EP2598755B1 - Procédé pour faire fonctionner un compresseur - Google Patents

Procédé pour faire fonctionner un compresseur Download PDF

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Publication number
EP2598755B1
EP2598755B1 EP11741157.9A EP11741157A EP2598755B1 EP 2598755 B1 EP2598755 B1 EP 2598755B1 EP 11741157 A EP11741157 A EP 11741157A EP 2598755 B1 EP2598755 B1 EP 2598755B1
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Prior art keywords
measurement
pressure
final pressure
suction pressure
throughput
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EP11741157.9A
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German (de)
English (en)
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EP2598755A1 (fr
Inventor
Georg Winkes
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Siemens AG
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Siemens AG
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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
    • 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
    • F04D27/0246—Surge control by varying geometry within the pumps, e.g. by adjusting vanes
    • 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

  • the controller opens a bypass valve and thus ensures a minimum distance to the pumping limit, in which the final pressure is lowered and, accordingly, the required flow rate, mass flow or volume flow is restored.
  • the so-called surge limit control protects the control of the Bypass valve the compressor from damage that would be caused by the pump, and in case of failure of any of the measuring signals involved, the protection of the machine must be guaranteed against this damage.
  • One possibility for reacting to a signal failure at the measuring points is the replacement of the disturbed measured value by the worst-case possible measured value-that is, a value which is closer to the surge limit than is actually the case.
  • the machine is still protected against pump surges, but it is possibly the most often designed as a control valve bypass valve opened unnecessarily, so that the efficiency of the system deteriorates.
  • the valve opens so far that the throughput through the compressor is reduced to an unacceptable minimum and so the usually connected by the compression process connected process can no longer be maintained.
  • the surge regulator generates a constant output signal in the event of a fault, which opens the valve so far that under any circumstances, a pump can occur. This also leads to a negative influence on the connected process.
  • the measured values measured also include a measurement of the throughput through the compressor.
  • EP 0 676 545 A2 suggests a procedure for the case of a "transmitter failure" on a similar arrangement.
  • the invention has the object to develop a fallback strategy in case of failure of one of the aforementioned measurements for the operation of a compressor of the type mentioned, which ensures an acceptable efficiency in continued operation despite a maximum of safety ,
  • the invention understands the measured values of a suction pressure measurement or final pressure measurement both the measured parameters in a unit characteristic of the physical parameter and a modification of this measured value by normalization, in particular normalization, which renders this measured value dimensionless.
  • This is expedient, for example, in the suction pressure and the final pressure, if these are normalized to the suction pressure.
  • the throughput is measured regularly by means of a differential pressure measurement via a metering orifice and can accordingly also be specified in the physical unit of a pressure and accordingly modified in the same way, particularly dimensionless, as the suction pressure and the final pressure.
  • Quantity measurement possible and the implementation of the invention with non-normalized or dimensioned measured sizes.
  • a preferred embodiment of the invention provides that in normal operation from the Saugdruck horrin and the final pressure measurement by means of the first control map, a target value for the surge limit is determined, which corresponds to a minimum value for the throughput.
  • the measurement of the angle of attack possiblysleitapparates or the speed.
  • the variation of the angle of the mecanicsleitapparates or the speed is particularly suitable for the substitute control with failed measurement of the final pressure or the inlet pressure.
  • a maximum ratio of end pressure to inlet pressure can be assigned to a specific position of the inlet guide apparatus. The same applies to the speed. In this way, each results in a particularly good approximation to the surge line for the replacement control.
  • the additional map can also be used if there should be a failure of the suction pressure measurement.
  • the minimum quantity setpoint is then formed according to the above approximation for the maximum pressure ratio.
  • the formula for the calculation of the actual values often contains the suction pressure, eg in the form V ⁇ ⁇ ⁇ p P a A .
  • An estimation without using the suction pressure can be given for example by the following formula: ⁇ p p A ⁇ ⁇ p p e * p e p A ⁇
  • FIG. 1 shows a compressor CO with the associated auxiliary systems and a drive T, which is designed here in the manner of a H semiconductorgasexpanders.
  • the compressor CO receives process fluid PF on a suction line SL at an inlet pressure PA and compresses it to a final pressure PE while delivering it to a pressure line PL.
  • the compressed process fluid PF is cooled after the compressor CO in a heat exchanger CL.
  • an input temperature TE is measured by means of a temperature measuring point TT
  • a volume flow VF is measured by means of a volume measuring point FE via a pressure difference ⁇ P of a local measuring diaphragm and the input pressure PA by means of a simple pressure measuring point PAE.
  • a counselsleitapparat ELA which is set to the angle of attack ⁇ .
  • the drive T is variable speed or an inlet guide ELA provided.
  • a quantity regulator MCTR controls the setting angle ⁇ of the inlet guide apparatus ELA by specifying a setpoint value ⁇ S for the setting angle ⁇ .
  • the actual value ⁇ C for the angle of attack ⁇ is transmitted to the quantity controller MCTR by a position transmitter ZT.
  • the final pressure PE is measured behind the heat exchanger CL by means of a pressure measuring point PEE.
  • the results of all measurements are from a control CTR detected, with part of this scheme is a surge limit control PCTR.
  • Decisive for the surge limit control is the activation of a bypass valve BV, which is designed as a control valve and controls the opening of a bypass BP, which closes the pressure line PL with the suction line SL via a defined opening short when the compressor CO threatens to the state of the pumping to reach.
  • FIG. 2 shows an operating point OP and a control line CTRL as an extract from the not completely shown control map CTFE.
  • the Y coordinate of the illustrated graph represents the ratio of end pressure PE to input pressure PA and the X coordinate represents the ratio of the differential pressure ⁇ P at the flow rate measurement to the input pressure PA.
  • the measured ratio of the final pressure PE to the input pressure PA is the basis for determining the setpoint value TV of the surge limit controller PCTR.
  • the actual value ⁇ V at the operating point OP is formed via the ratio of the differential pressure ⁇ P in relation to the input pressure PA.
  • the diagram shown essentially expresses a ratio of the compaction power on the Y-coordinate and the flow rate through the compressor CO on the X-coordinate.
  • the surge limit control PCTR opens the bypass valve BV when the operating point OP with respect to the flow rate reaches the target value TV or the surge limit line CTRL.
  • FIG. 3 shows a relationship between the angle of attack ⁇ as an input variable and minimum and maximum ratios between final pressures PE and input pressures PA shown in a replacement control map SCTFE, which is implemented by the surge limit control PCTR when the measurement of the input pressure or the final pressure or the amount fails. Based on the measurement of the angle of attack ⁇ , these minimum and maximum pressure ratios between input and output can be determined and according to the in FIG. 4 implement the sequence shown in the method according to the invention.
  • FIG. 4 shows a flowchart of the method according to the invention.
  • the method according to the invention is subdivided into four successive steps, wherein in a first step at least three measurements take place, in this case the inlet pressure PA, the final pressure PE and a differential pressure measurement ⁇ P carried out to determine the throughput. If these measurements are less than 1) trouble-free (Y), the method goes to step 2), during which the operating point OP is determined by means of a control characteristic diagram CTFE and a nominal value TF based on the difference to the control line CTRL.
  • the setpoint value TV is compared with the pressure difference ⁇ P, wherein at a larger value of ⁇ P compared to TV in a fourth step, the bypass valve BV remains closed and is otherwise opened. If a fault of one of the measurements is present in method step 1), a further measurement d) is used for the evaluation in a replacement control characteristic field SCTFE for determining a substitute setpoint value ETV. In the subsequent step 3a), a comparison is made in the same way as in step 3), here between the final pressure PE and the substitute setpoint TVE. If the final pressure PE is greater, a closing of the bypass valve BV takes place in method step 4), otherwise an opening.

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

Claims (10)

  1. Procédé pour faire fonctionner un compresseur ( CO ) ayant les mesurages installés
    a) mesurage ( PA ) de la pression d'aspiration,
    b) mesurage ( PE ) de la pression finale,
    c) mesurage ( ΔP ) du débit,
    dans lequel, dans un fonctionnement normal pendant lequel les mesurages se déroulent sans erreur, on détermine au moyen d'un premier diagramme ( CTFE ) caractéristique de régulation, à partir d'une ou de deux des grandeurs mesurées, une valeur de consigne pour un régulateur ( PCTR ) de limite de pompage, lequel compare celle-ci directement ou indirectement à la troisième grandeur de mesure, le régulateur ( PCTR ) de limite de pompage ouvrant une vanne ( BV ) de dérivation, si l'on passe en dessous ou au-dessus de la valeur ( TV ) de consigne, de manière à abaisser la pression ( PE ) finale ou à augmenter le débit dans le compresseur,
    caractérisé en ce que
    si est manquant au moins l'un des mesurages
    a) mesurage ( PA ) de la pression d'aspiration,
    b) mesurage ( PE ) de la pression finale,
    c) mesurage ( ΔP ) du débit,
    un mesurage supplémentaire d'une autre grandeur physique du processus de compression, ensemble avec une grandeur de mesure parmi les mesurages restants ou une variante de cette grandeur de mesurage, est, sur la base d'un diagramme caractéristique supplémentaire, une grandeur d'entrée pour un diagramme ( SCTFE ) caractéristique de réglage de remplacement, à partir duquel on détermine une valeur maximum ou une valeur minimum de la grandeur de mesure perturbée, valeur dont on tire parti pour la formation de la valeur de consigne dans le premier diagramme ( CTFE ) caractéristique de régulation ou qui soi-même est, comme valeur ( TV ) de consigne de remplacement, une grandeur d'entrée pour le régulateur ( PCPR ) de limite de pompage.
  2. Procédé suivant la revendication 1,
    dans lequel, dans un fonctionnement normal, on détermine au moyen du premier diagramme ( CTFE ) caractéristique de régulation, à partir de la pression ( PA ) d'aspiration et de la pression ( PE ) finale, la valeur ( TV ) de consigne pour le régulateur ( PCTR ) de limite de pompage, valeur qui correspond à une valeur minimum pour le débit, le régulateur de limite de pompage ouvrant la vanne ( BV ) de dérivation, si l'on passe en dessous de la valeur minimum pour le débit.
  3. Procédé suivant la revendication 1 ou 2,
    dans lequel le mesurage supplémentaire est le mesurage de l'angle ( α ) d'attaque d'un dispositif ( ELA ) de conduite d'entrée.
  4. Procédé suivant la revendication 1 ou 2,
    dans lequel le mesurage supplémentaire est le mesurage de la vitesse ( n ) de rotation de l'entraînement ( T ).
  5. Procédé suivant la revendication 3,
    dans lequel, si le mesurage de la pression ( PA ) d'aspiration ou le mesurage de la pression ( PE ) finale est manquant, le mesurage supplémentaire de l'autre grandeur physique est le mesurage de l'angle ( α ) d'attaque du dispositif ( ELA ) de conduite d'entrée et la pression ( PE ) finale maximum ou le rapport maximum de la pression ( PA ) d'aspiration à la pression ( PE ) finale provient de l'entrée de l'angle ( α ) d'attaque dans le diagramme caractéristique supplémentaire.
  6. Procédé suivant la revendication 4,
    dans lequel, si le mesurage de la pression ( PA ) d'aspiration ou le mesurage de la pression ( PE ) finale est manquant, le mesurage supplémentaire de l'autre grandeur physique est la mesure de la vitesse ( n ) de rotation d'entraînement ( T ) à la pression ( PE ) finale maximum ou le rapport maximum de la pression ( PA ) d'aspiration à la pression ( PE ) finale provient de l'entrée de la vitesse ( n ) de rotation dans le diagramme caractéristique supplémentaire.
  7. Procédé suivant au moins l'une des revendications 1 à 4,
    dans lequel la pression ( PA ) d'aspiration et/ou la pression ( PE ) finale et/ou le débit ( Δp ) sont, comme grandeur d'entrée d'un diagramme caractéristique, normés sur une grandeur de processus, notamment sur la pression ( PA ) d'aspiration.
  8. Procédé suivant l'une des revendications 3 à 5,
    dans lequel, si le mesurage de la pression ( PE ) finale ou de la pression d'aspiration ( PA ) est manquant, on a : p E p A ≤ p E p A ⁢ | max = f α ou p E p A ≤ p E p A ⁢ | max = f n
    Figure imgb0013
    avec :
    α = angle d'attaque des dispositifs ( ELA ) de conduite d'entrée
    n = vitesse de rotation d'entraînement ( T ).
  9. Procédé suivant la revendication 6,
    dans lequel, si le mesurage de la pression ( PA ) d'aspiration est manquant, on a en outre : Δ p p A ≤ Δ p * p E p A ⁢ | min * p E avec p E p A ⁢ | min = f α oder f n
    Figure imgb0014
  10. Procédé suivant l'une des revendications 3 à 5,
    dans lequel, si le mesurage des débits ( Δp ) est manquante, on limite par le régulateur le rapport de pression suivant : p E p A ≤ p E p A ⁢ | min * S mit S < 1
    Figure imgb0015
EP11741157.9A 2010-07-29 2011-07-18 Procédé pour faire fonctionner un compresseur Active EP2598755B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010032652 2010-07-29
PCT/EP2011/062248 WO2012013530A1 (fr) 2010-07-29 2011-07-18 Procédé pour faire fonctionner un compresseur

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EP2598755B1 true EP2598755B1 (fr) 2015-08-26

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US (1) US9410551B2 (fr)
EP (1) EP2598755B1 (fr)
CN (1) CN103038516B (fr)
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ITCO20120056A1 (it) * 2012-11-07 2014-05-08 Nuovo Pignone Srl Metodo per operare un compressore in caso di malfunzionamento di uno o piu' segnali di misura
CN105829730B (zh) * 2013-05-29 2018-09-21 西门子公司 用于运行压缩机的方法和具有压缩机的装置
JP6152062B2 (ja) * 2014-02-19 2017-06-21 三菱重工業株式会社 遠心圧縮機、ターボ冷凍機、過給機、及び遠心圧縮機の制御方法
JP6152061B2 (ja) * 2014-02-19 2017-06-21 三菱重工業株式会社 遠心圧縮機、ターボ冷凍機、過給機、及び遠心圧縮機の制御方法
CN104763662B (zh) * 2015-02-15 2016-12-07 杭州和利时自动化有限公司 变工况运行的侧流型压缩机运行空间的确定方法及系统
CN105257580A (zh) * 2015-11-17 2016-01-20 神华集团有限责任公司 用于反应气压缩机的控制系统及方法
US10208745B2 (en) * 2015-12-18 2019-02-19 General Electric Company System and method for controlling a fluid transport system
CN105571181B (zh) * 2016-01-12 2017-11-28 珠海格力电器股份有限公司 一种变频离心式冷水机组及其控制调节方法
CN116357623B (zh) * 2023-03-14 2023-11-24 深圳市氢蓝时代动力科技有限公司 一种燃料电池用离心式空压机防喘振控制方法

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DE102008058799A1 (de) * 2008-11-24 2010-06-02 Siemens Aktiengesellschaft Verfahren zum Betrieb eines mehrstufigen Verdichters

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CN103038516A (zh) 2013-04-10
WO2012013530A1 (fr) 2012-02-02
US9410551B2 (en) 2016-08-09
EP2598755A1 (fr) 2013-06-05
CN103038516B (zh) 2015-04-01
US20130129477A1 (en) 2013-05-23

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