EP0356690A1 - Producteur de chaleur chauffé au carburant - Google Patents

Producteur de chaleur chauffé au carburant Download PDF

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Publication number
EP0356690A1
EP0356690A1 EP89113385A EP89113385A EP0356690A1 EP 0356690 A1 EP0356690 A1 EP 0356690A1 EP 89113385 A EP89113385 A EP 89113385A EP 89113385 A EP89113385 A EP 89113385A EP 0356690 A1 EP0356690 A1 EP 0356690A1
Authority
EP
European Patent Office
Prior art keywords
line
fuel
burner
inlet
flow
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
EP89113385A
Other languages
German (de)
English (en)
Other versions
EP0356690B1 (fr
Inventor
Karl Dungs
Alfred Sinner
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.)
Karl Dungs GmbH and Co KG
Original Assignee
Karl Dungs GmbH and Co KG
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 Karl Dungs GmbH and Co KG filed Critical Karl Dungs GmbH and Co KG
Priority to AT89113385T priority Critical patent/ATE89657T1/de
Publication of EP0356690A1 publication Critical patent/EP0356690A1/fr
Application granted granted Critical
Publication of EP0356690B1 publication Critical patent/EP0356690B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N1/00—Regulating fuel supply
    • F23N1/04—Regulating fuel supply conjointly with air supply and with draught
    • F23N1/045—Regulating fuel supply conjointly with air supply and with draught using electrical or electromechanical means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N2225/00—Measuring
    • F23N2225/08—Measuring temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N2225/00—Measuring
    • F23N2225/08—Measuring temperature
    • F23N2225/20—Measuring temperature entrant temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N2233/00—Ventilators
    • F23N2233/02—Ventilators in stacks
    • F23N2233/04—Ventilators in stacks with variable speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N5/00—Systems for controlling combustion
    • F23N5/18—Systems for controlling combustion using detectors sensitive to rate of flow of air or fuel

Definitions

  • the invention relates to a fuel-fired heat generator with a burner, which has an inlet line for supplying a fuel / air mixture and an outlet line for discharging the exhaust gases, with a main line connected to the inlet line, in which a flow sensor is arranged, with a first fuel line, introduces a fixed-size fuel flow, which determines the minimum heating power, into the area of the main and inlet lines between the flow sensor and the burner, with at least one secondary line which supplies an air flow proportional to its cross-section to the inlet line, with a second fuel line which surrounds the inlet line Area a second focal Introduces material flow that is in the same ratio to the fixed size fuel flow as the cross section of the secondary line to the cross section of the main line, with a fan determining the size of the air flow flowing through the lines and with a delivery rate of the fan depending on the output signal of the Main line arranged flow sensor controlling control device.
  • Such a heat generator is known from DE 37 00 084 A1. It enables the burner to be operated in a very simple manner with flows of the fuel / air mixture of very different strengths while maintaining the optimum fuel / air ratio. Nevertheless, the controllability of such a heat generator is subject to strict limits because the outflow speed of the fuel / air mixture does not permit any great variation. If the outflow rate exceeds the ignition rate of the fuel / air mixture, the flame breaks off. If, on the other hand, the outflow speed becomes too low, the flame moves too close to the burner and the burner is inadmissibly overheated due to the reduced cooling capacity due to the reduced flow speed.
  • the invention is based on the object of developing a fuel-fired heat generator of the type described at the outset in such a way that the heating output can be varied to a much greater extent than in the known heat generators.
  • outlet line and the inlet line are connected to one another by a return line provided with a valve, via which a flow of the exhaust gas which decreases with increasing size can be mixed with the fuel / air mixture flow.
  • the volume of the fuel / air mixture is increased and thereby the outflow speed is increased without the fuel portion of the mixture and thus its heat content being increased or the ratio of fuel to air volume, which is important for optimal combustion, being changed.
  • the ignition speed of the mixture is reduced by the addition of exhaust gases, so that a reduction in the throughput compared to conventionally operated burners is also possible.
  • the double effect of increasing the throughput with a constant calorific value and reducing the ignition speed makes it possible to operate conventional burners far below the minimum power required previously, thereby considerably expanding their control range.
  • a particular advantage of this measure is that it does not require any complicated measures to regulate the composition of the fuel / Lusft mixture or the burner behavior, but the advantages of the known heat generator are retained in full.
  • a valve arrangement which enables the heat generator according to DE 37 00 084 A1 to be designed in a particularly simple manner.
  • a similar arrangement can also be used successfully with the heat generator designed according to the invention.
  • a preferred embodiment of the invention provides that the secondary line, the second fuel line and the return line open side by side in the inlet line and the mouths of the three lines a common slide is assigned, which can optionally be brought into a position that simultaneously releases or covers the two mouths of the secondary line and the second fuel line, in which it covers or releases the mouth of the return line in the reverse manner.
  • valve arrangement When using such a valve arrangement, there is no need to install separate valves in the return line, the secondary line and the second fuel line and, if necessary, to connect them to a common drive.
  • special fittings such as T-pieces or the like need not be provided in order to bring the various lines together, since the valve arrangement according to the invention fulfills both the functions of the shut-off valves and the line mergers. Therefore, such a valve arrangement significantly simplifies the structure and reduces the space requirement of fuel-fired heat generators of the type described.
  • valve arrangement enables that in a further embodiment of the invention the orifices of the secondary line, the fuel line and also the return line have cross sections which are proportional to one another and the slide can be able to be brought into intermediate positions in which it releases or covers corresponding portions of the orifice cross sections.
  • the outlets of the secondary line and the return line have a rectangular shape Cross-section, the throughputs of the secondary line and the return line are exactly proportional to the travel of the slide or inversely proportional.
  • either the mouth of the assigned fuel line can also have a rectangular cross section, or all holes can have the same diameter when using holes.
  • the main line, the secondary line and the return line open into the inlet line in the area of a chamber having an arcuate wall section and the slide is designed as a rotary slide valve.
  • Rotary slide valve arrangements are particularly easy to manufacture and allow simple storage and particularly simple drive of the slide valve.
  • the chamber can be formed in a particularly simple manner completely by a cylindrical pot open at one end, in the jacket of which, in addition to the secondary line, the return line also opens, while the inlet line leading to the burner of the heat generator connects to the open end of the pot.
  • the bottom of the chamber also permits the bearing of a shaft which is sealed off from the bottom and to which the slide is fastened inside the chamber and whose end penetrating the bottom is connected to a drive motor.
  • the heat generator shown in the drawing has a burner 1, to which a gas / air mixture is supplied via an inlet line 2.
  • the burner 1 is located within a boiler housing 3, which also encloses the heat exchanger 4 of a heating system.
  • the boiler housing 3 is provided with an outlet line 5 for the exhaust gases, in which there is a fan 7 driven by a motor 6.
  • the inlet line 2 connects the burner 1 to a main line 21 which leads to an air inlet opening 8.
  • a temperature sensor 9 and a flow sensor 10 also protrude into the main line 21.
  • the output signals of these sensors 9, 10 are fed to a control device 11.
  • a first fuel line 13 opens into the main line 21 and supplies gas to the main line as fuel.
  • a gas pressure regulator 14 is located in the fuel line 13 in the flow direction of the gas, so that the main line 21 is supplied with the gas at a predetermined pressure and therefore also as a current of a predetermined strength.
  • a precisely defined one belongs to the given gas flow Airflow.
  • the supply of the correct air flow is monitored by the flow sensor 10, the output signal of which is characteristic of the flow speed of the air in the main line 21.
  • the control device 11 controls depending on the output signals of the temperature sensor 9 and the flow sensor 10, the speed of the motor 6 used to drive the blower 7 in such a way that the flow rate required for supplying the correct amount of air prevails in the main line 21. This ensures in a very simple manner that optimal combustion conditions are present for the gas supplied to the burner 1.
  • the main line 21 has a secondary line 22 connected in parallel, which, like the main line 21, opens into the inlet line 2. Similar to the main line 21, the secondary line 22 also has an open end serving as an air inlet opening, and it is assigned a second fuel line 23 which branches off from the first fuel line 13 opening into the main line 21. A shut-off valve 24 is located in this second fuel line 23. A shut-off valve 25 is also located in the secondary line 21. The shut-off valves 24 and 25 are connected to a common servomotor 26 which, if necessary, causes the shut-off valves 24, 25 to open and close together .
  • the check valves 24, 25 schematically shown in FIG. 1 for the secondary line 21 and the associated fuel line 23 are integrated in a valve arrangement which has a cylindrical pot 31, in the jacket 32 of which the Air inlet opening 8 leading section 2 of the main line and the secondary line 21 open.
  • both lines have the same rectangular cross-section in the exemplary embodiment shown and are arranged parallel to one another in such a way that they abut one side 27 and 28, respectively.
  • the leading to the burner 1 section 2 'of the main line connects to the open end of the pot 31.
  • the section 2 'of the main line opposite end of the pot 31 is provided with a bottom 33 into which an annular channel 34 is incorporated.
  • the base 33 consists of two disc-shaped parts 35, 36, of which the upper part 36 has a groove forming the annular channel 34 on its side facing the lower part 35.
  • the lower disc-shaped part 35 is provided with a screw connection for the gas line 13, so that the gas line 13 opens into the annular channel 34.
  • This ring channel 34 communicates with the interior of the pot 31 via bores 37 and 38, of which the bore 37 is arranged in front of the mouth of section 2 of the main line and has a diameter such that the amount of gas entering the pot via this bore 37 corresponds to the minimum output of the burner, to which the amount of air flowing through the main line 2, 2 'is set by means of the sensors 9, 10.
  • the bores 38 are arranged within the sector 39 delimited by dash-dotted lines in FIG. 2, which is defined by the mouth 40 of the secondary line 21 in the jacket 32 of the pot 31, and next to one another on a circular arc 41, likewise indicated by dash-dotted lines.
  • the bores 38 in their entirety form the fuel line 23 assigned to the secondary line 21.
  • the overall cross section of these bores 38 is so dimensioned that the amount of gas supplied to the pot 31 through these holes to the amount of air supplied via the secondary line 21 is in the same ratio as the amount of gas supplied via the bore 37 to the amount of air supplied through section 2 of the main line.
  • the amount of gas supplied over the entirety of the bores 38 and the amount of air supplied via the secondary line 21 can be dimensioned such that the maximum output of the burner 1 is achieved together with the fuel / air mixture always carried by the main line 2, 2 ' .
  • the section 2 of the main line and the secondary line 21 leading to the air inlet opening 8 have the same cross section, so that the entirety of the bores 38 has the same cross section as the bore 37 and the heating power of the burner 1 is doubled by switching on the secondary line 21 can be.
  • a rotary slide valve 51 serves as shut-off valves 24, 25 for the secondary line 21 and the associated gas line 23, which is fastened on the inner end of a shaft 52 which is rotatably mounted in the base 33 and is sealed against the base in a manner not shown is.
  • This rotary slide valve has at its end a plate 53 with a circular arc in cross section, which covers the mouth 40 of the secondary line 21 in a first end position and thus blocks the secondary line 21.
  • the rotary slide 51 In its section connecting the plate 53 to the shaft 52, the rotary slide 51 has a bore 54 perpendicular to the bottom 33 of the pot, in which a stamp-like insert 55 is mounted displaceably and is loaded by a helical compression spring 56 arranged in the bore 54, so that the latter Insert with the outer surface of his head 57 abuts the bottom 33.
  • the through Knife of the head 57 is dimensioned such that it completely covers the holes 38 arranged on the circular arc 41 when the plate 53 covers the mouth 40 of the secondary line 21.
  • the rotary valve 51 By pivoting the rotary valve 51 by an angle which is substantially equal to the angle of the sector 39 defined by the mouth 40 of the secondary line 21, the rotary valve 51 can be brought into a second end position, not shown in the drawing, in which the plate 53 the mouth 40 and also the head 57 of the insert 55 clears all the bores 38. If the rotary valve occupies a position lying between these two end positions, the mouth 40 of the secondary line 21 is only partially released.
  • the use of tubes with a rectangular cross section has the result that the mouth 40 of the secondary line also has a rectangular cross section and the released section of the secondary line is exactly proportional to the swivel angle of the rotary valve.
  • the use of a number of bores 38 as the mouth of the fuel line assigned to the secondary line 21 ensures that the amount of gas supplied is proportional to the number of bores released and thus in turn to the swivel angle of the rotary valve. It is advisable to gradually adjust the rotary valve so that each additional hole is completely released or covered. If a completely constant change in the heating output is desired, the row of holes could be replaced by a corresponding slot. It would also be possible to partially cover a larger bore similar to the mouth of the secondary line, in which case such a bore would correspond to a circular mouth of the secondary line. With regard to a linear dependence of the power change on the angle of rotation, however, the described embodiment preferred with a rectangular mouth of the secondary line and a correspondingly designed mouth of the associated fuel line.
  • the drive motor 26 for the rotary valve 51 which corresponds to the two shut-off valves 24, 25 according to FIG. 1, is fastened to the base 33 of the pot 31 by means of a holder 61 such that the output shaft 62 of the motor with the rotary valve 51 supporting shaft 52 is aligned and can be connected to this shaft by a plug-in coupling 63.
  • the motor 26 can be a stepping motor, but it can also be a continuously running motor with appropriate control, which preferably has a strong reduction, since the rotary valve 51 may only be adjusted at a relatively low speed. Since the air throughput is determined by the delivery rate of the blower 7, the change in the line cross-sections and thus the fuel supply must not take place faster than the speed with which the blower 7 can react to the changed air requirement.
  • the invention is not limited to the exemplary embodiment shown, but deviations from it are possible without leaving the scope of the invention.
  • the cylindrical shape of the pot is only important for the pivoting range of the rotary valve, so that even when using a rotary valve, the chamber formed by the pot is also different Can have a cross-sectional shape as long as only the secondary line opens into a cylindrical wall section and there is sufficient space for the rotary valve to pivot away.
  • a linearly movable valve can also be used and that it is possible to provide the mouths of the air and gas lines in the same wall section.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Feeding And Controlling Fuel (AREA)
  • Gas Burners (AREA)
EP89113385A 1988-09-01 1989-07-21 Producteur de chaleur chauffé au carburant Expired - Lifetime EP0356690B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT89113385T ATE89657T1 (de) 1988-09-01 1989-07-21 Brennstoffbefeuerter waermeerzeuger.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3829664A DE3829664C1 (fr) 1988-09-01 1988-09-01
DE3829664 1988-09-01

Publications (2)

Publication Number Publication Date
EP0356690A1 true EP0356690A1 (fr) 1990-03-07
EP0356690B1 EP0356690B1 (fr) 1993-05-19

Family

ID=6362054

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89113385A Expired - Lifetime EP0356690B1 (fr) 1988-09-01 1989-07-21 Producteur de chaleur chauffé au carburant

Country Status (3)

Country Link
EP (1) EP0356690B1 (fr)
AT (1) ATE89657T1 (fr)
DE (1) DE3829664C1 (fr)

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1008805A1 (fr) * 1998-12-11 2000-06-14 Honeywell B.V. Procédé de régulation d'un brûleur à gaz
EP1052365A2 (fr) 1999-05-11 2000-11-15 Hunter Douglas Industries B.V. Dispositif d'entraínement pour un store vénitien
US9645584B2 (en) 2014-09-17 2017-05-09 Honeywell International Inc. Gas valve with electronic health monitoring
US9657946B2 (en) 2012-09-15 2017-05-23 Honeywell International Inc. Burner control system
US9683674B2 (en) 2013-10-29 2017-06-20 Honeywell Technologies Sarl Regulating device
US9835265B2 (en) 2011-12-15 2017-12-05 Honeywell International Inc. Valve with actuator diagnostics
US9841122B2 (en) 2014-09-09 2017-12-12 Honeywell International Inc. Gas valve with electronic valve proving system
US9846440B2 (en) 2011-12-15 2017-12-19 Honeywell International Inc. Valve controller configured to estimate fuel comsumption
US9851103B2 (en) 2011-12-15 2017-12-26 Honeywell International Inc. Gas valve with overpressure diagnostics
US10422531B2 (en) 2012-09-15 2019-09-24 Honeywell International Inc. System and approach for controlling a combustion chamber
US10503181B2 (en) 2016-01-13 2019-12-10 Honeywell International Inc. Pressure regulator
US10564062B2 (en) 2016-10-19 2020-02-18 Honeywell International Inc. Human-machine interface for gas valve
US10697632B2 (en) 2011-12-15 2020-06-30 Honeywell International Inc. Gas valve with communication link
US10697815B2 (en) 2018-06-09 2020-06-30 Honeywell International Inc. System and methods for mitigating condensation in a sensor module
US11073281B2 (en) 2017-12-29 2021-07-27 Honeywell International Inc. Closed-loop programming and control of a combustion appliance

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4120831A1 (de) * 1991-06-24 1993-01-07 Asea Brown Boveri Verfahren zum betrieb einer feuerungsanlage oder brennkammer
DE19502905C2 (de) * 1995-01-31 1997-12-18 Stiebel Eltron Gmbh & Co Kg Gasbrennergerät mit Abgasrezirkulation
DE19711140A1 (de) * 1997-03-18 1998-06-04 Bosch Gmbh Robert Verfahren zum Betreiben eines mit einem Brennstoff-Luftgemisch gespeisten Brenners
EP0908670B1 (fr) * 1997-10-06 2004-07-28 Robert Bosch Gmbh Dispositif pour actionner un brûleur atmosphérique à gaz
DE19947565A1 (de) * 1999-10-02 2001-04-05 Ruhrgas Ag Vorrichtung zum Mischen von fluidförmigem Brennstoff mit zwei Gasströmen
DE19920113A1 (de) * 1999-05-03 2000-11-09 Kromschroeder Ag G Verfahren und Vorrichtung zum Beheizen eines Ofenraums
US8899264B2 (en) 2011-12-15 2014-12-02 Honeywell International Inc. Gas valve with electronic proof of closure system
US8947242B2 (en) 2011-12-15 2015-02-03 Honeywell International Inc. Gas valve with valve leakage test
US8839815B2 (en) 2011-12-15 2014-09-23 Honeywell International Inc. Gas valve with electronic cycle counter
US9074770B2 (en) 2011-12-15 2015-07-07 Honeywell International Inc. Gas valve with electronic valve proving system
US8905063B2 (en) 2011-12-15 2014-12-09 Honeywell International Inc. Gas valve with fuel rate monitor
US9995486B2 (en) 2011-12-15 2018-06-12 Honeywell International Inc. Gas valve with high/low gas pressure detection
US10024439B2 (en) 2013-12-16 2018-07-17 Honeywell International Inc. Valve over-travel mechanism

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE685899C (de) * 1935-04-29 1939-12-28 Rateau Soc Regelvorrichtung fuer Abgasturbogeblaese fuer die Verbrennungsluft von Dampferzeugern
EP0062854A1 (fr) * 1981-04-13 1982-10-20 Honeywell B.V. Dispositif de chauffage à gaz pour eau ou air
EP0109620A2 (fr) * 1982-11-18 1984-05-30 Joh. Vaillant GmbH u. Co. Source de chaleur chauffée par combustible
DE3708573A1 (de) * 1987-03-17 1988-09-29 Dungs Karl Gmbh & Co Ventilanordnung

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE685899C (de) * 1935-04-29 1939-12-28 Rateau Soc Regelvorrichtung fuer Abgasturbogeblaese fuer die Verbrennungsluft von Dampferzeugern
EP0062854A1 (fr) * 1981-04-13 1982-10-20 Honeywell B.V. Dispositif de chauffage à gaz pour eau ou air
EP0109620A2 (fr) * 1982-11-18 1984-05-30 Joh. Vaillant GmbH u. Co. Source de chaleur chauffée par combustible
DE3708573A1 (de) * 1987-03-17 1988-09-29 Dungs Karl Gmbh & Co Ventilanordnung

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1008805A1 (fr) * 1998-12-11 2000-06-14 Honeywell B.V. Procédé de régulation d'un brûleur à gaz
EP1052365A2 (fr) 1999-05-11 2000-11-15 Hunter Douglas Industries B.V. Dispositif d'entraínement pour un store vénitien
US9835265B2 (en) 2011-12-15 2017-12-05 Honeywell International Inc. Valve with actuator diagnostics
US10851993B2 (en) 2011-12-15 2020-12-01 Honeywell International Inc. Gas valve with overpressure diagnostics
US9846440B2 (en) 2011-12-15 2017-12-19 Honeywell International Inc. Valve controller configured to estimate fuel comsumption
US9851103B2 (en) 2011-12-15 2017-12-26 Honeywell International Inc. Gas valve with overpressure diagnostics
US10697632B2 (en) 2011-12-15 2020-06-30 Honeywell International Inc. Gas valve with communication link
US10422531B2 (en) 2012-09-15 2019-09-24 Honeywell International Inc. System and approach for controlling a combustion chamber
US11421875B2 (en) 2012-09-15 2022-08-23 Honeywell International Inc. Burner control system
US9657946B2 (en) 2012-09-15 2017-05-23 Honeywell International Inc. Burner control system
US9683674B2 (en) 2013-10-29 2017-06-20 Honeywell Technologies Sarl Regulating device
US9841122B2 (en) 2014-09-09 2017-12-12 Honeywell International Inc. Gas valve with electronic valve proving system
US10203049B2 (en) 2014-09-17 2019-02-12 Honeywell International Inc. Gas valve with electronic health monitoring
US9645584B2 (en) 2014-09-17 2017-05-09 Honeywell International Inc. Gas valve with electronic health monitoring
US10503181B2 (en) 2016-01-13 2019-12-10 Honeywell International Inc. Pressure regulator
US10564062B2 (en) 2016-10-19 2020-02-18 Honeywell International Inc. Human-machine interface for gas valve
US11073281B2 (en) 2017-12-29 2021-07-27 Honeywell International Inc. Closed-loop programming and control of a combustion appliance
US10697815B2 (en) 2018-06-09 2020-06-30 Honeywell International Inc. System and methods for mitigating condensation in a sensor module

Also Published As

Publication number Publication date
ATE89657T1 (de) 1993-06-15
DE3829664C1 (fr) 1990-01-18
EP0356690B1 (fr) 1993-05-19

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