EP0335105B1 - Procédé pour éviter le pompage d'un compresseur centrifuge par le contrôle d'échappement - Google Patents
Procédé pour éviter le pompage d'un compresseur centrifuge par le contrôle d'échappement Download PDFInfo
- Publication number
- EP0335105B1 EP0335105B1 EP89103056A EP89103056A EP0335105B1 EP 0335105 B1 EP0335105 B1 EP 0335105B1 EP 89103056 A EP89103056 A EP 89103056A EP 89103056 A EP89103056 A EP 89103056A EP 0335105 B1 EP0335105 B1 EP 0335105B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- flow
- blow
- delivery
- minimum
- 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.)
- Expired - Lifetime
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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 avoiding the pumping of a turbocompressor supplying a downstream process via a discharge line with a gaseous pressure medium, according to the preamble of patent claim 1.
- a method of the type mentioned is known from DE-B-11 07 887.
- This method uses two independent control devices, namely a conventional, slow-acting and an additional, fast-acting control device.
- the conventional control device works in a known manner in accordance with a control difference, which is determined as a function of the intake volume flow and the final pressure of the compressor.
- the additional control device operates in accordance with values for the pressure or flow of the compressed medium which are recorded close to the downstream process and, if necessary, brings about a rapid partial or complete opening of the single blow-off valve or an additional, parallel blow-off valve.
- a disadvantage of this method is that it requires two independent, juxtaposed control devices to carry it out, which represents a high technical outlay.
- the new control method requires only one control device for the blow-off control to be carried out, to which one of two control differences is supplied, which first signals a fault or the larger fault.
- the additional effort for the implementation of the new control method is therefore advantageously low; however, it is ensured that both malfunctions, the cause of which lies in the area of the turbocompressor, and malfunctions resulting from a downstream process, are recognized at an early stage and converted into corresponding control processes. This ensures safe operation of the turbocompressor without pumps and without pressure drops in the downstream process.
- the discharge flow can either be measured directly by a corresponding measuring device in a pressure line for the pressure medium led to the process or in a simulation from parameters of the downstream process, such as the position of one or more valves and / or the pressure at one or more points in the process, be calculated.
- the first method variant is particularly expedient if, for other reasons, a flow measuring device is already available at a suitable point, the measurement results of which can be used for the new method.
- the calculation of the flow is to be preferred if a flow measuring device would have to be installed especially for the method. This avoids unnecessarily high investment costs. Regardless of the type of recording of the discharge flow, be it by measurement or by calculation, this can be done with one for both ways the procedure can be obtained with sufficient accuracy.
- the discharge flow is measured as a mass flow, ie as a mass per unit of time, a conversion must be carried out in order to arrive at the same units for the intake volume flow and the discharge flow.
- the mass flow is in a fixed relationship with the volume flow via the density of the compressed gas and the density in turn is a function of the pressure.
- a pressure measurement at the input of the process and a subsequent conversion are required to calculate the discharge flow as volume flow.
- the minimum intake volume flow that is just permissible is a function of the compressor end pressure.
- the same minimum flow value, supplied by a common function generator as a function of the compressor pressure, is used for the minimum intake volume flow and for the minimum discharge flow.
- Another, somewhat more complex process variant provides, in order to enable a higher accuracy and greater influence on the process, that for the minimum intake volume flow and for the minimum discharge flow, independently calculated minimum flow values, each supplied by a separate function generator, are used, the minimum intake volume flow as a function of the compressor end pressure and Minimum discharge flow is determined as a function of pressure at the discharge flow detection point near the entrance of the process.
- blow-off flow through the blow-off valve is additionally detected and added to the discharge flow.
- the blow-off flow rate is recorded either by a measurement in the blow-off line upstream and downstream of the blow-off valve or by a calculation which saves its own measuring device.
- the blow-off flow is calculated by means of a simulation calculation from the position of the blow-off valve and the pressure in front of the blow-off valve. This requires a position indicator on the relief valve, which in practice is often already available for other reasons.
- the blow-off flow can also be calculated from a control variable for the adjustment of the blow-off valve generated in the blow-off control by simulating the dynamic behavior of the blow-off valve and from the pressure in front of the blow-off valve.
- a simulation of the dynamic behavior of the valve is no problem with the electronic data processing options available today.
- the temperature of the medium flowing through the blow-off valve and / or the pressure behind the blow-off valve are additionally measured and included in the calculation of the blow-off flow.
- other variables influencing the flow through the blow-off valve can also be recorded and included in the calculation.
- the blow-off valve would be primarily controlled by the changes in the blow-off flow or the sum of this and the discharge flow. This causes the compressor to operate at an unnecessarily large distance from the surge limit.
- the value for the discharge flow or the sum of this and the value for the blow-off flow before entry into the control can be multiplied by a predeterminable factor which is greater than 1.
- a predeterminable constant can be added to the value for the discharge flow or to the sum of this and the value for the blow-off flow before entering the control. The result of this is that an undesirable increase in the safety distance from the surge limit only occurs if the error in the discharge flow determination becomes greater than the predetermined factor, which can be 1.1, for example, or as the added size.
- Another embodiment of the method provides that a correction quantity is added to the value for the discharge flow or the sum of the values for the discharge flow and blow-off flow in an additional device with a large time constant, which is changed until the sum corresponds exactly to the intake volume flow .
- a suitable choice of the time constant of the additional device which can be implemented by an integrator, for example, can ensure that the compensating effect takes place so slowly that temporary dynamic imbalances between the intake volume flow and the discharge flow rate and between the associated control differences can pass unhindered.
- the integrator can be limited to certain values, in particular negative values, which prevents the setting of an excessively large safety distance from the surge limit.
- a further embodiment of the method provides that the values for the discharge flow or the sum of this and the word for the blow-off flow are given as an input signal to a compliant reference, the reference essentially consisting of an integrator with an adjustable time constant, the output signal of which this time constant follows the input signal, and the difference between the input and output signals which occurs temporarily after sudden changes in the input signal as a correction variable for one of the intake volume flow and the minimum intake volume flow formed, used in the normal relief control first control difference.
- This control difference can be changed directly or by applying the correcting variable with the correct sign to the setpoint or actual value for the calculation of the control difference.
- Such an earlier reaction is not necessary in the event of disturbances in the direction of an increase in the discharge flow, which is why this regulation is expediently designed to act only in the first-mentioned direction of decrease by means of a flexible reference.
- FIG. 1 A sequence example of the method according to the invention is explained below with reference to a drawing.
- the single figure of the drawing shows a schematic representation of a turbocompressor along with associated lines, valves and the like elements together with a control scheme of the method.
- a turbocompressor 1 is shown, the suction side with an intake line 10 and is connected on the pressure side to an output line 11.
- a blow-off line 20 branches off from the discharge line 11, into which a blow-off valve 2 is switched on. With the blow-off valve 2 open, part of the gaseous medium conveyed into the discharge line 11 by the compressor 1 can be blown off into the atmosphere by the blow-off line 20.
- the relief valve 2 is adjustable for this purpose by means of a valve actuation device 21.
- a non-return valve 3 is inserted into this, as usual. After this check valve 3, the discharge line 11 leads to a process downstream of the compressor 1, which is to be supplied with the compressed gaseous medium.
- a measuring device 4 is used in the intake line 10, which serves to measure the intake volume flow V ⁇ A flowing through the line 10 to the compressor 1.
- a further measuring device 5 is arranged in the discharge line 11, which serves to measure the compressor end pressure P E.
- Another measuring device 6 is finally inserted into the discharge line 11 before the process downstream of the compressor 1. This measuring device 6 is used to measure the discharge flow V ⁇ P to the process, with a conversion into volume per unit of time possibly taking place via the density of the medium at the measuring point if the discharge flow is measured as a mass flow, ie as a mass per unit of time.
- x d1 is defined as the difference between the minimum flow, here the minimum intake volume flow V ⁇ Amin , and the intake volume flow V ⁇ A.
- the measured values for the discharge flow V ⁇ P are used to calculate a second control difference x d2 , where x d2 is defined as the difference between the minimum flow, here the minimum discharge flow V ⁇ Pmin and the measured discharge flow V ⁇ P.
- x d2 is defined as the difference between the minimum flow, here the minimum discharge flow V ⁇ Pmin and the measured discharge flow V ⁇ P.
- the same minimum flow rate is used for both control difference formation in the present example, ie here the minimum intake volume flow rate Vstrom amine is equal to the minimum discharge flow rate V ⁇ Pmin .
- a separate minimum delivery flow can also be calculated.
- the two control differences x d1 and x d2 are fed to a maximum value selection. In this maximum value selection, the larger of the two control difference values is selected and fed to the blow-off control as control difference x d .
- the blow-off control calculates a control variable y from the control difference x d supplied to it, which is applied to the already mentioned valve actuation device 21 for adjusting the blow-off valve 2 and there causes a corresponding adjustment of the blow-off valve 2.
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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)
- Control Of Non-Positive-Displacement Pumps (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Claims (15)
- Procédé pour éviter le pompage d'un turbocompresseur (1) alimentant en fluide sous pression gazeux, par l'intermédiaire d'une canalisation de sortie (11), un processus branché à sa suite, au moyen d'une régulation d'évacuation dans laquelle le débit volumique d'aspiration (VA) et la pression à la sortie du compresseur (PE) sont détectés en continu et dans laquelle, à partir du débit volumique d'aspiration (VA) et d'un débit volumique d'aspiration minimal (VAmin) encore admissible, dépendant de la pression (PE) à la sortie du compresseur et se situant au-dessus du débit volumique limite de pompage, une première différence de réglage (xd1) est formée, laquelle, au moyen d'une régulation d'évacuation, garantit par une ouverture réglée d'au moins une soupape d'évacuation (2), que le débit volumique d'aspiration (VA) est maintenu par le compresseur (1) au-dessus de sa limite de pompage, tandis qu'au voisinage de l'entrée du processus branché à la suite du compresseur (1), le débit de sortie (VP) vers le processus branché à la suite du compresseur (1) est détecté et, en cas de dépassement d'une valeur limite par ce débit de sortie (VP), il s'effectue également une ouverture de la soupape d'évacuation (2), procédé caractérisé en ce que la valeur limite est un débit de sortie minimal (VPmin) encore admissible, variant en fonction de la pression, qui est déterminé en fonction d'une pression sur la canalisation de sortie (11), en ce qu'une seconde différence de réglage (xd2) est formée à partir du débit de sortie (VP) et du débit de sortie minimal (VPmin), en ce que les deux différences de réglage (xd1, xd2) sont appliquées à un choix de valeurs maximales, et en ce que la plus grande des deux valeurs de différence de réglage est choisie et appliquée à la régulation d'évacuation.
- Procédé selon la revendication 1, caractérisé en ce que le débit de sortie (VP) est mesuré.
- Procédé selon la revendication 1, caractérisé en ce que le débit de sortie (VP) est calculé par une simulation à partir de paramètres du processus branché à la suite, tels que la position d'une ou plusieurs soupapes et/ou de la pression en un ou plusieurs points du processus.
- Procédé selon l'une des revendications 1 à 3, caractérisé en ce que, pour le débit volumique d'aspiration minimal (VAmin) et pour le débit de sortie minimal (Vpmin), on utilise la même valeur de débit minimal délivrée par un générateur de fonction commun en fonction de la pression (PE) à la sortie du compresseur.
- Procédé selon l'une des revendications 1 à 3, caractérisé en ce que, pour le débit volumique d'aspiration minimal (VAmin) et pour le débit de sortie minimal (VPmin) calculés indépendamment l'un de l'autre, on utilise des valeurs de débit minimal délivrées respectivement par un générateur de fonction distinct, tandis que le débit volumique d'aspiration minimal (VAmin) est déterminé en fonction de la pression (PE) à la sortie du compresseur, et le débit de sortie minimal (VPmin) est déterminé en fonction de la pression du point de détection du débit de sortie au voisinage de l'entrée du processus.
- Procédé selon l'une des revendications 1 à 5, caractérisé en ce qu'en outre le débit d'évacuation (VB) à travers la soupape d'évacuation (2) est détecté et ajouté au débit de sortie (VP).
- Procédé selon la revendication 6, caractérisé en ce que le débit d'évacuation (VB) est mesuré.
- Procédé selon la revendication 6, caractérisé en ce que le débit d'évacuation (VB) est déterminé par un calcul de simulation à partir de la position de la soupape d'évacuation (2) et de la pression en amont de la soupape d'évacuation (2).
- Procédé selon la revendication 6, caractérisé en ce que le débit d'évacuation (VB) est calculé à partir d'une grandeur de réglage (y), obtenue dans la régulation d'évacuation, pour le réglage de la soupape d'évacuation (2), et à partir de la pression en amont de la soupape d'évacuation (2) en simulation du comportement dynamique de la soupape d'évacuation (2).
- Procédé selon l'une des revendications 8 ou 9, caractérisé en ce qu'en supplément, la température du fluide s'écoutant à travers la soupape d'évacuation (2) et/ou la pression en aval de la soupape d'évacuation (2) sont mesurées et introduites dans le calcul du débit d'évacuation (VB).
- Procédé selon l'une des revendications 1 à 10, caractérisé en ce que la valeur pour le débit de sortie (VP) ou bien la somme de cette valeur et de la valeur pour le débit d'évacuation (VB), sont multipliées avant l'entrée dans la régulation par un facteur susceptible d'être prédéfini, qui est supérieur à 1.
- Procédé selon l'une des revendications 1 à 10, caractérisé en ce que à la valeur pour le débit de sortie (VP) ou bien à la somme de cette valeur et de la valeur pour le débit d'évacuation (VB), on ajoute avant l'entrée dans la régulation une constante susceptible d'être prédéfinie.
- Procédé selon l'une des revendications 1 à 10, caractérisé en ce que dans un dispositif supplémentaire à grande constante de temps, une grandeur de correction est ajoutée à la valeur pour le débit de sortie (VP) ou bien à la somme des valeurs pour le débit de sortie (VP) et le débit d'évacuation (VB), grandeur de correction qui est modifiée jusqu'à ce que la somme corresponde exactement au débit volumique d'aspiration (VA).
- Procédé selon l'une des revendications 1 à 10, caractérisé en ce que les valeurs pour le débit de sortie (VP) ou bien la somme de ce débit et de la valeur pour le débit d'évacuation (VB) sont fournies en tant que signal d'entrée à une référence modifiable, cette référence étant essentiellement constituée d'un intégrateur avec une constante de temps réglable, dont le signal de sortie suit avec cette constante de temps le signal d'entrée, et en ce que la différence apparaissant temporairement entre le signal d'entrée et le signal de sortie après des modifications soudaines du signal d'entrée, est utilisée comme grandeur de correction pour une première différence de réglage (xd1) entrant dans la régulation normale d'évacuation et formée à partir du débit volumique d'aspiration (VA) et du débit volumique d'aspiration minimal (VAmin).
- Procédé selon l'une des revendications 1 à 13, caractérisé en ce que le débit de sortie (VP) est détecté sous la forme de plusieurs débits de sortie partiels individuels en des points différents, voisins de défauts possibles, du processus branché à la suite du compresseur (1), et en ce que, pour chacun de ces débits partiels, on calcule indépendamment les unes des autres, respectivement par un générateur de fonction distinct et en fonction de la pression (PE) régnant à la sortie du compresseur, des valeurs de débit minimal distinctes.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE3810717A DE3810717A1 (de) | 1988-03-30 | 1988-03-30 | Verfahren zur vermeidung des pumpens eines turboverdichters mittels abblaseregelung |
DE3810717 | 1988-03-30 |
Publications (3)
Publication Number | Publication Date |
---|---|
EP0335105A2 EP0335105A2 (fr) | 1989-10-04 |
EP0335105A3 EP0335105A3 (en) | 1990-08-22 |
EP0335105B1 true EP0335105B1 (fr) | 1994-11-09 |
Family
ID=6351007
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP89103056A Expired - Lifetime EP0335105B1 (fr) | 1988-03-30 | 1989-02-22 | Procédé pour éviter le pompage d'un compresseur centrifuge par le contrôle d'échappement |
Country Status (5)
Country | Link |
---|---|
US (1) | US4948332A (fr) |
EP (1) | EP0335105B1 (fr) |
JP (1) | JPH01300093A (fr) |
AT (1) | ATE114021T1 (fr) |
DE (2) | DE3810717A1 (fr) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10012380A1 (de) * | 2000-03-14 | 2001-09-20 | Man Turbomasch Ag Ghh Borsig | Verfahren zum Schutz eines Turbokompressors vor Betrieb im instabilen Arbeitsbereich |
Families Citing this family (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5195875A (en) * | 1991-12-05 | 1993-03-23 | Dresser-Rand Company | Antisurge control system for compressors |
US5306116A (en) * | 1992-04-10 | 1994-04-26 | Ingersoll-Rand Company | Surge control and recovery for a centrifugal compressor |
JP3658415B2 (ja) * | 1993-12-28 | 2005-06-08 | 株式会社 日立インダストリイズ | ガスタービン装置 |
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 |
DE19726547A1 (de) * | 1997-06-23 | 1999-01-28 | Babcock Bsh Gmbh | Verfahren zur Bestimmung des Betriebspunktes eines Ventilators und Ventilator |
DE19828368C2 (de) * | 1998-06-26 | 2001-10-18 | Man Turbomasch Ag Ghh Borsig | Verfahren und Vorrichtung zum Betreiben von zwei- oder mehrstufigen Verdichtern |
CN100557249C (zh) * | 2006-11-08 | 2009-11-04 | 财团法人工业技术研究院 | 压缩机喘振的预判方法 |
EP2101240B1 (fr) * | 2008-03-10 | 2013-06-26 | Karl Morgenbesser | Organe de régulation pour liquides |
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 |
JP6501380B2 (ja) * | 2014-07-01 | 2019-04-17 | 三菱重工コンプレッサ株式会社 | 多段圧縮機システム、制御装置、異常判定方法及びプログラム |
RU2016112469A (ru) * | 2016-04-01 | 2017-10-04 | Фишер-Роузмаунт Системз, Инк. | Способы и устройство для обнаружения и предотвращения помпажа компрессора |
KR101989588B1 (ko) * | 2018-11-27 | 2019-06-14 | 터보윈 주식회사 | 서지 영역에서의 운전이 가능한 터보 블로어 |
Family Cites Families (19)
Publication number | Priority date | Publication date | Assignee | Title |
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DE1107887B (de) * | 1957-04-16 | 1961-05-31 | Power Jets Res & Dev Ltd | Regler zur Pumpverhuetung bei Stroemungsverdichtern |
US3276674A (en) * | 1963-03-06 | 1966-10-04 | Shell Oil Co | Method for preventing surging of compressors |
DE1428066A1 (de) * | 1963-08-30 | 1968-11-28 | Continental Elektro Ind Ag | Grenzmengenregelung an Turboverdichtern |
US3994623A (en) * | 1975-02-11 | 1976-11-30 | Compressor Controls Corporation | Method and apparatus for controlling a dynamic compressor |
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 |
US4486142A (en) * | 1977-12-01 | 1984-12-04 | Naum Staroselsky | Method of automatic limitation for a controlled variable in a multivariable system |
DE3105376C2 (de) * | 1981-02-14 | 1984-08-23 | M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 4200 Oberhausen | Verfahren zum Betreiben von Turboverdichtern |
US4464720A (en) * | 1982-02-12 | 1984-08-07 | The Babcock & Wilcox Company | Centrifugal compressor surge control system |
US4560319A (en) * | 1983-08-01 | 1985-12-24 | MAN Maschinenfabrik Unternehmensbereich GHH Sterkrade | Method and apparatus for controlling at least two parallel-connected turbocompressors |
US4697980A (en) * | 1984-08-20 | 1987-10-06 | The Babcock & Wilcox Company | Adaptive gain compressor surge control system |
DE3540088A1 (de) * | 1985-11-12 | 1987-05-14 | Gutehoffnungshuette Man | Verfahren zur erfassung von pumpstoessen an 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 |
JP2585324B2 (ja) * | 1987-12-09 | 1997-02-26 | 株式会社日立製作所 | ガスタービンの制御方法及びその装置 |
-
1988
- 1988-03-30 DE DE3810717A patent/DE3810717A1/de active Granted
-
1989
- 1989-02-22 EP EP89103056A patent/EP0335105B1/fr not_active Expired - Lifetime
- 1989-02-22 DE DE58908615T patent/DE58908615D1/de not_active Expired - Lifetime
- 1989-02-22 AT AT89103056T patent/ATE114021T1/de not_active IP Right Cessation
- 1989-03-09 US US07/321,519 patent/US4948332A/en not_active Expired - Lifetime
- 1989-03-29 JP JP1075269A patent/JPH01300093A/ja active Pending
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10012380A1 (de) * | 2000-03-14 | 2001-09-20 | Man Turbomasch Ag Ghh Borsig | Verfahren zum Schutz eines Turbokompressors vor Betrieb im instabilen Arbeitsbereich |
Also Published As
Publication number | Publication date |
---|---|
DE58908615D1 (de) | 1994-12-15 |
EP0335105A2 (fr) | 1989-10-04 |
DE3810717A1 (de) | 1989-10-19 |
JPH01300093A (ja) | 1989-12-04 |
US4948332A (en) | 1990-08-14 |
EP0335105A3 (en) | 1990-08-22 |
DE3810717C2 (fr) | 1992-06-04 |
ATE114021T1 (de) | 1994-11-15 |
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