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WO1999052755A1 - Retardateur hydraulique - Google Patents

Retardateur hydraulique Download PDF

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Publication number
WO1999052755A1
WO1999052755A1 PCT/EP1999/002427 EP9902427W WO9952755A1 WO 1999052755 A1 WO1999052755 A1 WO 1999052755A1 EP 9902427 W EP9902427 W EP 9902427W WO 9952755 A1 WO9952755 A1 WO 9952755A1
Authority
WO
WIPO (PCT)
Prior art keywords
pump
retarder
rotor
retarder according
stator
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.)
Ceased
Application number
PCT/EP1999/002427
Other languages
German (de)
English (en)
Inventor
Pablo Carballo Rodriquez
Luis Millan Derqui
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.)
Kloft Lothar
Original Assignee
Kloft Lothar
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 Kloft Lothar filed Critical Kloft Lothar
Priority to EP99920630A priority Critical patent/EP0988198A1/fr
Publication of WO1999052755A1 publication Critical patent/WO1999052755A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D57/00—Liquid-resistance brakes; Brakes using the internal friction of fluids or fluid-like media, e.g. powders
    • F16D57/06—Liquid-resistance brakes; Brakes using the internal friction of fluids or fluid-like media, e.g. powders comprising a pump circulating fluid, braking being effected by throttling of the circulation
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T1/00—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles
    • B60T1/02—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles acting by retarding wheels
    • B60T1/08—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles acting by retarding wheels using fluid or powdered medium
    • B60T1/093—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles acting by retarding wheels using fluid or powdered medium in hydrostatic, i.e. positive displacement, retarders
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T10/00—Control or regulation for continuous braking making use of fluid or powdered medium, e.g. for use when descending a long slope
    • B60T10/04—Control or regulation for continuous braking making use of fluid or powdered medium, e.g. for use when descending a long slope with hydrostatic brake

Definitions

  • the invention relates to a retarder, preferably for use as an additional braking device, in particular for a vehicle, such as a truck, car or the like, with a stator and a rotor rotatably mounted in the stator, the rotor with the units to be braked, such as the drive train, gearbox, or motor shaft or the like is coupled.
  • a retarder preferably for use as an additional braking device, in particular for a vehicle, such as a truck, car or the like, with a stator and a rotor rotatably mounted in the stator, the rotor with the units to be braked, such as the drive train, gearbox, or motor shaft or the like is coupled.
  • Retarders of this type are already generally known. In general, these retarders are based on the principle of eddy current braking of the rotor, which is rotatably mounted between the magnet coils of a stator. Such retarders are described for example in DE 39 08 234 AI. These known retarders have proven themselves quite well in practice. However, the known retarders, which are based on the principle of eddy current braking, are also quite complex in terms of the structure and control of the retarder braking power.
  • the invention is based on the object of developing retarders of the type mentioned in such a way that the retarder is simple in construction and can be assembled quickly and inexpensively, at the same time ensuring high reliability and simple control of the retarder performance.
  • the retarder is designed as a hydraulic retarder with a circulation displacement pump with at least one pump chamber and the circulation displacement pump is assigned a controlled or regulated pressure valve on the pressure side.
  • the retarder is therefore hydraulic
  • ⁇ ESWIGUNGSKOPIE Circulation displacement pump is formed, in which the rotor is coupled to the drive train or the like of the unit to be braked.
  • the power to be output by the hydraulic pump or the braking force or braking torque are determined by the respective setting of the controlled or regulated pressure valve.
  • the braking torque of this retarder is determined by the power demanded by the circulating displacement pump. This performance in turn depends on the setting of the controlled or regulated pressure valve.
  • the energy released when the rotor is braked is converted into thermal energy, which leads to an increase in the temperature of the fluid.
  • This construction of the retarder according to the invention means that the use of magnetic field generating elements, such as coils or the like, and the associated control or regulating power electronics can be dispensed with entirely.
  • the retarder according to the invention is also simple and compact and light, for example it can be installed or retrofitted in the vehicle. To this extent, the retarder is used in particular as an additional braking device, for example in trucks, heavy industrial vehicles or
  • the circulating displacement pump is designed as a gear pump with internal or external toothing, screw pump, vane pump, such as a single-stroke or multi-stroke driving vane pump or preferably as a blocking vane pump.
  • vane pump such as a single-stroke or multi-stroke driving vane pump or preferably as a blocking vane pump.
  • the circulation displacement pump is designed as a blocking slide pump, the stator being essentially one circular cylindrical inner wall and the rotor has at least one electrical or oval or other non-circular outer wall with in particular 180 ° rotational symmetry and the inner diameter of the inner wall corresponds essentially to a large semiaxis or the maximum diameter of the outer wall.
  • the rotor can also be designed as a double cam rotor or the like.
  • the large semiaxes and the maximum diameter of the rotor sections are offset by 180 ° / n. Because at least two pumping chambers are provided with rotor sections offset by 90 ° in this case, extremely continuous output or continuous braking torque is achieved via a 360 "rotation of the rotor. Under certain circumstances, this continuous output of the circulating displacement pump can be further improved that more than two pumping chambers are provided with the corresponding number of rotor sections It is understood that the individual pumping chambers are separated from one another by partitions or the like.
  • the measure that the blocking slide pump is designed as a double-chamber pump proves to be particularly advantageous. This ensures a very simple mechanical construction, the power output of the blocking slide pump or the braking torque generated by the blocking slide pump being quite uniform or continuous.
  • each pumping chamber is assigned two gate valves, which in the stator is radially displaceable and are arranged essentially diametrically to one another per pump chamber. Because of this measure, two pressure chamber and two suction chamber regions are formed for each pump chamber, which improves the performance of the gate valve pump.
  • the locking slides are subjected to an outward bias acting against the direction of the rotor axis, for example by a compression spring or the like. This measure ensures that, due to the action of the associated compression springs, the locking slides are initially positioned in an opening position in which the pressure chamber area is connected to the suction chamber area.
  • the locking slide can be moved from the locking position into an open position and vice versa by means of a control device. It is thus possible that the braking torque of the retarder can be suddenly reduced to zero by moving the locking slide from the locking position into an open position. If the blocking slides are primarily moved radially outwards from the contact position on the rotor or the rotor sections, they are
  • Each pumping chamber of the circulating displacement pump is advantageously assigned two blocking slides, whereby at least two pressure chamber and two suction chamber regions are formed in each pump chamber.
  • all pressure chamber areas are at least indirectly connected to the inlet of the pressure valve via bores in the stator and connected fluid channels or lines.
  • suction chamber areas are at least indirectly connected to the outlet of the pressure valve via bores in the stator and connected fluid channels or lines.
  • a heat exchanger and / or a fluid reservoir and / or a fluid filter are particularly advantageously connected in the fluid circuit between the pressure chamber area and the suction chamber area.
  • the heat exchanger is used to dissipate the thermal energy which, due to the braking torque given off by the retarder, leads to heating of the fluid in the fluid circuit.
  • the heat exchanger is connected to a cooling circuit, wherein this cooling circuit is in particular part of the brake engine of the motor vehicle.
  • control device for the locking slide is actuated according to a preferred embodiment of the invention by means of a solenoid valve, for example via compressed air.
  • the pressure valve itself is preferably designed as an electromagnetically controlled pressure control valve.
  • the retarder has an electronic control for controlling or regulating the braking power, to which one or more of the parameters vehicle speed, pressure of the pumping fluid, temperature of the pumping fluid, manual start / stop signal or manual or programmed braking power preselection are supplied as an input variable.
  • the output variables of the control are used to control or regulate the pressure valve and / or to actuate the control device of the gate valve or the like.
  • FIG. 1 shows a side view of an exemplary embodiment of the retarder according to the invention in a basic illustration, partly in section
  • FIG. 2 shows a schematic representation of a top view of the retarder in the direction of the rotor axis to explain the configuration and arrangement of the rotor sections
  • FIG. 3 shows a section of the retarder in a sectional view in the area of a locking slide to explain the position of the pressure chamber and suction chamber areas
  • Figure 4 is a schematic representation of an overall view of the retarder with associated fluid circuit and additional components and
  • Figure 5 shows a schematic representation of the control of the retarder according to the invention with different input and output variables.
  • the retarder 10 shown in the figures is preferably used as an additional braking device in motor vehicles, such as trucks, cars or the like.
  • the retarder 10 has a stator 12 and a rotor 14 which is rotatably mounted in the stator 12, the rotor 14 being coupled to the units 16 to be braked, such as a drive train, a cardan shaft or other shaft.
  • the retarder 10 is designed as a hydraulic retarder 10 with a circulation displacement pump 18 with at least one pump chamber 20, 22.
  • the circulating displacement pump 18 is assigned a controlled or regulated pressure valve 24 on the pressure side.
  • the circulating displacement pump 18 can be a gear pump with internal or external toothing, screw pump, vane pump, such as a single-stroke or multi-stroke driving vane pump, preferably also a blocking vane pump 26. If the circulating displacement pump 18 is designed as a blocking slide pump 26, the stator 12 has an essentially circular cylindrical inner wall 28.
  • the rotor 14 has at least one elliptical, oval or other non-circular outer wall 30, 32 with in particular 180 ° rotational symmetry.
  • the inner diameter of the inner wall 28 is essentially identical to a large semi-axis or the maximum diameter of the outer wall 30, 32.
  • the blocking slide pump 26 has two pumping chambers 20, 22, with each pumping chamber 20, 22 being assigned a rotor section 34, 36, each with an elliptical outer wall 30, 32 and 180 ° rotational symmetry.
  • the large semiaxes or the maximum diameters of the rotor sections 34, 36 are offset from one another by 90 °.
  • Each pump chamber 20, 22 is assigned two locking slides 38, 40, 42, 44, which are mounted in the housing of the stator 12 so as to be radially displaceable and are arranged essentially diametrically to one another per pump chamber 20, 22.
  • the locking slides 38 to 44 are acted upon, for example, by a compression spring 46, 48 with a prestress acting in the direction of the rotor axis 50.
  • a control device 52, 54 is assigned to each of the locking slides 38 to 44, with which the locking slide 38 to 44 can be moved from a locking position into an open position and vice versa.
  • Each pump chamber 20, 22 of the circulation displacement pump 18 has at least two pressure chamber regions 56 and suction chamber region 58. All pressure chamber areas 56 are at least indirectly connected to the inlet 64 of the pressure valve 24 via bores 60 in the housing of the stator 12 and connected fluid channels 62 or fluid lines. everyone too Suction chamber areas 58 are indirectly connected to the outlet 70 of the pressure valve 24 via bores 66 in the housing of the stator 12 and connected fluid channels 68 or fluid lines.
  • a heat exchanger 74, a fluid reservoir 76 and a fluid filter 78 are connected in the fluid circuit 72 between the pressure chamber region 56 and the suction chamber region 58.
  • the heat exchanger 74 is preferably connected to a cooling circuit 80, for example the internal combustion engine of the motor vehicle.
  • the control device 52, 54 for the locking slide 38 to 44 is actuated by means of a magnetic air valve via lines 92 carrying compressed air.
  • the pressure valve 24 is designed as an electromagnetically controlled pressure control valve.
  • an electronic controller 80 is provided for controlling or regulating the braking power of the retarder 10, to which the parameters vehicle speed 84, pressure of the pump fluid 86, temperature of the pump fluid 88, manual start / stop signal 90 of the manual or programmed braking power preselection are supplied as input variables.
  • the output variables of the controller 80 are used to control or regulate the pressure valve 24 and / or to actuate the control device 52, 54 of the locking slides 38 to 44.
  • the rotor 14 is mounted in the housing of the stator 12 by means of a bearing 94 and bearing rings 96.
  • the rotor 14 is seated on a shaft 98, which in turn is coupled to the unit 16.
  • a seal 100 is provided between the shaft 98 and the housing of the stator 12.
  • the rotor 14 has two rotor sections 23, 36, which are essentially elliptical and are arranged offset by 90 ° to one another. Due to this measure, a more uniform braking torque is generated by rotating the rotor 14 through 360 °. In other words, this means that these measures achieve a delivery volume of the blocking slide pump 26 which is proportional to the speed or the angle of rotation of the rotor 14.
  • the stator 12 is cylindrical and has an inner diameter which, taking manufacturing tolerances into account, corresponds to the maximum outer diameter of the rotor 14. Integrated in the stator 12 are the bores 60, 66, the locking slides 38 to 44 and possibly also the fluid channels 62, 68 and possibly the control device 52, 54, furthermore the pressure valve 24, the heat exchanger 74, the fluid reservoir 76 and the fluid filter 78 or the entire fluid circuit 72 may be arranged in the stator 12.
  • the locking slides 38 to 44 controlled by the control device 42, 54 rest in the locking position on the outer walls 30, 32 of the rotor 14 and thus ensure a separation of the pressure chamber region 56 and the suction chamber region 58.
  • the fluid is forced out of the pressure chamber region 56 the bores 60 and the fluid channels 62 to flow to the inlet 64 of the pressure valve 24.
  • the fluid from the outlet 70 of the pressure valve 24 is passed directly or indirectly to the suction chamber area 58.
  • Suction chamber area 58 can flow. With the blocking slides 38 to 44 in the open position, the rotor 14 rotates in the stator 12 practically without resistance.
  • the pressure valve 24 determines the required braking power between the value zero and the maximum value.
  • the braking torque is directly proportional to the fluid pressure, which can be adjusted by a corresponding control or regulation of the pressure valve 24.
  • the heat exchanger 74 ensures that the heat absorbed by the fluid due to the braking torque is dissipated via a cooling circuit, for example of the vehicle engine.
  • the fluid reservoir 76 can itself be integrated in the stator 12 or can also be arranged independently of the stator 12, for example in the region of the vehicle.
  • the electronic control 62 can, for example, receive information from the cabin of the vehicle that is based on various braking torque values or also the vehicle top speed. For example, the activity of the retarder 10 can start when a specific, predetermined maximum vehicle speed value is exceeded.
  • the retarder 10 works as follows:
  • the pressure valve 24 is also fully opened, so that the fluid can escape from the pumping chambers 20, 22, for example due to its own centrifugal force, into the bores 60, 66 to fluid channels 62, 68.
  • the rotor 14 rotates in the stator 12 practically without friction, the retarder 10 not developing any braking torque.
  • the chambers which hold the locking slides 38 to 44 are pressurized with compressed air, for example via a solenoid air valve, which ensures that the locking slides 38 to 44 counter to the action of the compression springs 46, 48 radially inwards in the direction of the rotor axis 50 can be moved and rest sealingly on the outer wall 30, 32 of the rotor sections 34, 36.
  • the pump chambers 20, 22 of the blocking slide pump 26 are subdivided into said pressure chamber regions 56 and suction chamber regions 58, so that a pumping action for the fluid now takes place and the fluid is guided out of the bores 60 and fluid channels 62 to the inlet 64 of the pressure valve 24.
  • the fluid is sucked into the suction chamber area 58 via the bores 66 and the fluid channels 68.
  • the envelope of the braking torque output by the retarder 10 is determined by the setting of the pressure valve 24, since the braking force or the braking torque is essentially proportional to the fluid pressure. A variation in the braking torque is ensured by a corresponding activation or regulation of the pressure valve 24. 13
  • the braking torque output by the retarder 10 is converted into heat, which heats the fluid flowing in the fluid circuit 72.
  • a heat exchanger 74 is provided in order to reduce the fluid temperature.
  • the heat exchanger 74 can be connected to the engine cooling water circuit of the motor vehicle or to an independent circuit.
  • the resistance torque or braking torque of the retarder 10 which is dependent on the angle of rotation, runs essentially sinusoidally between zero and a maximum value.
  • These fluctuations in the braking torque are practically compensated for in that the second rotor section 36 is arranged offset by 90 ° with respect to the first rotor section 34, so that the sum of the two resistance moments or braking torques dependent on the angle of rotation is essentially constant over the entire angle of rotation of 360 ° is.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Transportation (AREA)
  • Transmission Of Braking Force In Braking Systems (AREA)
  • Braking Arrangements (AREA)

Abstract

L'invention concerne un retardateur (10) comprenant un stator (12) et un rotor (14) monté pivotant dans le stator (12). Le rotor (14) est relié aux ensembles à freiner (16), tels que l'ensemble des pièces de transmission, l'arbre de la boîte de vitesses, l'arbre du moteur ou équivalent. Le retardateur (10) est conçu sous la forme d'un retardateur hydraulique doté d'une pompe de refoulement de circulation (18) contenant au moins une chambre de pompage (20, 22). Une soupape de refoulement (24) commandée ou régulée est associée au côté refoulement de la pompe de refoulement de circulation (18). Le retardateur (10) est utilisé, de préférence, comme dispositif de freinage supplémentaire destiné notamment aux véhicules, tels que les poids lourds, les automobiles ou équivalent.
PCT/EP1999/002427 1998-04-10 1999-04-09 Retardateur hydraulique Ceased WO1999052755A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP99920630A EP0988198A1 (fr) 1998-04-10 1999-04-09 Retardateur hydraulique

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE1998116101 DE19816101C2 (de) 1998-04-10 1998-04-10 Hydraulischer Retarder
DE19816101.8 1998-04-10

Publications (1)

Publication Number Publication Date
WO1999052755A1 true WO1999052755A1 (fr) 1999-10-21

Family

ID=7864234

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1999/002427 Ceased WO1999052755A1 (fr) 1998-04-10 1999-04-09 Retardateur hydraulique

Country Status (3)

Country Link
EP (1) EP0988198A1 (fr)
DE (1) DE19816101C2 (fr)
WO (1) WO1999052755A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114274932A (zh) * 2021-12-31 2022-04-05 富奥汽车零部件股份有限公司 一种液力缓速器的控制方法和控制装置

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB0201330D0 (en) * 2002-01-21 2002-03-06 Monfor Alexander O Hydraulic drive
DE102019202849A1 (de) * 2019-03-01 2020-09-03 Thyssenkrupp Ag Antriebseinrichtung für ein Fahrzeug, Fahrzeug und Verfahren zur Abbremsung einer Antriebseinrichtung
CN114151328B (zh) * 2021-12-31 2024-04-30 富奥汽车零部件股份有限公司 一种缓速装置

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1880194A (en) * 1929-09-19 1932-10-04 Edgar W Brown Jr Hydraulic brake
US3913453A (en) * 1974-08-30 1975-10-21 Deere & Co Hydrostatic transmission
US3987874A (en) * 1973-03-28 1976-10-26 General Motors Corporation Transmission with retarder and controls
US4006804A (en) * 1974-04-29 1977-02-08 Compagnie De Construction Mechanique Sulzer Electromagnetically-actuatable rotary vane pump for use as a hydraulic brake
US4214652A (en) * 1978-12-01 1980-07-29 The Jacobs Manufacturing Company Variable power transmission and absorption device
EP0177767A1 (fr) * 1984-10-09 1986-04-16 MAN Nutzfahrzeuge Aktiengesellschaft Frein de service pour poids lourd ou autobus
DE3908234A1 (de) 1989-02-27 1990-08-30 Hans Heinrich Holm Eggers Zusatzbremseinrichtung fuer fahrzeuge
WO1992016767A1 (fr) * 1991-03-20 1992-10-01 Skorodoff, Ivan Systeme de frein hydraulique pour vehicules
DE19735287A1 (de) * 1997-08-14 1999-02-18 Zahnradfabrik Friedrichshafen Hydrostatischer Retarder mit Nebenabtrieb

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3621290A1 (de) * 1986-06-25 1988-01-14 Dornier Gmbh Radbremse fuer fahrzeuge, insbesondere fuer luft- und raumfahrzeuge
DE3907053A1 (de) * 1989-03-04 1990-09-06 Walter Arndt Oelhydraulische dauerbremse zum abbremsen von fahrzeugen

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1880194A (en) * 1929-09-19 1932-10-04 Edgar W Brown Jr Hydraulic brake
US3987874A (en) * 1973-03-28 1976-10-26 General Motors Corporation Transmission with retarder and controls
US4006804A (en) * 1974-04-29 1977-02-08 Compagnie De Construction Mechanique Sulzer Electromagnetically-actuatable rotary vane pump for use as a hydraulic brake
US3913453A (en) * 1974-08-30 1975-10-21 Deere & Co Hydrostatic transmission
US4214652A (en) * 1978-12-01 1980-07-29 The Jacobs Manufacturing Company Variable power transmission and absorption device
EP0177767A1 (fr) * 1984-10-09 1986-04-16 MAN Nutzfahrzeuge Aktiengesellschaft Frein de service pour poids lourd ou autobus
DE3908234A1 (de) 1989-02-27 1990-08-30 Hans Heinrich Holm Eggers Zusatzbremseinrichtung fuer fahrzeuge
WO1992016767A1 (fr) * 1991-03-20 1992-10-01 Skorodoff, Ivan Systeme de frein hydraulique pour vehicules
DE19735287A1 (de) * 1997-08-14 1999-02-18 Zahnradfabrik Friedrichshafen Hydrostatischer Retarder mit Nebenabtrieb

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114274932A (zh) * 2021-12-31 2022-04-05 富奥汽车零部件股份有限公司 一种液力缓速器的控制方法和控制装置
CN114274932B (zh) * 2021-12-31 2022-12-02 富奥汽车零部件股份有限公司 一种液力缓速器的控制方法和控制装置

Also Published As

Publication number Publication date
DE19816101A1 (de) 1999-10-21
EP0988198A1 (fr) 2000-03-29
DE19816101C2 (de) 2000-05-11

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