EP0972940B1 - Dispositif de contrôle de puissance pour la régulation de la puissance hydraulique dans un circuit de travail - Google Patents
Dispositif de contrôle de puissance pour la régulation de la puissance hydraulique dans un circuit de travail Download PDFInfo
- Publication number
- EP0972940B1 EP0972940B1 EP19990113344 EP99113344A EP0972940B1 EP 0972940 B1 EP0972940 B1 EP 0972940B1 EP 19990113344 EP19990113344 EP 19990113344 EP 99113344 A EP99113344 A EP 99113344A EP 0972940 B1 EP0972940 B1 EP 0972940B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- control device
- pressure
- throttle
- main valve
- 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
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/002—Hydraulic systems to change the pump delivery
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/08—Regulating by delivery pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B2205/00—Fluid parameters
- F04B2205/17—Opening width of a throttling device
- F04B2205/172—Opening width of a throttling device after the pump outlet
Definitions
- the invention relates to a power control device for controlling the hydraulic power in a working line.
- Power control devices are already known in a variety of designs.
- DE 35 41 750 C2 discloses a power control device which consists of a simple control valve arranged in the working line. The pressure downstream of the control valve is tapped and returned via a control line to the control valve.
- a special embodiment of the passage opening of the control valve ensures that the product of high pressure and flow through the control valve is adjusted to a constant value.
- a disadvantage is the immediate arrangement of the power function predetermining control valve in the working line, since the control valve and in particular its opening cross-section must be made relatively large.
- the control valve can not be designed as a simple slide valve, since the geometry of the opening cross-section must meet special requirements because of the power control function.
- a known for example from DE 196 26 793 C1 power control device comprises a so-called hyperbola controller, which acts back on a pivoting angle acting as a power control valve proportional valve.
- the reaction is dependent on the one hand by the pressure in the working line of the associated hydraulic pump and on the other hand by the lever arm, with which the pressure of the working line acts on the pivot lever.
- This constellation results in a hyperbolic control characteristic, ie at Achieving the predetermined maximum power controls the power control device, the hydraulic pump to a constant power, ie a constant product of working pressure in the working line and delivery volume of the hydraulic pump, a.
- the invention is based on the finding that the power control device is less susceptible to interference and the control function is more accurate when the elements that predetermine the power control punctuation are not directly in the Working line but are arranged in a side circuit.
- the working line there is only one main valve, which can be extremely simple, for example, designed as a slide valve and designed for the control of large volume flows, without causing constructive difficulties.
- From the input of the power control device according to the invention branches a side circuit.
- the secondary circuit is supplied via a flow control device, a constant volume flow, which is in particular independent of the prevailing in the working line high pressure.
- a drain throttle is further provided, which is connected to the valve body of the main valve, so that the throttle cross-section depends on the position of the valve body of the main valve.
- the invention makes use of the fact that the supplied volume flow must be removed again from the outlet throttle. From this continuity condition results for each high pressure in the working line, a certain opening cross section of the outlet throttle and thus a certain secondary pressure in the secondary circuit between the Sromregel issued and the outlet throttle. This secondary pressure is supplied to a first valve chamber of the main valve to control the valve body.
- the power control device according to the invention Compared with an acting on the adjustment of an adjustable hydraulic pump power control device with hyperbola, there is the advantage of universal applicability in the power control device according to the invention.
- the power control is independent of the speed of the connected hydraulic pump.
- the power control device according to the invention can be used in any hydraulic lines to remote from the pump body, since it does not require a mechanical reaction to the pump.
- the power-regulating element directly in the working line.
- the power control device according to the invention the advantage of a simple structural design of the arranged in the working line main valve and the more accurate control function.
- the actual flow control function taking over together with the flow control device flow restrictor can be designed to be relatively small, since it controls only a small flow of the secondary circuit.
- the flow control device and the outlet throttle can be integrated together with the main valve in a common valve block.
- an additional proportional control valve may be provided that is acted upon by the pressure difference between the prevailing at the input high pressure and the pressure prevailing in the secondary circuit between the flow control device and outlet throttle secondary pressure.
- the flow control valve may be connected to a valve body of the main valve adjacent the second valve chamber, so that the valve body of the main valve is acted upon by increasing pressure difference between the high pressure and the secondary pressure in the direction of a decreasing opening cross section of the main valve.
- the proportional control valve supports and accelerates the actuation of the valve piston of the main valve. In principle, however, it is also conceivable to effect the return of the valve piston of the main valve against the application of the secondary pressure with a return spring and to save the proportional control valve.
- the proportional control valve may be designed according to claim 3, in particular as a 3/2-way valve.
- the flow control device preferably consists of a throttle arranged in the secondary circuit and a limiting valve arranged downstream or upstream of the throttle.
- the limiting valve is corresponding Claim 4 driven by the pressure drop across the throttle.
- the limiting valve is preferably designed as a 2/2-way valve according to claim 5.
- the outlet throttle is preferably integrated on the valve body of the main valve according to claim 6. If the power control valve is to limit the power in the working line to a constant maximum power, the opening cross-section of the outlet throttle is designed so that it increases in proportion to the square root of the displacement of the valve body of the main valve.
- a flow control valve and / or a pressure relief valve may be provided. Before reaching the maximum power of the connected hydraulic pump, the entire device then operates in a flow control mode in which the flow control valve adjusts the flow rate in the working line to a constant value. Upon reaching the maximum power of the hydraulic pump, the delivery volume is reduced so that the product of delivery volume and working pressure, so the hydraulic power remains constant. If, however, a maximum pressure is exceeded, the pressure limiting valve responds.
- the power control device 1 shows an exemplary embodiment of the power control device according to the invention, which is designated generally by the reference numeral 1.
- the power control device 1 according to the invention is arranged in a working line 2 between an input 3 and an output 4.
- an adjustable hydraulic pump 17 is connected in the embodiment shown in FIG. 1, while at the output 4 any consumer, such as a hydraulic motor or a hydraulic piston can be connected.
- the power control device 1 comprises a arranged in the working line 2 main valve 5, depending on the position of a valve piston 6, the working line 2 releases, throttles or completely shuts off.
- a secondary circuit 7 is provided, which is fed via a flow control device 8 with a constant volume flow.
- the flow control device 8 is connected via a connecting line 29 to the input 3 and thus to the pressure prevailing in the working line 2 high pressure.
- the flow control device 8 consists of an example of 2/2-way valve designed limiting valve 9 and a downstream throttle 10.
- the throttle 10 has a preferably adjustable but fixed during operation of the power control device 8 throttle cross-section.
- the limiting valve 9 is driven by the pressure drop across the throttle 10. As the pressure drop across the throttle 10 increases, the restriction valve 9 reduces its opening area. Conversely, the opening cross section of the limiting valve 9 is increased when the pressure drop across the throttle 10 decreases. In this way, the pressure drop across the throttle 10 is kept constant, resulting in a constant volume flow, which is fed by the flow control device 8 in the secondary circuit 7.
- the throttle cross section of the outlet throttle 12 is variable and determined by the position of the valve body 6 of the main valve 5. The smaller the opening cross section of the main valve 5, the lower the throttle cross section of the outlet throttle 12.
- the secondary pressure prevailing in the secondary circuit 7 between the throttle 10 of the flow control device 8 and the outlet throttle 12 is supplied to a first valve chamber 13 adjoining the valve piston 6 of the main valve 5.
- the valve body 6 of the main valve 5 is acted upon in the direction of an increasing opening cross-section of the main valve 5.
- a proportional control valve 16 is provided, which is acted upon by the pressure difference between the prevailing in the working line 2 at the input 3 high pressure and the secondary pressure prevailing in the secondary circuit 7. If the secondary pressure prevailing in the secondary circuit 7 drops relative to the high pressure prevailing in the working line 2, the formed in the embodiment as a 3/2-way valve proportional valve 16 so that an adjacent to the valve body 6 of the main valve 5 second valve chamber 14 is increasingly pressurized via a connecting line 15 with pressure, so that the valve body 6 of the main valve 5 increasingly toward one decreasing opening cross section of the main valve 5 is acted upon.
- the second valve chamber 14 is relieved via the connecting line 15 and the proportional control valve 16 to the pressure medium tank 11 out.
- the valve body 6 of the main valve 5 with increasing secondary pressure in the secondary circuit 7 in Fig. 1 to the left in the direction of an increasing opening cross section of the main valve 5 and vice versa with decreasing secondary pressure in the secondary circuit 7 in Fig. 1 to the right towards one decreasing opening cross section of the main valve 5 is applied.
- the second valve chamber 14 and the proportional control valve 16 could also be dispensed with for simplifying the power control device 1 according to the invention and be replaced by a return spring, for example.
- the operation of the power control device 1 according to the invention is the following:
- the secondary circuit 7 continues to be supplied with a constant volumetric flow through the current control device 8. Due to the falling pressure gradient, however, a short-term volume flow compared to the volume flow supplied by means of the flow control device 8 is temporarily removed by the outlet throttle 12 from the secondary circuit 7. This results in a pressure increase in the sub-circuit 7 and thus an increase in the pressure in the first valve chamber 13. Further, the proportional control valve 16 is shifted so that the pressure in the second valve chamber 14 decreases by the second valve chamber 14 to the pressure medium tank 11 is relieved. The valve body 6 of the main valve 5 is deshald shifted in the direction of an increasing opening cross-section of the main valve 5. At the same time, the throttle cross-section of the outlet valve 12 coupled to the main valve 5 is increased, so that a new equilibrium is established between the constant volume flow supplied and the discharged volume flow.
- the opening cross section of the main valve 5 is reduced by the power control device 1 according to the invention, when the high pressure in the working line 2 increases and vice versa, the opening cross section of the power control device 5 increases when the high pressure in the working line 2 falls.
- the opening cross-section of the outlet throttle 12 as a function of the valve lift of the main valve 5 can be achieved that the product of high pressure in the working line 2 and from the flow through the main valve 5, ie the hydraulic power, is adjusted to a constant value, which corresponds for example to the maximum power of the hydraulic pump 17.
- the adjustable hydraulic pump 17 sucks from the pressure medium tank 11, the pressure medium and feeds it into the working line 2 a.
- an adjusting device 18 which has a first actuating piston 19a and a first actuating cylinder 20a and a second actuating piston 19b and a second actuating cylinder 20b.
- a spring 21 which swings the hydraulic pump 17 to maximum displacement.
- a flow control valve 22 and a pressure relief valve 23 are provided in the embodiment shown in FIG.
- the flow control valve 22 compares the pressure in the working line 2 at the input 3 of the power control device 1 with the pressure at the output 4 of the power control device 1, ie it detects the pressure drop across the main valve 5 of the power control device 1.
- the first actuating cylinder 20a is the Actuator 18 increasingly acted upon with control pressure, so that the adjustable hydraulic pump 17 pivots back.
- the first actuating cylinder 20a of the actuator 18 is relieved when the pressure drop across the main valve 5 falls, so that the hydraulic pump 17 is swung to a larger displacement volume.
- the flow control valve 22, a pressure relief valve 23 is connected downstream, which responds as soon as the high pressure in the working line 2 exceeds a predetermined maximum pressure.
- the pressure limiting valve then increases the actuating pressure in the first actuating cylinder 20a of the adjusting device 18 and pivots the hydraulic pump 17 back.
- the power device 1 according to the invention, the flow control valve 22 and the pressure relief valve 23 work together as follows:
- the power control device 1 responds and ensures that the product does not exceed a predetermined power from the high pressure prevailing in the working line 2 and the flow rate flowing in the working line 2.
- the pressure limiting valve 23 responds and pivots the hydraulic pump 17 back so far that the permissible maximum pressure of the working line 2 is not exceeded.
- the power control device 1 can of course also be used with another external circuit.
- the power control device 1 serves to limit the power in any hydraulic working line 2.
- the power control device 1 according to the invention can therefore also be arranged as a compact valve assembly on a position spatially remote with respect to the hydraulic pump 17, for example immediately before the user.
- each consumer may be assigned a separate power control device 1, which is in each case tuned such that a permissible maximum power of the connected consumer is not exceeded.
- FIG. 2 shows a constructive realization of the power control device 1 according to the invention shown in FIG. 1 in a cutaway view.
- the input 3 the output 4 and a terminal 30 for connection to the flow control valve 22.
- the proportional control valve 16 is integrated in an outer housing body 31, the proportional control valve 16 is integrated.
- a valve piston 33 is axially displaceable.
- the valve piston 33 has a thickening 34 and two tapers 35 and 36.
- the valve piston 33 is biased by a return spring 37.
- the axial position of the valve piston 33 is determined by the pressure difference between a connected to the input 3 first valve chamber 38 and connected to the secondary circuit 7 second valve chamber 39 and the position of the mouth of the bore 34.
- valve piston 33 When the high pressure at the inlet 3 with respect to the secondary pressure in the secondary circuit 7 increases, the valve piston 33 is displaced in Fig. 2 upwards, so that the connecting line 15 is increasingly acted upon by the prevailing at the input 3 high pressure and thus the pressure in the second valve chamber 14 of the main valve 5 increases. Conversely, the second valve chamber 14 of the main valve 5 is relieved when the high pressure at the inlet 3 against the secondary pressure in the secondary circuit 7 drops.
- the existing from the limiting valve 9 and the throttle 10 flow control device 8 is located in Fig. 2 below the input 3.
- the valve piston 40 of the limiting valve 9 has two thickened portions 41 and 42 and a taper 43.
- the limiting valve 9 is connected via the connecting line 29 with the input 3 in connection.
- Over two connecting lines 44 and 45 the pressure in front of and behind the throttle 10 is detected and respectively supplied to a first valve chamber 47 and a second valve chamber 48. Further, a return spring 46 is provided.
- the opening area of the restriction valve 9 is reduced. This ensures that the flow control device 8 the secondary circuit 7 regardless of the high pressure at the input 3 supplies a constant volume flow.
- the process from the secondary circuit 7 is regulated via the outlet throttle 12.
- the outlet throttle 12 is integrated with the valve piston 6 of the main valve 5 and adjoins the first valve chamber 13 of the main valve 5.
- the first valve chamber 13 is connected via a connecting line 50 and an annular groove 51 with the secondary circuit 7.
- the outlet throttle 12 is formed by a stationary pin 52 cooperating with an annular body 53 and releasing a gap 54 which depends on the valve stroke b and which is rectangular in the exemplary embodiment.
- Fig. 3 the area of the outlet throttle 12 is shown in a sectional view corresponding to the viewing direction A in Fig. 2 again, wherein the annular body 53, the pin 52 and rectangular in the embodiment gap 54 can be seen.
- the gap 54 has a constant gap length a and a gap width h dependent on the valve stroke b.
- the valve lift is indicated in Fig. 2 by an arrow.
- the smallest valve lift b results when the thickening 55 of the valve body 6 completely closes the annular groove 56 in the inner housing body 57.
- the largest valve lift b results when the annular groove 58 of the valve body 6 completely overlaps with the annular groove 56 leading to the outlet 4, as shown in FIG.
- the geometric dependence of the throttle opening of the outlet throttle 54 as a function of the valve lift b determines the control characteristic of the invention Power control device 1.
- the power control device 1 according to the invention is operated so that it limits the hydraulic power to a predetermined constant power.
- this can be achieved if, at a constant gap length a, the gap width h (b) dependent on the valve lift b is proportional to the square root of the valve lift b. As can be seen from Fig. 2, therefore, the flank of the pin 52 is formed accordingly.
- the specified geometric relationship between the gap width h and the valve lift b results from the considerations described below.
- A is the inflow cross section, A from the outflow cross section, V to the inflow velocity and V from the Outflow velocity.
- the relations used for the inflow velocity v to and the outflow velocity v ab are derived from the Bernoulli equation of motion for incompressible fluids (see, for example, BHJ Matthies "Introduction to Oil Hydraulics", Teubner organizations founded, page 35).
- ⁇ denote the density of the pressure medium used, if ⁇ a friction value, ⁇ p the pressure drop at the throttle 10 and p x the secondary pressure in the secondary circuit 7.
- the pressure in the secondary circuit 7 p x corresponds to the pressure drop at the outlet throttle 12, since this leads directly to the pressure medium tank 11.
- the inflow cross section A to and the pressure difference ⁇ p at the inflow throttle 10 are constant quantities.
- a a b a ⁇ H
- a is the constant column length
- h is the gap width dependent on the valve lift b.
- the power control device 1 therefore provides a constant power when the gap width h is proportional to the square root of the valve lift b, which can be achieved by a corresponding geometric configuration of the pin 52 readily in the embodiment shown in FIG. Basically it is possible, the functional relationship between the gap width h and the flow cross-section A, and the valve b in other ways to choose a different control characteristics of the power control device 1 according to the invention which can be achieved.
- the gap length a of the outlet throttle 54 need not be constant.
- annular throttle gap and form the pin 52 for example, as a rotationally symmetrical body, which can be realized in manufacturing technology easier.
- the function of the radius of the rotationally symmetric pin 52 as a function of the valve lift b can be determined either numerically or by experiments in a simple manner and manufacture easily in a numerically controlled manufacturing machine.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
Claims (9)
- Dispositif de régulation de puissance (1) pour la régulation de la puissance hydraulique dans une conduite de travail (2) comprenant une valve principale (5) agencée entre une entrée (3) et une sortie (4) dans la conduite de travail (4) et comprenant un corps de valve (6) qui libère ou qui étrangle la conduite de travail (2) en fonction de sa position,
un dispositif de régulation de courant (8) relié à l'entrée (3) qui conduit un courant volumétrique constant (Qzu) à un circuit annexe (7),
un étranglement d'évacuation (12) agencé dans le circuit annexe (7), dont la section d'étranglement (Aab) dépend de la position du corps de valve (6) de la valve principale (5), et
une première chambre de valve (13) adjacente au corps de valve (6) de la valve principale (5), chambre qui est agencée dans le circuit annexe (7) entre le dispositif de régulation de courant (8) et l'étranglement d'évacuation (12) et qui applique au corps de valve (6) une pression annexe croissante (px) dans le circuit annexe (7) en direction d'une augmentation de la section d'ouverture (Abgr) de la valve principale (5),
dans lequel est prévue une valve de régulation proportionnelle (16) qui est attaquée par la différence de pression entre la haute pression (pHD) qui règne à l'entrée (3) et la pression annexe (px) qui règne entre le dispositif de régulation de courant (8) et l'étranglement d'évacuation (12). - Dispositif de régulation de puissance selon la revendication 1,
caractérisé en ce que
la valve de régulation proportionnelle (16) est reliée à une seconde chambre de valve (14), adjacente au corps de valve (6) de la valve principale (5) de telle façon que le corps de valve (6) de la valve principale (5) est sollicité lors d'une augmentation de la différence de pression entre la haute pression (pHD) et la pression auxiliaire (px) en direction d'une réduction de la section d'ouverture (Abgr) de la valve principale (5). - Dispositif de régulation de puissance selon la revendication 1 ou 2,
caractérisé en ce que
la valve de régulation proportionnelle (16) est une valve 3 voies/2 positions. - Dispositif de régulation de puissance selon l'une quelconque des revendications 1 à 3,
caractérisé en ce que
le dispositif de régulation de courant (8) est constitué par un étranglement (10) agencé dans le circuit annexe (7) et par une valve de limitation (9) agencée dans le circuit annexe (7), en amont ou en aval de l'étranglement (10), ladite valve de limitation (9) étant pilotée par la chute de pression au niveau de l'étranglement (10). - Dispositif de régulation de puissance selon la revendication 4,
caractérisé en ce que
la valve de limitation (9) est une valve 2 voies/2 positions. - Dispositif de régulation de puissance selon l'une quelconque des revendications 1 à 5,
caractérisé en ce que
l'étranglement d'évacuation (12) est réalisé sur le corps de valve (6) de la valve principale (5), la section d'étranglement (Aab) de l'étranglement d'évacuation (12) augmentant avec l'augmentation de la section d'ouverture (Abgr) de la valve principale (5). - Dispositif de régulation de puissance selon la revendication 6,
caractérisé en ce que
le dispositif de régulation de puissance (1) limite la puissance dans la conduite de travail (2) à une puissance constante, la section d'ouverture (Aab) de l'étranglement d'évacuation (12) augmentant proportionnellement à la racine carrée de la course (b) de la valve principale (5). - Dispositif de régulation de puissance selon l'une quelconque des revendications 1 à 7,
caractérisé en ce que
le dispositif de régulation de puissance (1) est intégré dans la conduite de travail (2) d'une pompe hydraulique réglable (17) et sert à la chute de pression via la valve principale (5) pour le pilotage d'un dispositif de réglage (18) de la pompe hydraulique (17). - Dispositif de régulation de puissance selon la revendication 8,
caractérisé en ce que
une valve de régulation de courant de refoulement (22) et/ou une valve de limitation de pression (23) est/sont agencée(s) entre l'entrée (3) et la sortie (4) du dispositif de régulation de puissance (1) et du dispositif de réglage (18).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE1998131586 DE19831586C2 (de) | 1998-07-14 | 1998-07-14 | Leistungsregelvorrichtung zur Regelung der hydraulischen Leistung in einer Arbeitsleitung |
DE19831586 | 1998-07-14 |
Publications (3)
Publication Number | Publication Date |
---|---|
EP0972940A2 EP0972940A2 (fr) | 2000-01-19 |
EP0972940A3 EP0972940A3 (fr) | 2000-09-27 |
EP0972940B1 true EP0972940B1 (fr) | 2006-08-30 |
Family
ID=7874042
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP19990113344 Expired - Lifetime EP0972940B1 (fr) | 1998-07-14 | 1999-07-09 | Dispositif de contrôle de puissance pour la régulation de la puissance hydraulique dans un circuit de travail |
Country Status (2)
Country | Link |
---|---|
EP (1) | EP0972940B1 (fr) |
DE (2) | DE19831586C2 (fr) |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4293284A (en) * | 1979-10-09 | 1981-10-06 | Double A Products Company | Power limiting control apparatus for pressure-flow compensated variable displacement pump assemblies |
US4710106A (en) * | 1984-11-26 | 1987-12-01 | Nippondenso Co., Ltd. | Volume controlling device for variable volume pump |
DE19626793C1 (de) * | 1996-07-03 | 1997-06-26 | Brueninghaus Hydromatik Gmbh | Hydraulische Regeleinrichtung zum parallelen Regeln mehrerer hydrostatischer Verstellpumpen |
-
1998
- 1998-07-14 DE DE1998131586 patent/DE19831586C2/de not_active Expired - Fee Related
-
1999
- 1999-07-09 EP EP19990113344 patent/EP0972940B1/fr not_active Expired - Lifetime
- 1999-07-09 DE DE59913813T patent/DE59913813D1/de not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
---|---|
DE19831586A1 (de) | 2000-02-03 |
EP0972940A3 (fr) | 2000-09-27 |
DE59913813D1 (de) | 2006-10-12 |
DE19831586C2 (de) | 2000-05-18 |
EP0972940A2 (fr) | 2000-01-19 |
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