EP0140499B1 - Verdichter mit Kontrolle des Pumpens - Google Patents

Verdichter mit Kontrolle des Pumpens Download PDF

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Publication number
EP0140499B1
EP0140499B1 EP84305463A EP84305463A EP0140499B1 EP 0140499 B1 EP0140499 B1 EP 0140499B1 EP 84305463 A EP84305463 A EP 84305463A EP 84305463 A EP84305463 A EP 84305463A EP 0140499 B1 EP0140499 B1 EP 0140499B1
Authority
EP
European Patent Office
Prior art keywords
surge
compressor
signal
control
line
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
Application number
EP84305463A
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English (en)
French (fr)
Other versions
EP0140499A2 (de
EP0140499A3 (en
Inventor
Donald Dziubakowski
Jeremiah Shaffer
Marion A. Keyes
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.)
Babcock and Wilcox Co
Original Assignee
Babcock and Wilcox Co
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 Babcock and Wilcox Co filed Critical Babcock and Wilcox Co
Publication of EP0140499A2 publication Critical patent/EP0140499A2/de
Publication of EP0140499A3 publication Critical patent/EP0140499A3/en
Application granted granted Critical
Publication of EP0140499B1 publication Critical patent/EP0140499B1/de
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
    • 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
    • F04D27/0284—Conjoint control of two or more different functions

Definitions

  • This invention relates to surge control systems for compressors and to methods of controlling surge in compressors.
  • FIG. 1a Three common forms of presently used surge control lines are shown in Figures 1a to 1c of the accompanying drawings.
  • the one position of this line is parallel to the surge limit line ( Figure 1a).
  • the surge control line should be set as close to the surge limit line as possible. Setting the control line with a slope less than that of the limit line ( Figure 1b) can lead to excess recirculation at high pressures, and surge at low pressures during stopping and startup.
  • the third method is to select a minimum safe volumetric flow, and set a vertical control line (Figure 1c). This can lead to excess recirculation at low pressures, and surge at high pressures. Many systems measure flow in the discharge without correcting for suction conditions. This gives maximum recirculation with minimum surge protection.
  • control is accomplished by opening a bypass valve around the . compressor or blowing off gas to atmosphere to maintain minimum flow through the compressor. Since bypassing or blowing off gas wastes power, it is desirable to determine surge flow as accurately as possible to avoid bypassing gas unnecessarily while maintaining safe operation. However, determining surge flow is often not a simple matter, but a complex one. Surge flow for a compressor is not a fixed quantity, but is related to other variables. Where other variables substantially affect surge flow, they must be measured and included in the surge system. However, present surge systems control surge only as a function of surge control line and make no provisions for anticipatory action from a controlled variable by way of a feed forward signal of such variable.
  • One such system is responsive to a first signal indicative of the pressure differential across an orifice in an inlet line of the compressor and a second signal indicative of the differential pressure across the compressor to control a surge condition by controlling blowing off to atmosphere.
  • a centrifugal compressor having a surge control system, the surge control system being responsive to a first signal indicative of the pressure differential across an orifice in an inlet line of the compressor and a second signal indicative of the differential pressure across the compressor to control a surge condition, and the surge control system being characterised by:
  • the invention also provides a method of controlling surge in a centrifugal compressor, the method employing a first signal indicative of the pressure differential across an orifice in an inlet line of the compressor and a second signal indicative of the differential pressure across the compressor, and the method being characterised by:
  • a preferred embodiment of the present invention described hereinbelow solves or at least alleviates the problems associated with prior art surge controls by providing a surge control system for a compressor which will anticipate a surge condition in advance of the normal surge control line and will initiate anti-surge action prior to that initiated by the surge control line.
  • a feed forward control signal from a controlled variable other than one used to establish the surge control line is utilised to establish a second or anticipatory surge control line which is offset from the main surge control line and which will initiate anti-surge protection in advance of the main surge control line.
  • This second surge control line will provide a variably offset control point from the main surge control line which will depend on the variation of the controlled variable.
  • a large change in the controlled variable will provide a larger offset than a small change and will give more advanced warning of an oncoming surge.
  • the preferred surge control.system thus has an advanced warning capability of an oncoming surge condition, and has more advance warning for larger anticipated surge conditions.
  • Figure 2 of the drawings shows a parallel compressor system 10 having a reciprocating compressor 12 parallel connected to a centrifugal compressor 14 used to provide an output pressure at an output line 16.
  • the reciprocating compressor 12 acts as a base load machine and can operate normally in one of two different capacities; 50% and 100% of its output pressure. This change of capacity from 100% to 50% initiates a surge condition in the compressor 14 and forms the basis of the advance warning system for a surge control system 18.
  • the centrifugal compressor 14 acts as a booster in the parallel arrangement, and because it is a dynamic machine (vs positive displacement like the reciprocating compressor 12) it has the potential of surging because of the decrease in flow.
  • This potential surge condition is provided as an input along a line 22 to the surge control system 18 which, as may be best seen in Figure 4, establishes an offset anticipatory surge control line 24 offset from the usual surge control line 26.
  • control of the bypass valve 28 allowing the bypass of flow across the centrifugal compressor along a line 30 is initiated by the surge control system 18 prior to the surge being initiated across the centrifugal compressor 14.
  • the surge control system 18 is schematically depicted in SAMA Standard RC22-11-1966 notation with the symbols applicable to mechanical, pneumatic, or electronic control systems.
  • Measured variables llPo and AP represent, respectively, the pressure differentials across an orifice 32 in an inlet line 34 of the centrifugal compressor 14 and the differential pressure across the centrifugal compressor. These measured variables are inputted into a function generator 36 which develops an output at a line 40 representative of the surge control line 26 which is substantially parallel to a compressor surge line 38 and a predetermined distance K to the right of the surge line 38.
  • a comparison station 42 compares the surge control line output developed at the line 40 with the measured speed S T of the centrifugal compressor 14, thus locating the intersection point 44 of a particular compressor rotation speed performance line N, and the surge control line 26.
  • This intersection point 44 is transmitted along a line 46 to an adding station 48 where the anticipatory surge signal is added from the line 22.
  • This anticipatory signal is from a process variable; namely, a manual or automatic demand variation on the base load, which will cause the surge condition.
  • the greater the signal from this process variable the greater the additive signal to the summing station 48 and the greater the offset of the anticipatory surge control line 24 from the main surge control line 26.
  • the end result of the summing station 48 is to move the point 44 to a point 50 on the line 24.
  • This point 50 defines a certain flow rate of the compressor 14which is compared in a difference station 52 with an actual measured compressor flow rate F T supplied along a line 54 to the difference station 52.
  • the output of the difference station 52 is provided along a line 55 to a proportional and integral action controller 56 having a predetermined set point which will then control the final control element 28; namely, the valve controlling the amount of bypass in the line 30 to stop the surge condition by allowing the starved compressor 14 inlet 34 to utilise compressor 14 outlet fluid from a line 58.
  • the proportional plus integral controller 56 has an antiwindup feature.
  • the antiwindup feature is necessary due to the nature of the proportional and integral functions. Normally, the compressor 14 operates in an area some distance from the surge control line 16, resulting in an offset between the measurement and the set point of the controller 56. As a result, the output signal winds up to its high or low limit.
  • Antiwindup adjusts the integral loading to shift the proportional band to the same side of the control line that the measurement is on when the controller reaches its output limit. Then, if the control line is approached rapidly, the measurement enters the proportional band and control starts before the valve reaches the control line. Therefore, overshoot is eliminated.
  • Derivative control is not used, because it can open the anti-surge valve far from the surge line and can cause system oscillations. Rapid oscillations in flow, even in the safe operating zone, can cause the valve to open because of. the characteristics of the derivative response.
  • the controller 56 will commence to control the valve 28 to open to offset an incipient surge condition. This is the normal mode of control. Because of the anticipatory feed forward signal along the line 22 to the summing station 48, this control of the surge condition will occur before the compressor 14 begins to see the effects and large or small surge causing conditions are easily taken care of by providing earlier anticipation for larger surge conditions.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Control Of Positive-Displacement Air Blowers (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Claims (9)

1. Zentrifugalverdichter (14) mit einem Pumpkontrollsystem (18), wobei das Pumpkontrollsystem (18) auf ein erstes Signal anspricht, welches eine Anzeige für die Druckdifferenz (AP.) über einer Blendenöffnung (32) in einer Einlaßleitung (34) des Verdichters (14) ist, sowie auf ein zweites Signal anspricht, welches eine Anzeige des Differenzdruckes (AP") über den Verdichter (14) ist, um einen Pumpzustand zu kontrollieren, und wobei das Pumpkontrollsystem gekennzeichnet ist durch:
erste Signalerzeugende Einrichtungen (36, ST, 42), welche aufweisen: einen Funktionsgenerator (36), der auf die ersten und zweiten Signale anspricht, um eine Ausgangsgröße bereitzustellen, die einer Hauptpumpkontrollkurve (26) entspricht, welche im wesentlichen parallel zu einer Pumpkurve (38) des Verdichters (14) verläuft und, ausgedrückt in Einheiten der Durchflußrate, um einen vorbestimmten Abstand (K) von dieser beabstandet ist; und eine Vergleichsstation (42), welche im Betrieb den Ausgangswert der Hauptpumpkontrollkurve mit einem Signal vergleicht, welches eine Anzeige der Geschwindigkeit (ST) des Verdichters (14) ist, um ein Signal zu erzeugen, welches einen Punkt (44) des Betriebes des Zentrifugalverdichters auf der Hauptpumpkontrollkurve darstellt;
zweite Signalerzeugungseinrichtungen (20, 22) zum Bereitstellen eines Vorwärtsschubsteuersignales einer Prozeßvariablen, welche möglicherweise einen Pumpzustand in dem Zentrifugalverdichter (14) verursacht;
einer Summiereinrichtung (48) zum Kombinieren der Signale aus der ersten Signalerzeugungseinrichtung (36, ST, 42) und der zweiten Signaleinrichtung (20, 22), um bereits im Vorgriff eine Pumpkontrollkurve (24) bereitzustellen, welche gegenüber der Hauptpumpkontrollkurve (26) der ersten Signalerzeugungseinrichtung proportional zur Größe des Signals von der zweiten Signalerzeugungseinrichtung versetzt ist, sowie ein Steuersignal, welches eine Anzeige hierfür ist; und
eine Bypaßventilsteuereinrichtung (56), welche mit der Summiereinrichtung (48) verbunden ist, um den Betrag des Bypasses in einer Bypaßleitung (30), welche in Überbrückung des Zentrifugalverdichters (14) angeschlossen ist, unter Ansprechen auf das Steuersignal aus der Summiereinrichtung.
2. Zentrifugalverdichter nach Anspruch 1, wobei die zweite Signalerzeugungseinrichtung (20, 22) eine Kontrollstation (20) aufweist, um die Belastungsbedingungen des Zentrifugalverdichters (14) zu verändern.
3. Zentrifugalverdichter nach Anspruch 1, wobei:
ein Kolbenverdichter (12) parallel zu dem Zentrifugalverdichter (14) angeschlossen ist; und
die zweite Signalerzeugungseinrichtung (20, 22) eine Kontrollstation (20) zum Verändern des Ausgangsdruckes des Kolbenverdichters (12) aufweist, sowie eine Steuerleitung (22), welche zwischen der Kontrollstation (20) und der Summiereinrichtung (48) angeschlossen ist, um zu erlauben, daß die Pumpkontrollkurve (24) im Vorgriff durch die Druckänderungsbedingungen an dem Kolbenverdichter (12) versetzt wird.
4. Zentrifugalverdichter nach Anspruch 1, 2 oder 3, wobei eine Differenzstation zwischen der Summiereinrichtung (48) und der Bypaßventilsteuereinrichtung (56) angeschlossen und so betreibbar ist, daß sie ein Signal (54), welches eine Anzeige des Verdichterflusses ist, mit dem Kontrollsignal von der Summiereinrichtung (48) kombiniert, um ein kaskadenartiges (stufenweises) Signal für die Kontrolleinrichtung (56) bereitzustellen und so einen vorbestimmten Fluß durch den Zentrifugalverdichter (14) sicherzustellen.
5. Verfahren zum Kontrollieren des Pumpens in einem Zentrifugalverdichter (14), wobei das Verfahren ein erstes Signal verwendet, welches eine Anzeige für die Druckdifferenz (OPa) über einer Blendenöffnung (32) in einer Einlaßleitung (34) des Verdichters (14) ist, sowie unter Verwendung eines zweiten Signales, welches eine Anzeige des Differenzdruckes (ΔPc) über dem Verdichter (14) ist, wobei das Verfahren gekennzeichnet ist durch:
Bereitstellen (36) eines Ausgangssignales, welches, als Funktion der ersten und zweiten Signale, representativ für eine Verschiebung einer Hauptpumpkontrollkurve (26) gegenüber einer Pumpkurve (38) des Verdichters (14) ist, ausgedrückt in Einheiten der Durchflußrate,
Vergleichen (42) des Ausgangswertes für die Hauptpumpkontrollkurve mit einem Signal, welches eine Anzeige für die Geschwindigkeit (ST) des Verdichters (14) ist, um ein Signal zu erzeugen, welches einen Punkt (44) des Zentrifugälverdichterbetriebes auf der Hauptpumpkontrollkurve identifiziert bzw. festlegt,
Erzeugen eines Steuersignales für einen Vorwärtsschub, welches eine Funktion einer Systemvariablen ist, die möglicherweise einen Pumpzustand in dem Verdichter (14) verursacht, und
Bereitstellen (48) einer Pumpkontrollkurve (24) im Vorgriff, welche gegenüber der Hauptpumpkontrollkurve (26) versetzt ist als Funktion des Signales, welches einen Punkt (44) des Zentrifugalverdichterbetriebes auf der Hauptpumpkontrollkurve identifiziert, sowie des erzeugten Steuersignales für die Zufuhr in Vorwärtsrichtung.
6. Verfahren nach Anspruch 5, wobei die Hauptpumpkontrollkurve (26) im wesentlichen parallel zur Pumpkurve (38) bereitgestellt wird und, ausgedrückt in Einheiten der Durchflußrate, um einen vorbestimmten Betrag (K) gegenüber dieser versetzt ist.
7. Verfahren nach Anspruch 6, wobei die vorweggenommene Pumpkontrollkurve (Pumpkontrollkurve im Vorgriff) (24) gegenüber der Hauptpumpkontrollkurve (26), ausgedrückt in Einheiten der Durchflußrate, um einen Betrag versetzt ist, der proportional der Größe des erzeugten Steuersignales für die Zufuhr in Vorwärtsrichtung ist.
8. Verfahren nach Anspruch 5, 6 oder 7, wobei ein Kolbenverdichter (12) parallel zu dem Zentrifugalverdichter (14) montiert ist und schaltbaren Druckausgangsbetrieb aufweist, wobei das Steuersignal für die Zufuhr in Vorwärtsrichtung ein Signal ist, welches den Zustand des schaltbaren Druckausganges steuert bzw. überwacht.
9. Verfahren nach Anspruch 8, wobei ein Ventil (28) zum Steuern des Fluidflusses in einer Bypaßleitung (30) in Überbrückung des Zentrifugalverdichters (14) entsprechend der relativen Lage eines gemessenen Punktes bezüglich der vorweggenommenen Pumpkontrollkurve (24) gesteuert wird.
EP84305463A 1983-10-07 1984-08-10 Verdichter mit Kontrolle des Pumpens Expired EP0140499B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US53977383A 1983-10-07 1983-10-07
US539773 1983-10-07

Publications (3)

Publication Number Publication Date
EP0140499A2 EP0140499A2 (de) 1985-05-08
EP0140499A3 EP0140499A3 (en) 1986-07-16
EP0140499B1 true EP0140499B1 (de) 1990-05-09

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EP84305463A Expired EP0140499B1 (de) 1983-10-07 1984-08-10 Verdichter mit Kontrolle des Pumpens

Country Status (11)

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EP (1) EP0140499B1 (de)
JP (1) JPS6093197A (de)
KR (1) KR870001551B1 (de)
AU (1) AU563560B2 (de)
BR (1) BR8403336A (de)
DE (1) DE3482204D1 (de)
ES (1) ES8602208A1 (de)
HK (1) HK83690A (de)
IN (1) IN162594B (de)
MX (1) MX160411A (de)
SG (1) SG64390G (de)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
US5709526A (en) * 1996-01-02 1998-01-20 Woodward Governor Company Surge recurrence prevention control system for dynamic compressors
EP2414748B1 (de) 2009-03-30 2019-11-27 TMEIC Corporation System und verfahren zur überspannungsregelung bei einem verdichter
NO333438B1 (no) * 2010-07-14 2013-06-03 Statoil Asa Fremgangsmate og apparat for sammensetningsbasert kompressorkontroll og ytelsesovervaking.
CN102635565B (zh) * 2012-03-30 2014-10-15 西安陕鼓动力股份有限公司 一种透平压缩机防喘振曲线动态偏置的方法
CN113591223B (zh) * 2021-08-09 2024-01-23 同济大学 一种燃料电池车用离心压缩系统喘振边界预测方法

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5812477A (ja) * 1981-07-15 1983-01-24 Hitachi Ltd 固体撮像素子

Also Published As

Publication number Publication date
JPH0350919B2 (de) 1991-08-05
KR850003769A (ko) 1985-06-26
IN162594B (de) 1988-06-18
JPS6093197A (ja) 1985-05-24
AU563560B2 (en) 1987-07-16
AU3274984A (en) 1985-04-18
ES534704A0 (es) 1985-11-16
BR8403336A (pt) 1985-06-18
MX160411A (es) 1990-02-19
KR870001551B1 (ko) 1987-09-02
DE3482204D1 (de) 1990-06-13
SG64390G (en) 1990-09-07
EP0140499A2 (de) 1985-05-08
EP0140499A3 (en) 1986-07-16
HK83690A (en) 1990-10-25
ES8602208A1 (es) 1985-11-16

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