EP1049874B1 - Axial piston pump - Google Patents
Axial piston pump Download PDFInfo
- Publication number
- EP1049874B1 EP1049874B1 EP99903678A EP99903678A EP1049874B1 EP 1049874 B1 EP1049874 B1 EP 1049874B1 EP 99903678 A EP99903678 A EP 99903678A EP 99903678 A EP99903678 A EP 99903678A EP 1049874 B1 EP1049874 B1 EP 1049874B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- swash plate
- axial piston
- pump housing
- shaft
- piston pump
- 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
Links
- 230000003068 static effect Effects 0.000 description 4
- 238000005452 bending Methods 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 230000004308 accommodation Effects 0.000 description 1
- 230000000903 blocking effect Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 238000005553 drilling Methods 0.000 description 1
- 230000002265 prevention Effects 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 238000009987 spinning Methods 0.000 description 1
- 230000006641 stabilisation Effects 0.000 description 1
- 238000011105 stabilization Methods 0.000 description 1
Images
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
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/14—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
Definitions
- the invention relates to an axial piston pump with a Pump housing, a motor-driven shaft, one with the shaft rotatably connected swash plate and one Number of pistons that swings back and forth using the swash plate can be moved here, as described, for example, in DE-B-1 234 529 or DE 44 45 522 A1.
- Such axial piston pumps are used, among other things.
- electronic Brake systems for motor vehicles used with regulated blocking prevention devices individual wheels when braking, to prevent the Spinning the driven wheels and others Devices for active vehicle stabilization can be equipped.
- Devices for active vehicle stabilization can be equipped.
- the functioning of such braking systems depends on the fact that all components of the system with regard to the expected static and dynamic loads on the one hand, robust and designed to be as wear-resistant as possible but also the demands for space and Weight saving as well as economical Manufacturing meet.
- a central bore is provided in a generic axial piston pump in the pump housing, through which an extension of the shaft extends, at the end of which the swash plate is arranged outside the pump housing.
- the swash plate is advantageously arranged in a cover, which can be designed as a valve block or electronics box of an electronic brake system.
- the pump pistons are advantageously arranged between the swash plate and the pump drive motor. It is also proposed that the pistons are clamped between the swash plate and the inner end of the bores by means of the return springs.
- a shaft bearing is expediently axially supported on the surface of a stepped bore of the pump housing, which is opposite the inner end of the bores.
- the proposal according to the invention has the great advantage that the frictional connection over the extension stressed in tension the shaft takes place and from the housing only the part between Bearing and inner end of the holes in the Main direction of force is subjected to pressure. Furthermore becomes the frictional connection over the bearing under pressure and the pistons also under pressure and Return springs as well as the stressed on bending Swashplate closed.
- the housing has essentially only absorb lateral forces, i.e. the components that not parallel to the axis of the shaft or the bores are directed.
- the required larger space requirement for the holes in radial direction doesn't matter because that Pump housing for the attachment of the drive motor usually larger in any case transversely to the shaft axis must be carried out as it is for the accommodation of the Bores for the pistons are required. Besides, will the larger space requirement in the radial direction by one less space requirement of the pump housing in the axial Direction compensated because the channels for the inlet and Removal of the medium is no longer arranged on the edge are, but in the middle of the case and because only in the central part that of the bearing height, the piston length and the thickness of the swash plate including the bearing dependent full height of the pump housing can be realized got to.
- the motor-driven shaft 2 has an extension 9, on the end of which a swash plate 3 with an axial bearing 13 is rotatably attached.
- a bearing 6 is arranged between the shaft 2 and the pump housing 1, via which radial and axial forces can be transmitted from the shaft 2 to the pump housing 1.
- holes 7 for pistons 4 and return springs 5, preferably rounded at the front are arranged parallel to the shaft axis, the inner ends 10 of which face a surface 11 of the stepped bore 12 formed in the housing 1 for the bearing 6.
- the material area of the pump housing 1 lying between the inner ends 10 of the bores 7 and the surface 11 is the only part of the pump housing which has to absorb forces in the main direction of attack parallel to the shaft axis. Adjacent to the inner ends 10, the bores 7 are connected to channels 14 and 15 formed in the pump housing 1 for the supply and discharge of the delivery medium.
- the extension 9 of the shaft 2 is, according to the invention, passed through a central bore 8 in the pump housing 1, which is closed by a cover 16 which overlaps the swash plate 3 and which does not have to be part of the pump housing.
- the cover is designed as a valve block and / or electronics box of an electronically controlled braking system.
- the pistons are therefore preferably arranged between the swash plate 3 and the motor (not shown) driving the pump 1. Opposite the cover 16, a receiving area 17 for the arrangement of the drive motor for the shaft 2 is provided in the pump housing 1.
- the pump housing 1 can be flatter overall be held because only the central area is the full, by the dimensions of the bearing 6, the return springs 5, the piston 4 and the swash plate 3 due to design must have full height.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Reciprocating Pumps (AREA)
- Valves And Accessory Devices For Braking Systems (AREA)
Description
Die Erfindung betrifft eine Axialkolbenpumpe mit einem Pumpengehäuse, einer motorisch antreibbaren Welle, einer mit der Welle drehfest verbundenen Taumelscheibe und einer Anzahl von Kolben, die mittels der Taumelscheibe hin- und herbewegbar sind, wie sie beispielsweise in der DE-B-1 234 529 oder DE 44 45 522 A1 beschrieben ist.The invention relates to an axial piston pump with a Pump housing, a motor-driven shaft, one with the shaft rotatably connected swash plate and one Number of pistons that swings back and forth using the swash plate can be moved here, as described, for example, in DE-B-1 234 529 or DE 44 45 522 A1.
Derartige Axialkolbenpumpen werden u.a. in elektronischen Bremssystemen für Kraftfahrzeuge verwendet, die mit geregelten Einrichtungen zur Verhinderung des Blockierens einzelner Räder beim Bremsen, zur Verhinderung des Durchdrehens der angetriebenen Räder sowie weiteren Einrichtungen zur aktiven Fahrzeugstabilisierung ausgestattet sein können. Für das dauerhaft zuverlässige Funktionieren solcher Bremssysteme kommt es darauf an, daß sämtliche Komponenten des Systems im Hinblick auf die zu erwartenden statischen und dynamischen Beanspruchungen einerseits robust und möglichst verschleißarm ausgelegt werden, andererseits aber auch den Forderungen nach Platzund Gewichtsersparnis sowie nach wirtschaftlicher Herstellung gerecht werden.Such axial piston pumps are used, among other things. in electronic Brake systems for motor vehicles used with regulated blocking prevention devices individual wheels when braking, to prevent the Spinning the driven wheels and others Devices for active vehicle stabilization can be equipped. For the permanently reliable The functioning of such braking systems depends on the fact that all components of the system with regard to the expected static and dynamic loads on the one hand, robust and designed to be as wear-resistant as possible but also the demands for space and Weight saving as well as economical Manufacturing meet.
Bei Axialkolbenpumpen kann man eine kompakte Bauweise erreichen, indem die Bohrungen für die Kolben im Pumpengehäuse auf einem Kreis mit möglichst kleinem Durchmesser angeordnet werden, wobei dann auch der Durchmesser der Taumelscheibe klein gehalten werden kann. Diese Anordnung hat jedoch den Nachteil, daß die Kanäle für die Zu- und Abfuhr des Fördermediums am äußeren Rand des Pumpengehäuses angeordnet werden müssen, und daß sich die statischen und dynamischen Reaktionskräfte im wesentlichen als Zugkräfte im Gehäuse auswirken, das aufgrund der Vielzahl von Bohrungen kein homogener Baukörper mehr ist, in dem die Kraftlinien sehr unübersichtlich verlaufen und in dem Spannungsspitzen auftreten können, was in Verbindung mit kleinsten Material- oder Fertigungsfehlern eine Versagensgefahr bedeuten könnte.With axial piston pumps you can have a compact design achieve by drilling the pistons in the Pump housing on a circle with the smallest possible Diameter can be arranged, with the Swash plate diameter can be kept small. However, this arrangement has the disadvantage that the channels for the supply and discharge of the medium at the outer edge of the Pump housing must be arranged, and that the static and dynamic reaction forces essentially impact as tensile forces in the housing, which due to Large number of holes is no longer a homogeneous structure, in which the lines of force run very confusing and in which voltage spikes can occur, what in connection with the smallest material or manufacturing defects Could mean failure.
Es besteht somit die Aufgabe, eine Axialkolbenpumpe der eingangs genannten Art so weiterzubilden, daß die genannten Nachteile überwunden werden können. Dabei soll einerseits der Kraftfluß besser überschaubar und andererseits die Randlage der Kanäle im Gehäuse möglichst vermieden werden, damit günstigere Gestaltungsmöglichkeiten für die äußeren Anschlüsse geschaffen werden können. Außerdem soll der zur Verfügung stehende Bauraum, beispielsweise eines elektronischen Bremssystems, optimal genutzt werden.There is therefore the task of an axial piston pump type mentioned in such a way that the mentioned Disadvantages can be overcome. On the one hand the flow of power is more manageable and on the other hand the The edge of the channels in the housing should be avoided if possible, thus cheaper design options for the outside Connections can be created. In addition, the Available space, for example one electronic braking system can be used optimally.
Zur Lösung dieser Aufgabe wird erfindungsgemäß
vorgeschlagen, daß bei einer gattungsgemäßen
Axialkolbenpumpe im Pumpengehäuse eine zentrale Bohrung
vorgesehen ist, durch die sich eine Verlängerung der Welle
hindurch erstreckt, an deren Ende die Taumelscheibe
außerhalb des Pumpengehäuses angeordnet ist. Mit Vorteil
ist dabei die Taumelscheibe in einer Abdeckung angeordnet,
die als Ventilblock bzw. Elektronikbox eines elektronischen
Bremssystems ausgebildet sein kann.
In vorteilhafter Weise sind die Pumpenkolben zwischen
Taumelscheibe und dem Pumpenantriebsmotor angeordnet.
Ferner wird vorgeschlagen, daß die Kolben mittels der
Rückstellfedern zwischen der Taumelscheibe und dem inneren
Ende der Bohrungen eingespannt sind. Ein Wellenlager ist
zweckmäßigerweise axial auf derjenigen Fläche einer
Stufenbohrung des Pumpengehäuses abgestützt, die dem
inneren Ende der Bohrungen gegenüberliegt.To achieve this object, it is proposed according to the invention that a central bore is provided in a generic axial piston pump in the pump housing, through which an extension of the shaft extends, at the end of which the swash plate is arranged outside the pump housing. The swash plate is advantageously arranged in a cover, which can be designed as a valve block or electronics box of an electronic brake system.
The pump pistons are advantageously arranged between the swash plate and the pump drive motor. It is also proposed that the pistons are clamped between the swash plate and the inner end of the bores by means of the return springs. A shaft bearing is expediently axially supported on the surface of a stepped bore of the pump housing, which is opposite the inner end of the bores.
Der erfindungsgemäße Vorschlag hat den großen Vorteil, daß der Kraftschluß uber die auf Zug beanspruchte Verlängerung der Welle erfolgt und vom Gehäuse nur der Teil zwischen Lager und innerem Ende der Bohrungen in der Hauptkraftrichtung auf Druck beansprucht wird. Im übrigen wird der Kraftschluß über das auf Druck beanspruchte Lager und die ebenfalls auf Druck beanspruchten Kolben und Rückstellfedern sowie über die auf Biegung beanspruchte Taumelscheibe geschlossen. Das Gehäuse hat im wesentlichen nur noch Querkräfte aufzunehmen, d.h. die Komponenten, die nicht parallel zur Achse der Welle bzw. der Bohrungen gerichtet sind.The proposal according to the invention has the great advantage that the frictional connection over the extension stressed in tension the shaft takes place and from the housing only the part between Bearing and inner end of the holes in the Main direction of force is subjected to pressure. Furthermore becomes the frictional connection over the bearing under pressure and the pistons also under pressure and Return springs as well as the stressed on bending Swashplate closed. The housing has essentially only absorb lateral forces, i.e. the components that not parallel to the axis of the shaft or the bores are directed.
Der erforderliche größere Platzbedarf für die Bohrungen in radialer Richtung spielt keine große Rolle, weil das Pumpengehäuse für die Anbringung des Antriebsmotors üblicherweise quer zur Wellenachse ohnehin größer ausgeführt werden muß, als es für die Unterbringung der Bohrungen für die Kolben erforderlich ist. Außerdem wird der größere Platzbedarf in radialer Richtung durch einen geringeren Platzbedarf des Pumpengehäuses in axialer Richtung kompensiert, weil die Kanäle für die Zu- und Abfuhr des Fördermediums nicht mehr randseitig angeordnet sind, sondern in mittlerer Höhe des Gehäuses und weil nur im zentralen Teil die von der Lagerhöhe, der Kolbenlänge und der Dicke der Taumelscheibe einschließlich Lager abhängige volle Höhe des Pumpengehäuses realisiert werden muß.The required larger space requirement for the holes in radial direction doesn't matter because that Pump housing for the attachment of the drive motor usually larger in any case transversely to the shaft axis must be carried out as it is for the accommodation of the Bores for the pistons are required. Besides, will the larger space requirement in the radial direction by one less space requirement of the pump housing in the axial Direction compensated because the channels for the inlet and Removal of the medium is no longer arranged on the edge are, but in the middle of the case and because only in the central part that of the bearing height, the piston length and the thickness of the swash plate including the bearing dependent full height of the pump housing can be realized got to.
Vorteilhafte Weiterbildungen des Erfindungsgedankens sind in den Unteransprüchen beschrieben. Weitere Einzelheiten werden anhand des in Figur 1 dargestellten Ausführungsbeispiels näher erläutert.
Figur 1- zeigt einen Längsschnitt durch den zentralen Teil eines Pumpengehäuses (1) für eine Axialkolbenpumpe gemäß der Erfindung.
- Figure 1
- shows a longitudinal section through the central part of a pump housing (1) for an axial piston pump according to the invention.
Die motorisch antreibbare Welle 2 besitzt eine Verlängerung
9, an der endseitig eine Taumelscheibe 3 mit einem
Axiallager 13 drehfest angebracht ist. Zwischen der Welle 2
und dem Pumpengehäuse 1 ist ein Lager 6 angeordnet, über
das radiale und axiale Kräfte von der Welle 2 auf das
Pumpengehäuse 1 übertragen werden können. Auf einem zur
Verlängerung 9 der Welle 2 konzentrisch angeordnetem Kreis
sind parallel zur Wellenachse Bohrungen 7 für vorzugsweise
stirnseitig abgerundete Kolben 4 und Rückstellfedern 5
angeordnet, deren innere Enden 10 einer Fläche 11 der im
Gehäuse 1 ausgebildeten Stufenbohrung 12 für das Lager 6
gegenüberliegen. Der zwischen den inneren Enden 10 der
Bohrungen 7 und der Fläche 11 liegende Materialbereich des
Pumpengehäuses 1, ist der einzige Teil des Pumpengehäuses,
der Kräfte in der Hauptangriffsrichtung parallel zur
Wellenachse aufnehmen muß. Benachbart zu den inneren Enden
10 sind die Bohrungen 7 mit im Pumpengehäuse 1
ausgebildeten Kanälen 14 und 15 fur die Zu- bzw. Abfuhr des
Fördermediums verbunden.
Die Verlängerung 9 der Welle 2 ist erfindungsgemäß durch
eine zentrale Bohrung 8 im Pumpengehäuse 1 hindurchgeführt,
die von einer die Taumelscheibe 3 übergreifenden Abdeckung
16, die nicht Teil des Pumpengehäuses sein muß,
abgeschlossen ist. In besonders vorteilhafter Weise ist die
Abdeckung als Ventilblock und/oder Elektronikbox eines
elektronisch geregelten Bremssystems ausgebildet.
Erfindungsgemäß sind die Kolben also bevorzugt zwischen der
Taumelscheibe 3 und dem die Pumpe 1 antreibenden Motor
(nicht dargestellt) angeordnet. Der Abdeckung 16
gegenüberliegend ist im Pumpengehäuse 1 ein Aufnahmebereich
17 für die Anordnung des Antriebsmotors für die Welle 2
vorgesehen.The motor-driven
The
According to the invention, the pistons are therefore preferably arranged between the
Aus Figur 1 ist ohne weiteres ersichtlich, daß die
statischen und dynamischen Kräfte beim Betrieb der
Axialkolbenpumpe in einem kurzen und übersichtlichen
Kraftschluß verlaufen. Die parallel zur Wellenachse
wirkenden statischen Kräfte der Federn 5 und die in
gleicher Richtung verlaufenden Hauptkomponenten der durch
die Bewegung der Taumelscheibe 3 erzeugten dynamischen
Kräfte, wirken sich in der Verlängerung der Welle 2 als
Zugkräfte aus, die über Biegekräfte in der Taumelscheibe 3
sowie Druckkräfte in den Kolben 4, den Federn 5, einem
kurzen Wandteil des Pumpengehäuses 1 sowie im Wellenlager 6
aufgenommen werden. Damit ist das Pumpengehäuse 1 praktisch
frei von Beanspruchungen in der Hauptkraftrichtung und muß
nur noch im Hinblick auf die unvermeidbaren Querkräfte
ausgelegt werden. Dies ermoglicht eine platz- und
gewichtssparende Ausführung des Pumpengehäuses 1, das
festigkeitsmäßig weniger beansprucht ist und für das aus
diesem Grunde auch weniger hochfeste Werkstoffe verwendet
werden können.From Figure 1 it is readily apparent that the
static and dynamic forces during the operation of the
Axial piston pump in a short and clear
Traction. The parallel to the shaft axis
acting static forces of the
Als besonders vorteilhaft wird angesehen, daß die zwischen
Stirnfläche der Kolben 4 und innerem Ende der Bohrungen 7
ausgebildeten Förderkammern nicht mehr randseitig im
Gehäuse 1 liegen, so daß für die Anordnung der Kanäle 14,
15 zur Zu- bzw. Abfuhr des Fördermediums sowie deren äußere
Anschlüsse bessere Gestaltungsmöglichkeiten bestehen.
Außerdem kann das Pumpengehäuse 1 insgesamt flacher
gehalten werden, weil nur der zentrale Bereich die volle,
durch die Abmessungen des Lagers 6, der Rückstellfedern 5,
der Kolben 4 und der Taumelscheibe 3 konstruktiv bedingte
volle Höhe aufweisen muß.It is considered particularly advantageous that the between
End face of the pistons 4 and inner end of the bores 7
trained delivery chambers no longer in the
Claims (7)
- Axial piston pump comprising a pump housing (1), a motor-driven shaft (2), a swash plate (3) connected to the shaft (2) in a rotationally fixed manner, and a number of pistons (4) which are movable to and fro by means of the swash plate (3), wherein the shaft (2) extends through the pump housing (1) and the swash plate (3) is arranged outside the pump housing (1) in a cover (16),
characterized in that the cover (16) is configured as a valve block and/or as an electronic box of an electronic brake system. - Axial piston pump as claimed in claim 1,
characterized in that the pistons (4) are arranged between the swash plate (3) and the motor driving the shaft (2). - Axial piston pump as claimed in claim 1,
characterized in that the pistons (4) are compressed by way of resetting springs (5) between the swash plate (3) and the inner end (10) of the bores (7) that accommodate the pistons (4). - Axial piston pump as claimed in claim 3,
characterized in that a bearing (6) of the shaft (2) is supported axially on a surface (11) of a stepped bore (12) of the pump housing (1) which is opposite to the inner end (10) of the bores (7). - Axial piston pump as claimed in any one of the preceding claims,
characterized in that an axial bearing (13) is arranged between the swash plate (3) and the piston (4). - Axial piston pump as claimed in claim 5,
characterized in that the ends of the pistons (4) facing the axial bearing (13) are rounded. - Axial piston pump as claimed in any one of the preceding claims,
characterized in that the bores (7) are connected to channels (14, 15) provided in the pump housing (1) for the supply and/or discharge of the flow medium.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE19803533A DE19803533A1 (en) | 1998-01-30 | 1998-01-30 | Axial piston pump |
| DE19803533 | 1998-01-30 | ||
| PCT/EP1999/000448 WO1999039100A1 (en) | 1998-01-30 | 1999-01-26 | Axial piston pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP1049874A1 EP1049874A1 (en) | 2000-11-08 |
| EP1049874B1 true EP1049874B1 (en) | 2003-05-02 |
Family
ID=7856093
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP99903678A Expired - Lifetime EP1049874B1 (en) | 1998-01-30 | 1999-01-26 | Axial piston pump |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP1049874B1 (en) |
| JP (1) | JP2002502007A (en) |
| DE (2) | DE19803533A1 (en) |
| WO (1) | WO1999039100A1 (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102008014974B4 (en) * | 2008-03-19 | 2016-06-23 | Schaeffler Technologies AG & Co. KG | Swash bearing and method for its production |
| JP4740983B2 (en) * | 2008-06-18 | 2011-08-03 | 三菱電機株式会社 | Fuel supply device |
| CN102966504B (en) * | 2012-12-10 | 2015-08-12 | 西安航空动力控制科技有限公司 | With baffle-type check valve without the axial piston pump of piston shoes without oil distribution casing |
Family Cites Families (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1877285A (en) * | 1931-10-01 | 1932-09-13 | Eckels Engineering Corp | Swash plate |
| US2998827A (en) * | 1958-04-14 | 1961-09-05 | Ernest E Cook | Valve construction for fluid pressure pump and the like |
| DE1234529B (en) * | 1963-11-13 | 1967-02-16 | Teves Kg Alfred | Axial roller bearings of the head swash plate of an axial piston pump |
| DE1453532A1 (en) * | 1964-04-07 | 1969-09-25 | Walter Hunger | Hydraulic support devices for motor vehicles that can be operated by hand or by electric motor |
| FR1407267A (en) * | 1964-06-20 | 1965-07-30 | Sarl Rech S Etudes Production | Advanced hydraulic pump, barrel and fluid bearings |
| JPS5011086B1 (en) * | 1967-06-14 | 1975-04-26 | ||
| DE3347307A1 (en) * | 1983-12-28 | 1985-07-11 | Speck-Kolbenpumpen-Fabrik Otto Speck Kg, 8192 Geretsried | PLUNGER PUMP |
| DE4203619C2 (en) * | 1992-02-07 | 1996-07-25 | Rexroth Mannesmann Gmbh | Hydraulic system |
| DE4303205A1 (en) * | 1993-02-04 | 1994-08-11 | Teves Gmbh Alfred | Pump, made of material produced in a continuous process, with a valve block, especially for a controlled braking system |
| DE4445522C2 (en) | 1994-12-20 | 1998-05-14 | Kaercher Gmbh & Co Alfred | Piston pump for a high pressure cleaning device |
-
1998
- 1998-01-30 DE DE19803533A patent/DE19803533A1/en not_active Withdrawn
-
1999
- 1999-01-26 WO PCT/EP1999/000448 patent/WO1999039100A1/en active IP Right Grant
- 1999-01-26 EP EP99903678A patent/EP1049874B1/en not_active Expired - Lifetime
- 1999-01-26 DE DE59905314T patent/DE59905314D1/en not_active Expired - Lifetime
- 1999-01-26 JP JP2000529539A patent/JP2002502007A/en active Pending
Also Published As
| Publication number | Publication date |
|---|---|
| EP1049874A1 (en) | 2000-11-08 |
| DE59905314D1 (en) | 2003-06-05 |
| WO1999039100A1 (en) | 1999-08-05 |
| JP2002502007A (en) | 2002-01-22 |
| DE19803533A1 (en) | 1999-08-05 |
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