EP0970309B1 - Radial piston pump for feeding high pressure fuel - Google Patents
Radial piston pump for feeding high pressure fuel Download PDFInfo
- Publication number
- EP0970309B1 EP0970309B1 EP98963344A EP98963344A EP0970309B1 EP 0970309 B1 EP0970309 B1 EP 0970309B1 EP 98963344 A EP98963344 A EP 98963344A EP 98963344 A EP98963344 A EP 98963344A EP 0970309 B1 EP0970309 B1 EP 0970309B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- piston pump
- radial piston
- drive shaft
- bucket
- pump according
- 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
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
- F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B1/0404—Details or component parts
- F04B1/0439—Supporting or guiding means for the pistons
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
- F02M59/04—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps
- F02M59/06—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps with cylinders arranged radially to driving shaft, e.g. in V or star arrangement
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
- F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
-
- 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
- F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B1/0404—Details or component parts
- F04B1/0421—Cylinders
Definitions
- the invention relates to a radial piston pump for High pressure fuel supply at Fuel injection systems of internal combustion engines, especially with a common rail injection system a drive shaft mounted in a pump housing, the is eccentric or in the circumferential direction has cam-like elevations, and preferably with several radially in one with respect to the drive shaft respective cylinder space arranged pistons, which by Turn the drive shaft in the respective cylinder space in radial direction are movable back and forth.
- the present Invention not only used in a radial piston pump can be, but also with high pressure pumps in particular with a demand quantity regulation.
- the invention is therefore based on the problem of a Radial piston pump to provide these disadvantages avoids and a further improved efficiency as well a further increased resilience with low Has manufacturing costs.
- Damage to the piston foot, such as cage breaks, is prevented be, so that the proper operation of the Radial piston pump is guaranteed even with partial filling.
- the radial piston pump according to the invention should Withstand pump pressures of up to 2000 bar.
- the openings according to the invention serve to equalize the pressure and ensure that even when the full Hubes only a minimal pressure difference between which the Drive shaft surrounding space and the respective Cylinder space results. This keeps the increase in Hertzian pressure in the useful stroke is low and in the suction stroke a full filling of the element is guaranteed. So is a high one even at peak pressures up to 2000 bar Guaranteed piston life.
- Another special embodiment of the invention is characterized in that the tappet each in a hole in the housing is guided, which is in the same direction as the associated cylinder space extends.
- the guidance enables even at high Pump pressures and rapid load changes make a round trip Movement of the lateral force absorption device. In particular becomes a tilting of the tappet in the cylinder space avoided.
- Another special embodiment of the invention is characterized in that the bottom of the tappet from a force plate is formed.
- the Force plate is in contact with the Drive shaft and can, depending on the load have different thickness.
- the surface of the Force plate can be specially treated to a to ensure high wear resistance.
- Another special embodiment of the invention is characterized in that the force absorption plate by the cup-shaped body connected with a guide ring is.
- the guide ring slides in the cylinder space. With area in contact with the cylinder space be specially treated to reduce the frictional forces minimize.
- the guide ring ensures that the Transverse force absorption device is not in the cylinder space canted.
- the dimensions of the guide ring depend on Pump pressure and the number of load changes per Time unit.
- Another special embodiment of the invention is characterized in that the pistons each by a Spring against the associated force plate of the Cup tappet are pressed. Through the spring force the piston moves toward the drive shaft so that fuel is sucked in. It is also possible that the Force plate of the tappet by a spring is pressed against the drive shaft. However, it would be in this case, that the force plate is connected to the piston to suck in To ensure fuel. If the piston is directly with the This force can be applied to the spring force between force plate and piston are eliminated.
- This Variant has the advantage that a so executed Radial piston pump manufactured easily and inexpensively can be. In addition, the application is in this variant of the present invention on known radial piston pumps easily possible.
- Another special embodiment of the invention is characterized in that the force receiving plate on the slightly convex towards the drive shaft is trained.
- the convex formation of the Force absorption plate serves to establish the contact area between Reduce drive shaft and force plate. This will move the drive shaft onto the tappet applied moment advantageously reduced.
- the design of the force plate must be elastic Deformation of the cup tappet must be taken into account.
- Another special embodiment of the invention is characterized in that between the drive shaft and a ring is arranged on the tappets.
- the ring serves to transfer the forces from the drive shaft to the Force absorbing plate.
- the ring is advantageously sliding on the drive shaft.
- the ring can either be cylindrical or polygonal.
- the present invention generally has the advantage that it can be implemented simply and inexpensively. Moreover the basic idea of the present invention can be found in simple way on existing radial piston pumps applied by e.g. one provided on the piston Ram plate is replaced by a bucket tappet. About that In addition, the component strength, especially with a Zero funding in suction stroke, increased.
- Figures 1 and 2 show a radial piston pump High pressure fuel supply at Fuel injection systems for internal combustion engines.
- the Radial piston pump is with an integrated Required quantity control.
- the fuel supply and dimensioning takes place via a not shown Metering unit.
- the radial piston pump according to the invention is particularly in Common rail fuel injection systems for Diesel engines used.
- “Common rail” means as much as “common management” or “common rail”.
- Injectors in common rail injection systems from one fed common line Injectors in common rail injection systems from one fed common line.
- the radial piston pump shown in Figures 1 and 2 comprises a stored in a pump housing 2 Drive shaft 4 with an eccentrically designed Shaft section 6.
- a ring 8 is provided, against which the Shaft section 6 is rotatable.
- the ring 8 comprises three each flattened 10 offset from each other by 120 ° a piston 12 is supported in each case.
- the pistons 12 are each in a cylinder chamber 18 to the drive shaft 4 in radial direction back and forth added.
- a spring plate 13 is attached to each Spring 14 is biased.
- the spring 14 presses the piston 12 against a force absorption plate 15 which leads to a Tappet 9 belongs, which is enlarged on a 2: 1 scale in the Figures 3 and 4 is shown.
- the force absorption plate 15 is in the form of a round disk has four rectangular cutouts 16 on its circumference are evenly distributed. How best to figure 4 sees, the force plate 15 by one cup-shaped body 17 with a guide ring 19 connected.
- the openings 16 each extend from the Force absorption plate 15 in the cup-shaped body 17. Die
- the size of the openings 16 is chosen so that the back and forth Moving the tappet 9 a pressure equalization takes place between the space in which the ring 8 is arranged and the space in which the spring 14 is arranged. The Ensure openings 16. that the pressure difference between the previously mentioned rooms in all operating states is.
- the tappet according to the invention absorbs the forces Circumferential direction of the ring 8.
- the tappet 9 is as shown in Figures 1 and 2, by the Guide ring 19 in a bore 24 in the housing 2 guided.
- the bore extends in the same Direction like the associated cylinder space 18.
- the main difference between the embodiment of Figures 5 and 6 compared to the embodiment of Figures 1 and 2 is that the ring 8 in the radial piston pump shown in Figures 5 and 6 does not have the shape of a polygon, but is cylindrical.
- the cup tappet 9 is the same in both embodiments and corresponds to the cup tappet 9, which is shown enlarged in FIGS. 3 and 4.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Fuel-Injection Apparatus (AREA)
- Reciprocating Pumps (AREA)
Description
Die Erfindung betrifft eine Radialkolbenpumpe zur Kraftstoffhochdruckversorgung bei Kraftstoffeinspritzsystemen von Brennkraftmaschinen, insbesondere bei einem Common-Rail-Einspritzsystem, mit einer in einem Pumpengehäuse gelagerten Antriebswelle, die exzentrisch ausgebildet ist oder in Umfangsrichtung nockenartige Erhebungen aufweist, und mit vorzugsweise mehreren bezüglich der Antriebswelle radial in einem jeweiligen Zylinderraum angeordneten Kolben, die durch Drehen der Antriebswelle in dem jeweiligen Zylinderraum in radialer Richtung hin und her bewegbar sind.The invention relates to a radial piston pump for High pressure fuel supply at Fuel injection systems of internal combustion engines, especially with a common rail injection system a drive shaft mounted in a pump housing, the is eccentric or in the circumferential direction has cam-like elevations, and preferably with several radially in one with respect to the drive shaft respective cylinder space arranged pistons, which by Turn the drive shaft in the respective cylinder space in radial direction are movable back and forth.
Es wird jedoch darauf hingewiesen, daß die vorliegende Erfindung nicht nur bei einer Radialkolbenpumpe eingesetzt werden kann, sondern auch bei Hochdruckpumpen insbesondere mit einer Bedarfsmengenregelung.However, it should be noted that the present Invention not only used in a radial piston pump can be, but also with high pressure pumps in particular with a demand quantity regulation.
Bei einer innen abgestützten Radialkolbenpumpe der genannten Art hat jeweils der Fuß der Kolben Kontakt mit der Antriebswelle. Die Kolben werden durch die Exzentrizität der Antriebswelle oder durch die nockenartigen Erhebungen auf der Antriebswelle nacheinander in eine Hin- und Herbewegung versetzt. Dabei werden von der sich drehenden Antriebswelle auf die Kolben jedoch nicht nur Kräfte in bezüglich der Antriebswelle radialer Richtung aufgebracht, d.h. in Längsrichtung der Kolben, sondern auch quer zu den Kolben. Diese Querkräfte erzeugen ein Moment auf den jeweiligen Kolben.With an internally supported radial piston pump the mentioned type the foot of the piston has contact with the drive shaft. The pistons are replaced by the Eccentricity of the drive shaft or by the cam-like elevations on the drive shaft one after the other in a reciprocating motion. In doing so, the rotating drive shaft on the pistons, however only forces in radial direction with respect to the drive shaft upset, i.e. in the longitudinal direction of the pistons, but also across the pistons. These shear forces create a moment on the respective piston.
Aus der EP 0 304 743 A1 und der DE 42 16 877 A1 sind Radialkolbenpumpen bekannt bei denen zwischen Kolben und Antriebswelle ein Tassenstößel vorgesehen ist. Dieser Tassenstößel soll die andernfalls von der Antriebswelle auf den Kolben eingeleiteten Querkräfte aufnehmen. Nachteilig an der in der EP 0 304 743 ist, dass die Tassenstößel eine signifikante Verschlechterung des Pumpenwirkungsgrads mit sich bringen, da der notwendig Druckausgleich zwischen Kurbelgehäuse und Tasseninnerem unbefriedigend gelöst ist. Bei der DE 42 16 877 A1 sind die Tassenstößel an der Zylinderbuchse geführt, so dass sich zwar das Problem des Druckausgleichs nicht stellt, allerdings ist die Führung des Tassenstößels gegenüber der EP 0 304 743 A1 verschlechtert.From EP 0 304 743 A1 and DE 42 16 877 A1 Radial piston pumps are known in those between pistons and Drive shaft a bucket tappet is provided. This Otherwise the bucket tappet should open from the drive shaft absorb the transverse forces introduced into the piston. adversely What is known in EP 0 304 743 is that the tappets have a significant deterioration in pump efficiency with bring themselves because of the necessary pressure equalization between Crankcase and cup interior is unsatisfactorily solved. In DE 42 16 877 A1, the tappets are on the Guided cylinder liner, so that the problem of Pressure equalization does not provide, however, is the lead of the tappet compared to EP 0 304 743 A1 deteriorated.
Der Erfindung liegt daher das Problem zugrunde, eine Radialkolbenpumpe bereitzustellen, welche diese Nachteile vermeidet und einen weiter verbesserten Wirkungsgrad sowie eine weiter erhöhte Belastbarkeit bei gleichzeitig geringen Herstellungskosten aufweist. Insbesondere sollen Beschädigungen des Kolbenfuß, wie Käfigbrüche, verhindert werden, so daß ein einwandfreier Betrieb der Radialkolbenpumpe auch bei Teilbefüllung gewährleistet ist. Die erfindungsgemäße Radialkolbenpumpe soll einen Pumpendruck von bis zu 2000 bar aushalten.The invention is therefore based on the problem of a Radial piston pump to provide these disadvantages avoids and a further improved efficiency as well a further increased resilience with low Has manufacturing costs. In particular, should Damage to the piston foot, such as cage breaks, is prevented be, so that the proper operation of the Radial piston pump is guaranteed even with partial filling. The radial piston pump according to the invention should Withstand pump pressures of up to 2000 bar.
Das Problem wird durch die in dem unabhängigen Patentanspruch offenbarte Radialkolbenpumpe gelöst. The problem is solved by those in the independent Disclosed claim radial piston pump solved.
Die erfindungsgemäßen Öffnungen dienen zum Druckausgleich und gewährleisten, daß sich auch bei Ausnutzung des vollen Hubes nur eine minimale Druckdifferenz zwischen dem die Antriebswelle umgebenden Raum und dem jeweiligen Zylinderraum ergibt. Dadurch bleibt die Zunahme der Hertz'schen Pressung im Nutzhub gering und im Saughub ist eine Vollbefüllung des Elements gewährleistet. Somit ist auch bei Spitzendrücken bis zu 2000 bar eine hohe Lebensdauer der Kolben gewährleistet.The openings according to the invention serve to equalize the pressure and ensure that even when the full Hubes only a minimal pressure difference between which the Drive shaft surrounding space and the respective Cylinder space results. This keeps the increase in Hertzian pressure in the useful stroke is low and in the suction stroke a full filling of the element is guaranteed. So is a high one even at peak pressures up to 2000 bar Guaranteed piston life.
Weitere vorteilhafte Ausführungsarten der Erfindung sind in den Unteransprüchen offenbart.Further advantageous embodiments of the invention are in disclosed in the subclaims.
Eine besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, daß der Tassenstößel jeweils in der gleichen Richtung wie der zugehörige Kolben hin und her bewegbar ist. Dadurch ist gewährleistet, daß von der Antriebswelle Kräfte in radialer Richtung, d.h. in Längsrichtung der Kolben, über den Tassenstößel auf die Kolben abgegeben werden können. Damit ist die für den Betrieb der Pumpe erforderliche Hin- und Herbewegung der Kolben der Radialkolbenpumpe gewährleistet.This is a special embodiment of the invention characterized in that the tappet each in the same direction as the associated piston back and forth is movable. This ensures that the Drive shaft forces in the radial direction, i.e. in Longitudinal direction of the piston, over the tappet on the Pistons can be delivered. So that's for the Operation of the pump required reciprocation of the Radial piston pump piston guaranteed.
Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, daß der Tassenstößel jeweils in einer Bohrung in dem Gehäuse geführt ist, die sich in der gleichen Richtung wie der zugehörige Zylinderraum erstreckt. Die Führung ermöglicht auch bei hohen Pumpendrücken und schnellen Lastwechseln eine Hin- und Herbewegung der Querkraftaufnahmeeinrichtung. Insbesondere wird ein Verkanten des Tassenstößels in dem Zylinderraum vermieden. Another special embodiment of the invention is characterized in that the tappet each in a hole in the housing is guided, which is in the same direction as the associated cylinder space extends. The guidance enables even at high Pump pressures and rapid load changes make a round trip Movement of the lateral force absorption device. In particular becomes a tilting of the tappet in the cylinder space avoided.
Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, daß der Boden des Tassenstößels von einer Kraftaufnahmeplatte gebildet wird. Die Kraftaufnahmeplatte befindet sich in Kontakt mit der Antriebswelle und kann je nach Belastung eine unterschiedliche Dicke aufweisen. Die Oberfläche der Kraftaufnahmeplatte kann besonders behandelt sein, um eine hohe Verschleißfestigkeit zu gewährleisten.Another special embodiment of the invention is characterized in that the bottom of the tappet from a force plate is formed. The Force plate is in contact with the Drive shaft and can, depending on the load have different thickness. The surface of the Force plate can be specially treated to a to ensure high wear resistance.
Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, daß die Kraftaufnahmeplatte durch den tassenförmigen Körper mit einem Führungsring verbunden ist. Der Führungsring gleitet in dem Zylinderraum. Die mit dem Zylinderraum in Kontakt befindliche Fläche kann speziell behandelt sein, um die Reibungskräfte zu minimieren. Der Führungsring sorgt dafür, daß die Querkraftaufnahmeeinrichtung sich nicht in dem Zylinderraum verkantet. Die Abmessungen des Führungsrings hängen vom Pumpendruck und von der Anzahl der Lastwechsel pro Zeiteinheit ab.Another special embodiment of the invention is characterized in that the force absorption plate by the cup-shaped body connected with a guide ring is. The guide ring slides in the cylinder space. With area in contact with the cylinder space be specially treated to reduce the frictional forces minimize. The guide ring ensures that the Transverse force absorption device is not in the cylinder space canted. The dimensions of the guide ring depend on Pump pressure and the number of load changes per Time unit.
Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, daß die Kolben jeweils durch eine Feder gegen die zugehörige Kraftaufnahmeplatte des Tassenstößels gedrückt werden. Durch die Federkraft wird der Kolben zur Antriebswelle hin bewegt, so daß Kraftstoff angesaugt wird. Es ist auch möglich, daß die Kraftaufnahmeplatte des Tassenstößels durch eine Feder gegen die Antriebswelle gedrückt wird. Allerdings wäre es in diesem Fall erforderlich, daß die Kraftaufnahmeplatte mit dem Kolben verbunden ist, um das Ansaugen von Kraftstoff zu gewährleisten. Wenn der Kolben direkt mit der Federkraft beaufschlagt wird, kann diese Verbindung zwischen Kraftaufnahmeplatte und Kolben entfallen. Diese Variante hat den Vorteil, daß eine so ausgeführte Radialkolbenpumpe einfach und kostengünstig hergestellt werden kann. Zudem ist bei dieser Variante die Anwendung der vorliegenden Erfindung auf bekannte Radialkolbenpumpen ohne weiteres möglich.Another special embodiment of the invention is characterized in that the pistons each by a Spring against the associated force plate of the Cup tappet are pressed. Through the spring force the piston moves toward the drive shaft so that fuel is sucked in. It is also possible that the Force plate of the tappet by a spring is pressed against the drive shaft. However, it would be in this case, that the force plate is connected to the piston to suck in To ensure fuel. If the piston is directly with the This force can be applied to the spring force between force plate and piston are eliminated. This Variant has the advantage that a so executed Radial piston pump manufactured easily and inexpensively can be. In addition, the application is in this variant of the present invention on known radial piston pumps easily possible.
Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, daß die Kraftaufnahmeplatte auf der zur Antriebswelle gerichteten Seite leicht ballig ausgebildet ist. Die konvexe Ausbildung der Kraftaufnahmeplatte dient dazu, die Kontaktfläche zwischen Antriebswelle und Kraftaufnahmeplatte zu verkleinern. Dadurch wird das von der Antriebswelle auf den Tassenstößel aufgebrachte Moment vorteilhaft reduziert. Bei der Auslegung der Kraftaufnahmeplatte muß die elastische Verformung des Tassenstößels berücksichtigt werden.Another special embodiment of the invention is characterized in that the force receiving plate on the slightly convex towards the drive shaft is trained. The convex formation of the Force absorption plate serves to establish the contact area between Reduce drive shaft and force plate. This will move the drive shaft onto the tappet applied moment advantageously reduced. In the The design of the force plate must be elastic Deformation of the cup tappet must be taken into account.
Eine weitere besondere Ausführungsart der Erfindung ist dadurch gekennzeichnet, daß zwischen der Antriebswelle und den Tassenstößeln ein Ring angeordnet ist. Der Ring dient zur Übertragung der Kräfte von der Antriebswelle auf die Kraftaufnahmeplatte. Vorteilhaft ist der Ring gleitend auf der Antriebswelle gelagert. Dabei kann der Ring entweder zylindrisch oder polygonförmig ausgebildet sein.Another special embodiment of the invention is characterized in that between the drive shaft and a ring is arranged on the tappets. The ring serves to transfer the forces from the drive shaft to the Force absorbing plate. The ring is advantageously sliding on the drive shaft. The ring can either be cylindrical or polygonal.
Die vorliegende Erfindung hat allgemein den Vorteil, daß sie einfach und kostengünstig realisiert werden kann. Zudem kann der Grundgedanke der vorliegenden Erfindung in einfacher Art und Weise auf bestehende Radialkolbenpumpen angewendet werden, indem z.B. eine am Kolben vorgesehene Stößelplatte durch einen Tassenstößel ersetzt wird. Darüber hinaus wird die Bauteilfestigkeit, insbesondere bei einer Nullförderung im Saughub, erhöht.The present invention generally has the advantage that it can be implemented simply and inexpensively. moreover the basic idea of the present invention can be found in simple way on existing radial piston pumps applied by e.g. one provided on the piston Ram plate is replaced by a bucket tappet. About that In addition, the component strength, especially with a Zero funding in suction stroke, increased.
Weitere Vorteile, Merkmale und Einzelheiten der Erfindung ergeben sich aus den Unteransprüchen sowie der nachfolgenden Beschreibung, in der unter Bezugnahme auf die Zeichnungen ein Ausführungsbeispiel im Einzelnen beschrieben ist. Dabei können die in den Ansprüchen und in der Beschreibung erwähnten Merkmale jeweils einzeln für sich oder in beliebiger Kombination erfindungswesentlich sein. Ein Weg zum Ausführen der beanspruchten Erfindung ist nachfolgend anhand der Zeichnungen im Einzelnen erläutert.
- Figur 1
- zeigt eine Schnittdarstellung einer erfindungsgemäßen Radialkolbenpumpe;
Figur 2- zeigt einen Schnitt entlang der Linie A-B durch die Radialkolbenpumpe aus Figur 1;
- Figur 3
- zeigt eine Untersicht eines erfindungsgemäßen Tassenstößels;
- Figur 4
- zeigt die Darstellung eines Schnitts durch den Tassenstößel aus Figur 3 entlang der Linie B-C;
- Figur 5
- zeigt einen Schnittdarstellung einer weiteren Ausführungsform der erfindungsgemäßen Radialkolbenpumpe;
Figur 6- zeigt einen Schnitt entlang der Linie A-B durch die Radialkolbenpumpe aus Figur 5.
- Figure 1
- shows a sectional view of a radial piston pump according to the invention;
- Figure 2
- shows a section along the line AB through the radial piston pump of Figure 1;
- Figure 3
- shows a bottom view of a tappet according to the invention;
- Figure 4
- shows the representation of a section through the tappet from Figure 3 along the line BC;
- Figure 5
- shows a sectional view of a further embodiment of the radial piston pump according to the invention;
- Figure 6
- shows a section along the line AB through the radial piston pump of Figure 5.
Die Figuren 1 und 2 zeigen eine Radialkolbenpumpe zur Kraftstoffhochdruckversorgung bei Kraftstoffeinspritzsystemen von Brennkraftmaschinen. Die Radialkolbenpumpe ist mit einer integrierten Bedarfsmengenregelung ausgestattet. Die Kraftstoffzufuhr und Dimensionierung erfolgt über eine nicht dargestellte Zumesseinheit.Figures 1 and 2 show a radial piston pump High pressure fuel supply at Fuel injection systems for internal combustion engines. The Radial piston pump is with an integrated Required quantity control. The fuel supply and dimensioning takes place via a not shown Metering unit.
Die erfindungsgemäße Radialkolbenpumpe wird insbesondere in Common-Rail-Einspritzsystemen zur Kraftstoffversorgung von Dieselmotoren eingesetzt. Dabei bedeutet "common rail" soviel wie "gemeinsame Leitung" oder "gemeinsame Schiene". Im Gegensatz zu herkömmlichen Hochdruckeinspritzsystemen, in denen der Kraftstoff über getrennte Leitungen zu den einzelnen Brennräumen gefördert wird, werden die Einspritzdüsen in Common-Rail-Einspritzsystemen aus einer gemeinsamen Leitung gespeist.The radial piston pump according to the invention is particularly in Common rail fuel injection systems for Diesel engines used. "Common rail" means as much as "common management" or "common rail". In contrast to conventional high pressure injection systems, in which the fuel via separate lines to the individual combustion chambers is promoted Injectors in common rail injection systems from one fed common line.
Die in den Figuren 1 und 2 gezeigte Radialkolbenpumpe
umfaßt eine in einem Pumpengehäuse 2 gelagerte
Antriebswelle 4 mit einem exzentrisch ausgebildeten
Wellenabschnitt 6. Auf dem exzentrischen Wellenabschnitt 6
ist ein Ring 8 vorgesehen, gegenüber dem der
Wellenabschnitt 6 drehbar ist. Der Ring 8 umfaßt drei
jeweils um 120° zueinander versetzte Abflachungen 10 gegen
die sich jeweils ein Kolben 12 abstützt. Die Kolben 12 sind
jeweils in einem Zylinderraum 18 zur Antriebswelle 4 in
radialer Richtung hin- und herbewegbar aufgenommen.The radial piston pump shown in Figures 1 and 2
comprises a stored in a
An dem zur Antriebswelle 4 hin gerichteten Ende der Kolben
12 ist jeweils ein Federteller 13 befestigt, gegen den eine
Feder 14 vorgespannt ist. Die Feder 14 drückt den Kolben 12
gegen eine Kraftaufnahmeplatte 15, die zu einem
Tassenstößel 9 gehört, der vergrößert im Maßstab 2:1 in den
Figuren 3 und 4 gezeigt ist.At the end of the piston directed towards the drive shaft 4
12, a
In der in Figur 3 gezeigten Untersicht ist zu erkennen, daß
die Kraftaufnahmeplatte 15 die Form einer runden Scheibe
hat, auf deren Umfang vier rechteckige Aussparungen 16
gleichmäßig verteilt sind. Wie man am besten in Figur 4
sieht, ist die Kraftaufnahmeplatte 15 durch einen
tassenförmigen Körper 17 mit einem Führungsring 19
verbunden. Die Öffnungen 16 erstrecken sich jeweils von der
Kraftaufnahmeplatte 15 in den tassenförmigen Körper 17. Die
Größe der Öffnungen 16 ist so gewählt, daß beim Hin- und
Herbewegen des Tassenstößels 9 ein Druckausgleich
stattfindet zwischen dem Raum, in dem der Ring 8 angeordnet
ist, und dem Raum, in dem die Feder 14 angeordnet ist. Die
Öffnungen 16 gewährleisten. daß die Druckdifferenz zwischen
den vorab erwähnten Räumen in allen Betriebszuständenminimal
ist. Dadurch bleibt die Zunahme der Hertz'schen
Pressung im Nutzhub der Kolben 12 gering, und im Saughub
ist bei entsprechend ausgelegter Feder 14 eine vollständige
Befüllung des jeweiligen Zylinderraums 18 gewährleistet.
Ohne die Öffnungen 16 wäre ein Hin- und Herbewegen des
Tassenstößels erschwert oder gar unmöglich. In the bottom view shown in Figure 3 it can be seen that
the
In Figur 1 ist gezeigt, daß sich die Kraftaufnahmeplatten
15 in Anlage mit den Abflachungen 10 des Rings 8 befinden.
Der Ring 8 ist gleitend auf der Antriebswelle 4 gelagert
und wird bei einer Drehung der Antriebswelle 4 durch den
exzentrisch ausgebildeten Wellenabschnitt 6 in Bewegung
versetzt. Diese Bewegung hat jedoch nicht nur eine
bezüglich der Antriebswelle 4 radiale Komponente, die für
den Kolbenhub benötigt wird, sondern auch eine Komponente
in Umfangsrichtung der Antriebswelle 4, d.h. quer zu den
Kolben 12. Diese Komponente, die den vorab erwähnten
Querkräften entspricht, ist unerwünscht, weil sie ein
Moment auf die Kolben bewirkt.In Figure 1 it is shown that the
Der erfindungsgemäße Tassenstößel nimmt die Kräfte in
Umfangsrichtung des Rings 8 auf. Der Tassenstößel 9 ist,
wie in den Figuren 1 und 2 gezeigt ist, durch den
Führungsring 19 in einer Bohrung 24 in dem Gehäuse 2
geführt. Die Bohrung erstreckt sich jeweils in der gleichen
Richtung wie der zugehörige Zylinderraum 18. Durch diese
Abstützung des Tassenstößels 9 in dem Gehäuse 2 werden die
Querkräfte von dem Ring 8 über die Kraftaufnahmeplatte 15,
den tassenförmigen Körper 17 und den Führungsring 19 in das
Gehäuse 2 geleitet. Das hat zur Folge, daß auf die Kolben
12 lediglich Kräfte in deren jeweiliger Längsrichtung
aufgebracht werden. Dadurch wird die Belastung und der
Verschleiß der Kolben 12 erheblich reduziert.The tappet according to the invention absorbs the forces
Circumferential direction of the
Die in den Figuren 5 und 6 gezeigte Radialkolbenpumpe entspricht weitestgehend der in den Figuren 1 und 2 dargestellten Ausführungsform. Deshalb wurden für Teile, die sowohl in der Radialkolbenpumpe der Figuren 1 und 2 als auch der Figuren 5 und 6 enthalten sind, die gleichen Bezugszeichen verwendet. Um Wiederholungen zu vermeiden wird auf eine nochmalige Beschreibung derartiger Teile bei der Erläuterung der Figuren 5 und 6 verzichtet. The radial piston pump shown in Figures 5 and 6 largely corresponds to that in FIGS. 1 and 2 illustrated embodiment. Therefore, for parts, which both in the radial piston pump of Figures 1 and 2 Figures 5 and 6 are also included, the same Reference numerals used. To avoid repetitions is a further description of such parts the explanation of Figures 5 and 6 omitted.
Der Hauptunterschied zwischen der Ausführungsform der
Figuren 5 und 6 gegenüber der Ausführungsform der Figuren 1
und 2 besteht darin, daß der Ring 8 bei der in den Figuren
5 und 6 gezeigten Radialkolbenpumpe nicht die Form eines
Polygons aufweist, sondern zylindrisch ausgebildet ist.
Der Tassenstößel 9 ist in beiden Ausführungsformen der
gleiche und entspricht dem Tassenstößel 9, der vergrößert
in den Figuren 3 und 4 dargestellt ist.The main difference between the embodiment of Figures 5 and 6 compared to the embodiment of Figures 1 and 2 is that the
The
Claims (8)
- Radial piston pump for fuel high-pressure supply in fuel injection systems of internal combustion engines, in particular in a common-rail injection system, with a drive shaft (4) which is mounted in a pump casing (2) and which is designed eccentrically or has cam-like elevations in the circumferential direction, and with preferably a plurality of pistons (12) which are arranged radially in a respective cylinder space (18) with respect to the drive shaft (4) and which are moveable back and forth in the radial direction in the respective cylinder space (18) as a result of the rotation of the drive shaft (4), in each case a bucket tappet with a bucket-shaped body (17) being arranged between the pistons (12) and the drive shaft (4), characterized in that a plurality of orifices (16) are provided in the bucket-shaped body (17).
- Radial piston pump according to Claim 1, characterized in that the bucket tappet (9) is moveable back and forth in each case in the same direction as the associated piston (12).
- Radial piston pump according to Claim 2, characterized in that the bucket tappet (9) is guided in each case in a bore (24) in the casing (2), the said bore extending in the same direction as the associated cylinder space (18).
- Radial piston pump according to one of the preceding claims, characterized in that the bottom of the bucket tappet (9) is formed by a force absorption plate (15).
- Radial piston pump according to Claim 4, characterized in that the force absorption plate (15) is connected to a guide ring (19) by means of the bucket-shaped body (17).
- Radial piston pump according to one of Claims 4 or 5, characterized in that the pistons (12) are pressed in each case by a spring (14) against the associated force absorption plate (15) of the bucket tappet (9).
- Radial piston pump according to one of Claims 4 to 6, characterized in that the force absorption plate (15) has a slightly convex design on the side directed towards the drive shaft (4).
- Radial piston pump according to one of the preceding claims, characterized in that a ring (8) is arranged between the drive shaft (4) and the bucket tappets (9).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE19753593A DE19753593A1 (en) | 1997-12-03 | 1997-12-03 | Radial piston pump for high-pressure fuel supply |
| DE19753593 | 1997-12-03 | ||
| PCT/DE1998/003321 WO1999028625A1 (en) | 1997-12-03 | 1998-11-12 | Radial piston pump for feeding high pressure fuel |
Publications (3)
| Publication Number | Publication Date |
|---|---|
| EP0970309A1 EP0970309A1 (en) | 2000-01-12 |
| EP0970309B1 true EP0970309B1 (en) | 2003-09-03 |
| EP0970309B2 EP0970309B2 (en) | 2009-04-22 |
Family
ID=7850594
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP98963344A Expired - Lifetime EP0970309B2 (en) | 1997-12-03 | 1998-11-12 | Radial piston pump for feeding high pressure fuel |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US6250893B1 (en) |
| EP (1) | EP0970309B2 (en) |
| JP (1) | JP4308921B2 (en) |
| DE (2) | DE19753593A1 (en) |
| WO (1) | WO1999028625A1 (en) |
Families Citing this family (18)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19844326B4 (en) * | 1998-09-28 | 2006-01-05 | Robert Bosch Gmbh | Radial piston pump |
| DE19956092A1 (en) * | 1999-11-22 | 2000-10-26 | Siemens Ag | Piston pump, especially high-pressure radial piston pump |
| DE10147981A1 (en) * | 2001-09-28 | 2003-04-24 | Siemens Ag | Connecting element for connecting a piston to a restoring element |
| DE10200792A1 (en) * | 2002-01-11 | 2003-07-31 | Bosch Gmbh Robert | Fuel pump for an internal combustion engine |
| KR100539209B1 (en) * | 2002-08-29 | 2005-12-27 | 주식회사 두원정공 | High pressure supply pump |
| JP2006514195A (en) * | 2003-02-11 | 2006-04-27 | ガンサー−ハイドロマグ アーゲー | High pressure pump |
| GB0311814D0 (en) * | 2003-05-22 | 2003-06-25 | Delphi Tech Inc | Pump assembly |
| DE10347715A1 (en) * | 2003-10-14 | 2005-05-12 | Zahnradfabrik Friedrichshafen | Radial piston pump |
| DE102004023541A1 (en) * | 2004-05-13 | 2005-12-01 | Robert Bosch Gmbh | High-pressure pump for a fuel injection device of an internal combustion engine |
| SE531362C2 (en) * | 2005-06-20 | 2009-03-10 | Oehlins Racing Ab | Pump device for, for example, front and rear wheel drive motorcycle |
| WO2007071661A1 (en) * | 2005-12-20 | 2007-06-28 | Industriehansa Consulting & Engineering Gmbh | High pressure pump with several pistons per cylinder |
| DE102007019261A1 (en) | 2007-04-17 | 2008-10-23 | Golle Motor Ag | Radial piston pump, esp. For Common Rail (CR) injection systems |
| EP2048359B1 (en) | 2007-10-12 | 2015-06-24 | Delphi International Operations Luxembourg S.à r.l. | Improvements relating to fuel pumps |
| DE102008000954A1 (en) | 2008-04-03 | 2009-10-08 | Robert Bosch Gmbh | High pressure fuel pump for operating internal combustion engine, has pump housing and pump piston that is operated over eccentric coil of pump cam shaft |
| DE102008001869A1 (en) | 2008-05-20 | 2009-11-26 | Robert Bosch Gmbh | Radial piston pump for high-pressure fuel supply in common-rail injection system of diesel engine in passenger car, has piston or support body and support ring, which are movably fixed together at region of supporting surface |
| JP5575226B1 (en) * | 2011-08-30 | 2014-08-20 | 三菱重工業株式会社 | Cover of hydraulic pump in renewable energy generator |
| GB201503556D0 (en) * | 2015-03-03 | 2015-04-15 | Delphi International Operations Luxembourg S.�.R.L. | High temperature fuel deflector for a fuel pump drive assembly |
| CN108915919B (en) * | 2018-08-28 | 2023-10-20 | 河南柴油机重工有限责任公司 | Common rail pump driving device of high-pressure common rail diesel engine |
Family Cites Families (19)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3066610A (en) * | 1961-01-26 | 1962-12-04 | Greenlee Bros & Co | Pump |
| DE2529473C3 (en) † | 1975-07-02 | 1980-11-20 | Danfoss A/S, Nordborg (Daenemark) | Slide shoe arrangement, especially for axial and radial piston machines |
| WO1983000724A1 (en) * | 1979-10-19 | 1983-03-03 | Clouse, Jerry, A. | Lifter assembly |
| DE2951012A1 (en) * | 1979-12-19 | 1981-07-23 | Zahnradfabrik Friedrichshafen Ag, 7990 Friedrichshafen | PUMP ARRANGEMENT |
| WO1986000667A1 (en) * | 1984-07-03 | 1986-01-30 | Baralaba Pty Ltd | Liquid pump |
| DE3721698A1 (en) * | 1987-07-01 | 1989-01-19 | Hauhinco Maschf | RADIAL PISTON PUMP FOR CONVEYING WATER |
| IT212433Z2 (en) * | 1987-08-25 | 1989-07-04 | Weber Srl | RADIAL PISTON PUMP |
| DE3804025A1 (en) | 1988-02-10 | 1989-08-24 | Bosch Gmbh Robert | FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES |
| DE4216877C2 (en) * | 1991-08-12 | 1996-08-29 | Elasis Sistema Ricerca Fiat | Radial piston pump |
| GB2260374A (en) * | 1991-10-12 | 1993-04-14 | Lucas Ind Plc | Fuel pump |
| US5630708A (en) * | 1993-12-28 | 1997-05-20 | Zexel Corporation | Radial piston pump for low-viscosity fuel |
| DE4401074B4 (en) * | 1994-01-15 | 2007-01-18 | Robert Bosch Gmbh | Pump arrangement, in particular for conveying fuel from a reservoir to an internal combustion engine |
| DE19507295B4 (en) † | 1995-03-02 | 2004-09-02 | Siemens Ag | Radial piston pump, in particular fuel pump for an internal combustion engine |
| DE19517628A1 (en) * | 1995-05-13 | 1996-11-14 | Luk Automobiltech Gmbh & Co Kg | Radial piston pump |
| DE19523283B4 (en) * | 1995-06-27 | 2006-01-19 | Robert Bosch Gmbh | Pump, in particular high-pressure pump for a fuel injection device of an internal combustion engine |
| DE19549108A1 (en) * | 1995-12-29 | 1997-07-03 | Bosch Gmbh Robert | High-pressure fuel generation system for a fuel injection system used in internal combustion engines |
| GB9610785D0 (en) * | 1996-05-23 | 1996-07-31 | Lucas Ind Plc | Radial piston pump |
| JPH1030525A (en) * | 1996-07-16 | 1998-02-03 | Denso Corp | High pressure supply pump |
| IT239879Y1 (en) * | 1996-12-23 | 2001-03-13 | Elasis Sistema Ricerca Fiat | REFINEMENTS TO A PISTON PUMP, IN PARTICULAR TO A RADIAL APISTON PUMP FOR THE FUEL OF AN INTERNAL COMBUSTION ENGINE. |
-
1997
- 1997-12-03 DE DE19753593A patent/DE19753593A1/en not_active Ceased
-
1998
- 1998-11-12 WO PCT/DE1998/003321 patent/WO1999028625A1/en active IP Right Grant
- 1998-11-12 JP JP52962599A patent/JP4308921B2/en not_active Expired - Fee Related
- 1998-11-12 US US09/355,756 patent/US6250893B1/en not_active Expired - Lifetime
- 1998-11-12 EP EP98963344A patent/EP0970309B2/en not_active Expired - Lifetime
- 1998-11-12 DE DE59809494T patent/DE59809494D1/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| EP0970309A1 (en) | 2000-01-12 |
| DE19753593A1 (en) | 1999-06-17 |
| JP2001510531A (en) | 2001-07-31 |
| US6250893B1 (en) | 2001-06-26 |
| DE59809494D1 (en) | 2003-10-09 |
| JP4308921B2 (en) | 2009-08-05 |
| EP0970309B2 (en) | 2009-04-22 |
| WO1999028625A1 (en) | 1999-06-10 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| EP0970309B1 (en) | Radial piston pump for feeding high pressure fuel | |
| DE4138313C2 (en) | Radial piston pump | |
| DE10212492B4 (en) | piston pump | |
| DE19816044C2 (en) | Radial piston pump for high-pressure fuel generation | |
| WO1999036697A1 (en) | Radial piston pump for high pressure fuel supply | |
| DE102009028394A1 (en) | high pressure pump | |
| DE19844326B4 (en) | Radial piston pump | |
| EP1319831A2 (en) | High pressure fuel pump having integrated vane feed pump | |
| DE102006044294B3 (en) | Radial piston pump for internal combustion engine, has pump units with cross heads having cross head bolts that are supported in small lugs of piston rod, where lugs are designed as slotted holes with longitudinal axes | |
| DE102006038839A1 (en) | High-pressure pump for fuel system of internal-combustion engine, has roller held between housing-side stationary sliding surfaces, where both opposite front surfaces of roller work together with stationary housing-side sliding surface | |
| DE102014224724A1 (en) | high pressure pump | |
| DE10313745A1 (en) | High pressure pump for IC engine fuel injection device e.g. for automobile, with hydrodynamic lubrication of bearings for ring segments operating pistons of pump elements | |
| EP0881380A1 (en) | High-pressure feed pump | |
| EP1798415B1 (en) | High pressure pump | |
| EP1906011B1 (en) | Fluid pump, in particular high pressure fuel pump for injection systems in combustion engines | |
| DE10226492B4 (en) | Axial piston machine with adjustable piston stroke | |
| DE102008017823B4 (en) | High-pressure pump with a pump piston, a plunger and a roller shoe consisting of at least two plate-shaped roller shoe segments | |
| DE102017214728A1 (en) | Camshaft for a pump, in particular a high-pressure fuel pump, and pump with camshaft | |
| DE102009003256A1 (en) | Piston pump, particularly high-pressure fuel pump, has drive shaft with drive section, piston cooperating with drive section and counter element | |
| DE2220164B2 (en) | In-line fuel pump for IC engine - has followers guided by flattened sides to reduce space requirement and prevent rotation | |
| DE102017111395A1 (en) | Device for changing the compression ratio of a reciprocating internal combustion engine | |
| DE102019120480A1 (en) | Connecting rod for an internal combustion engine with variable compression | |
| DE19847044A1 (en) | Radial piston pump for fuel injection has piston ring groove linked to channels in tee-groove format or channels formed by piston flats for oil leakage collection to keep piston in line. | |
| DE102007032218A1 (en) | Radial piston pump for high fuel-pressure production in e.g. common rail injection system of internal combustion engine, has cam follower, where radial clearance between cam follower and guide boring is position- and orientation-dependent | |
| DE102006048605B3 (en) | Radial piston pump for fuel supply in fuel injection system of internal combustion engine, has driving shaft which is mounted in pump housing with eccentric cam and piston arranged with respect to driving shaft in cylinder chamber |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
| AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): DE FR GB IT |
|
| 17P | Request for examination filed |
Effective date: 19991210 |
|
| 17Q | First examination report despatched |
Effective date: 20020724 |
|
| GRAH | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOS IGRA |
|
| GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
| GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
| AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): DE FR GB IT |
|
| REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D Free format text: NOT ENGLISH |
|
| REF | Corresponds to: |
Ref document number: 59809494 Country of ref document: DE Date of ref document: 20031009 Kind code of ref document: P |
|
| GBT | Gb: translation of ep patent filed (gb section 77(6)(a)/1977) |
Effective date: 20031223 |
|
| ET | Fr: translation filed | ||
| PLBI | Opposition filed |
Free format text: ORIGINAL CODE: 0009260 |
|
| PLAX | Notice of opposition and request to file observation + time limit sent |
Free format text: ORIGINAL CODE: EPIDOSNOBS2 |
|
| 26 | Opposition filed |
Opponent name: SIEMENS AGCT IP SV Effective date: 20040527 |
|
| PLBB | Reply of patent proprietor to notice(s) of opposition received |
Free format text: ORIGINAL CODE: EPIDOSNOBS3 |
|
| PLAB | Opposition data, opponent's data or that of the opponent's representative modified |
Free format text: ORIGINAL CODE: 0009299OPPO |
|
| R26 | Opposition filed (corrected) |
Opponent name: SIEMENS VDO AUTOMOTIVE AKTIENGESELLSCHAFT Effective date: 20040527 |
|
| PLAB | Opposition data, opponent's data or that of the opponent's representative modified |
Free format text: ORIGINAL CODE: 0009299OPPO |
|
| R26 | Opposition filed (corrected) |
Opponent name: CONTINENTAL AUTOMOTIVE GMBH Effective date: 20040527 |
|
| PUAH | Patent maintained in amended form |
Free format text: ORIGINAL CODE: 0009272 |
|
| STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: PATENT MAINTAINED AS AMENDED |
|
| 27A | Patent maintained in amended form |
Effective date: 20090422 |
|
| AK | Designated contracting states |
Kind code of ref document: B2 Designated state(s): DE FR GB IT |
|
| PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: IT Payment date: 20121124 Year of fee payment: 15 Ref country code: GB Payment date: 20121122 Year of fee payment: 15 |
|
| PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20121217 Year of fee payment: 15 |
|
| GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20131112 |
|
| REG | Reference to a national code |
Ref country code: FR Ref legal event code: ST Effective date: 20140731 |
|
| PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20131112 |
|
| PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20131112 Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20131202 |
|
| PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20180125 Year of fee payment: 20 |
|
| REG | Reference to a national code |
Ref country code: DE Ref legal event code: R071 Ref document number: 59809494 Country of ref document: DE |