic diagram.
  • FIG. 1 of the drawing shows, a gaseous medium to be compressed is fed through a suction line 10 to a turbo compressor 1, which conveys the compressed gaseous medium into a pressure line 11.
  • a flow measuring device 4 is installed in front of the compressor 1 in the suction line 10.
  • a pressure measuring device 5 is connected into the pressure line 11 downstream of the turbo compressor 1.
  • a blow-off line 21 branches off from it, with a blow-off valve 2 switched on.
  • the relief valve 2 is adjustable in its position by means of a valve actuation device 20.
  • the line 21 can also be returned to the suction line 10.
  • a non-return valve 3 is switched on. Behind this non-return valve 3, the compressed medium is fed through the pressure line 11 to a downstream consumer network.
  • the flow measuring device 4 By means of the flow measuring device 4, the flow flowing to the compressor 1 on the intake side is measured continuously.
  • the pressure measuring device 5 uses the pressure from the compressor 1 into the pressure line 11 pumped medium continuously measured.
  • a control difference is calculated from the measured values of the flow measurement and the pressure measurement, which is used to calculate a valve manipulated variable for the relief valve 2, more precisely its actuating device 20.
  • the measured values for the flow and the pressure define the position of the compressor operating point in the compressor map.
  • the control method ensures that the blow-off valve 2 is opened more or less as required, so that the flow through the turbo compressor 1 does not fall below a just permissible minimum flow. As far as described so far, the control method corresponds to the known prior art.
  • an operating point speed is calculated from the control difference calculated from the flow and the pressure, ie the speed at which the operating point of the compressor 1 moves in the characteristic diagram. In particular, it is determined here whether and at what speed the operating point approaches the blow-off line or surge limit. From this operating point speed and from the control difference, which represents the current position of the working point in the compressor map, a quick opening control forms control commands for the valve actuation device 20 of the relief valve 2, in order to open it if necessary with the greatest possible adjustment speed by the required amount.
  • the quick opening control system always intervenes when the operating point in the map reaches or exceeds a quick opening line that represents a speed-dependent minimum distance of the operating point from the blow-off line or surge limit. After the operating point has returned to the safe map area, the normal blow-off control with the valve manipulated variable calculation takes over the further control of the compressor 1 solely from the control difference.
  • FIG. 1 A first embodiment of the part of the method which is essential to the invention in FIG. 1 with the calculation of the operating point speed and rapid opening control is shown in FIG.
  • the control difference calculated in an earlier process step i.e. the signal that corresponds to the distance of the working point from the blow-off line and thus fixes the location coordinates of the working point is differentiated according to time (DIF).
  • DIF time
  • This differential corresponds to the speed of the operating point in the map in the direction of the surge limit or blow-off line. Speeds in other directions, especially parallel to the surge line or blow-off line, are not recorded.
  • This speed is then determined by the position of the working point, i.e. multiplied by the control difference dependent, non-linear function (FNC) (MUL).
  • FNC non-linear function
  • This product which represents a speed component, is then compared with the control difference, which represents the spatial coordinate of the working point (SUM1). If the numerical value of the speed component now exceeds the numerical value of the location coordinate, the result of the comparison (SUM1) becomes positive.
  • the subsequent logical AND operation (AND1) which has the function of a switching stage, then delivers a signal on the output side that represents a valve quick opening command. This command causes the relief valve to be adjusted in the opening direction.
  • the output of the AND operation (AND1) jumps back to the value "0" and the quick opening command is canceled. From now on, the normal blow-off control takes over the further adjustment of the blow-off valve 2.
  • the normal blow-off control more precisely the valve manipulated variable generated by it, during the addition of the new one Rapid opening control effecting rapid opening of the relief valve 2 is tracked to the current valve position thereby achieved.
  • the control diagram shown in FIG. 3 shows the block diagram from FIG. 2 with an addition, with the result that a valve quick opening command is only issued when the operating point has traveled a certain minimum distance in the characteristic diagram.
  • an integration NFI
  • LIM1 limits the positioning speed of the integration.
  • FIG. 4 shows a variant of the method in which the block diagram from FIG. 2 is supplemented by filtering.
  • the individual process steps additionally required for this consist of a limitation (LIM2) of the control difference, a subsequent integration (NFI), a summation (SUM4) and a further one logical AND operation (AND2).
  • LIM2 limitation
  • NFI subsequent integration
  • SUM4 summation
  • AND2 further one logical AND operation

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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)
EP89103021A 1988-03-18 1989-02-21 Verfahren zum sicheren Betreiben von Turbo-Kompressoren Expired - Lifetime EP0332888B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT89103021T ATE72304T1 (de) 1988-03-18 1989-02-21 Verfahren zum sicheren betreiben von turbokompressoren.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3809070A DE3809070A1 (de) 1988-03-18 1988-03-18 Verfahren zum sicheren betreiben von turbo-kompressoren
DE3809070 1988-03-18

Publications (3)

Publication Number Publication Date
EP0332888A2 EP0332888A2 (de) 1989-09-20
EP0332888A3 EP0332888A3 (en) 1990-07-25
EP0332888B1 true EP0332888B1 (de) 1992-01-29

Family

ID=6350057

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89103021A Expired - Lifetime EP0332888B1 (de) 1988-03-18 1989-02-21 Verfahren zum sicheren Betreiben von Turbo-Kompressoren

Country Status (5)

Country Link
US (1) US4938658A (enrdf_load_stackoverflow)
EP (1) EP0332888B1 (enrdf_load_stackoverflow)
JP (1) JPH01273900A (enrdf_load_stackoverflow)
AT (1) ATE72304T1 (enrdf_load_stackoverflow)
DE (2) DE3809070A1 (enrdf_load_stackoverflow)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2136975C1 (ru) * 1998-06-11 1999-09-10 ОАО "Омское машиностроительное конструкторское бюро" Устройство для регулирования перепуска воздуха из компрессора вспомогательной силовой установки

Families Citing this family (15)

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FR2666854B1 (fr) * 1990-09-19 1992-12-18 Framatome Sa Dispositif de commande de moyens d'antipompage d'un compresseur.
US5306116A (en) * 1992-04-10 1994-04-26 Ingersoll-Rand Company Surge control and recovery for a centrifugal compressor
DE19528253C2 (de) * 1995-08-01 1997-10-16 Gutehoffnungshuette Man Verfahren und Vorrichtung zur Vermeidung von Reglerinstabilitäten bei Pumpgrenzregelungen beim Betrieb von Strömungsmaschinen mit Reglern hoher Prportionalverstärkung
DE19541192C2 (de) * 1995-11-04 1999-02-04 Ghh Borsig Turbomaschinen Gmbh Verfahren zum Schutz eines Turbokompressors vor Betrieb im instabilen Arbeitsbereich mittels einer Abblaseeinrichtung
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
DE19913662A1 (de) 1999-03-25 2000-11-02 Wingas Gmbh Verfahren und Vorrichtung zur Überwachung und Regelung von Geräten und Anlagen mit einem zwei- oder mehrdimensionalen Betriebsbereich
DE10001365A1 (de) * 2000-01-14 2001-07-19 Man Turbomasch Ag Ghh Borsig Verfahren und Einrichtung zum Regeln eines Turbokompressors zur Verhinderung des Pumpens
AU2002307547A1 (en) * 2001-04-24 2002-11-05 Unit Instruments, Inc. System and method for configuring and asapting a mass flow controller
JP4528617B2 (ja) * 2002-07-19 2010-08-18 セレリティ・インコーポレイテッド マスフローコントローラにおける圧力補償のための方法および装置
US7216019B2 (en) * 2004-07-08 2007-05-08 Celerity, Inc. Method and system for a mass flow controller with reduced pressure sensitivity
KR100708388B1 (ko) * 2005-04-01 2007-04-19 주식회사 위너 차량용 엘피지 연료탱크의 연료공급장치
IT1402481B1 (it) * 2010-10-27 2013-09-13 Nuovo Pignone Spa Metodo e dispositivo che effettua una compensazione del tempo morto di anti-pompaggio basata su modello
CN110657991B (zh) * 2018-06-29 2021-05-07 中国航发商用航空发动机有限责任公司 一种航空发动机的喘振监测方法和喘振监测系统
CN115792606B (zh) * 2022-11-18 2024-04-02 苏州东剑智能科技有限公司 一种水泵电机故障检测方法、装置、设备及存储介质
CN118881620B (zh) * 2024-09-27 2025-01-17 潍柴动力股份有限公司 换向阀的控制方法、装置、程序产品和气缸控制系统

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DE1107887B (de) * 1957-04-16 1961-05-31 Power Jets Res & Dev Ltd Regler zur Pumpverhuetung bei Stroemungsverdichtern
DE1428066A1 (de) * 1963-08-30 1968-11-28 Continental Elektro Ind Ag Grenzmengenregelung an Turboverdichtern
DE2623899C3 (de) * 1976-05-28 1989-06-08 MAN Gutehoffnungshütte GmbH, 4200 Oberhausen Verfahren zum Betreiben von Turboverdichtern in der Nähe der Pumpgrenze
US4164034A (en) * 1977-09-14 1979-08-07 Sundstrand Corporation Compressor surge control with pressure rate of change control
GB2060210B (en) * 1979-10-11 1983-10-19 Borg Warner Surge suppression apparatus for compressor-driven system
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
DE3544821A1 (de) * 1985-12-18 1987-06-19 Gutehoffnungshuette Man Verfahren zum regeln von turbokompressoren zur vermeidung des pumpens
DE3544822A1 (de) * 1985-12-18 1987-06-19 Gutehoffnungshuette Man Verfahren zur pumpgrenzregelung von turbokomporessoren
DE3620614A1 (de) * 1986-06-20 1987-12-23 Gutehoffnungshuette Man Verfahren zum filtern eines verrauschten signals
US4781524A (en) * 1987-02-12 1988-11-01 Man Gutehoffnungshuette Gmbh Method and apparatus for detecting pressure surges in a turbo-compressor

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2136975C1 (ru) * 1998-06-11 1999-09-10 ОАО "Омское машиностроительное конструкторское бюро" Устройство для регулирования перепуска воздуха из компрессора вспомогательной силовой установки

Also Published As

Publication number Publication date
DE3809070C2 (enrdf_load_stackoverflow) 1992-01-09
EP0332888A3 (en) 1990-07-25
US4938658A (en) 1990-07-03
JPH01273900A (ja) 1989-11-01
EP0332888A2 (de) 1989-09-20
DE3809070A1 (de) 1989-10-26
DE58900778D1 (de) 1992-03-12
ATE72304T1 (de) 1992-02-15

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