EP1756426B1 - Pumps - Google Patents

Pumps Download PDF

Info

Publication number
EP1756426B1
EP1756426B1 EP05746325.9A EP05746325A EP1756426B1 EP 1756426 B1 EP1756426 B1 EP 1756426B1 EP 05746325 A EP05746325 A EP 05746325A EP 1756426 B1 EP1756426 B1 EP 1756426B1
Authority
EP
European Patent Office
Prior art keywords
rotor
teeth
pump
drive shaft
shaft
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.)
Active
Application number
EP05746325.9A
Other languages
German (de)
French (fr)
Other versions
EP1756426A1 (en
Inventor
Viktor Refenius
Hans Jürgen LAUTH
Bernd Schneider
Bernd Gebhard
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Magna Powertrain Bad Homburg GmbH
Original Assignee
Magna Powertrain Bad Homburg GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=34968623&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP1756426(B1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Magna Powertrain Bad Homburg GmbH filed Critical Magna Powertrain Bad Homburg GmbH
Publication of EP1756426A1 publication Critical patent/EP1756426A1/en
Application granted granted Critical
Publication of EP1756426B1 publication Critical patent/EP1756426B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
    • F04C15/0076—Fixing rotors on shafts, e.g. by clamping together hub and shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T403/00—Joints and connections
    • Y10T403/70—Interfitted members
    • Y10T403/7009—Rotary binding cam or wedge
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T403/00—Joints and connections
    • Y10T403/70—Interfitted members
    • Y10T403/7026—Longitudinally splined or fluted rod
    • Y10T403/7035—Specific angle or shape of rib, key, groove, or shoulder

Definitions

  • From the DE 10011065 A1 is a coupling between two waves known, wherein a number of lateral surfaces cooperate with contact surfaces of a cavity.
  • the EP 0458449 A1 shows a driving tool that creates one and has concave and convex surfaces, with no skewing is compensated.
  • a rotary piston machine in which the power transmission is produced by a splined connection. It is a pump in which a pinion is rotated in a ring gear, thereby forming a plurality of displacement cells. The pump is moved via a cardan shaft, which carries spherical outer splines. This is engaged with the pinion. In such a pump arrangement, no centering is provided. Also the US 3606598 A shows a rotary pump with a propeller shaft. Again, there is no centering of the drive between PTO and pinion. From the state oftechnik for example, the clutch Atlas, Schalitz, AGT Verlag Georg Thun, January 1, 1969, page 9 It is known that in toothed couplings different types of support of the sleeve relative to the hub are used.
  • a pump in which the toothing can be additionally acted upon by a transverse force.
  • Another feature of the toothing according to the invention is that between the teeth 7 of the rotor and the teeth 19 of the shaft results in a game, which may include an angular range of 3 ° to 12 °, preferably 6 °.
  • This game has the advantage that at low torsional shocks of the shaft within this range of play, the torsional impacts are not transmitted to the rotor form-fitting manner.
  • the friction forces occurring between the outer diameter 23 of the shaft toothing 19 and the inner diameter 11 of the rotor toothing 7 act as damping forces between the two movements of the rotor and shaft.
  • the inventive solution of this gearing is therefore the combination of the advantages of an outer diameter-centered spline connection, a spline connection with involute flanks, the crown of the teeth in the axial direction for intercepting angular errors between rotor and shaft and increased clearance between the tooth flanks.
  • the invention is particularly useful for pumps which are stressed by their installation location with torsional vibrations, such as. As in Dieselvor constitupumpen in which the diesel engine causes corresponding vibrations on the drive shaft.
  • the axial crowning of the toothing serves to compensate for the possible misalignment of the rotor relative to the drive shaft, which is fastened, for example, to a camshaft of the internal combustion engine.
  • the external diameter centering of the toothing on the shaft supports the transverse forces during operation.
  • the invention can be used mutatis mutandis for other pumps in which the torque entrainment between the drive shaft and the driven by the shaft gear is also acted upon with corresponding transverse forces. But also for not querkraftbeetzmannte pumps such. B. saubige vane pumps, this gearing is advantageous because the outer diameter centering of the shaft teeth and the inner diameter centering of the rotor for a better centering of the shaft as known gears. Again, a possible skewing of the rotor relative to the shaft by the axial crowning of this toothing according to the invention can be compensated.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Rotary Pumps (AREA)

Description

Die Erfindung betrifft eine Pumpe, insbesondere eine Flügelzellenpumpe oder Rollenzellenpumpe, mit einer Rotationsgruppe, welche unter anderem einen Rotor mit radial verschiebbaren Flügeln oder Rollen aufweist, und mit einer Antriebswelle, wobei die Antriebswelle und der Rotor durch eine Verzahnung an der Antriebswelle und am Rotor zur Drehmitnahme miteinander verbunden sind.The invention relates to a pump, in particular a vane pump or roller-cell pump, with a rotation group, which has, inter alia, a rotor with radially movable wings or rollers, and with a drive shaft, wherein the drive shaft and the rotor by a toothing on the drive shaft and the rotor for Rotational drive are connected together.

Derartige Pumpen sind bekannt. Dabei weisen die Pumpen beispielsweise Zahnwellen-Verbindungen mit Evolventenflanken nach DIN 5480 oder Keilwellen-Verbindungen mit geraden Flanken nach DIN 5463 auf. Beide Arten von Verbindungen verfügen nicht über eine axiale Balligkeit an der Verzahnung, so dass es nicht möglich ist, eine Schiefstellung zwischen den Antriebspartnern auszugleichen. Durch das geringe Spiel zwischen den Zahnflanken werden außerdem Torsionsstöße aus der Antriebswelle ungedämpft an die Antriebspartner weitergeleitet, so dass der Verschleiß an den Antriebspartnern begünstigt wird.
Aus der US 4231727B1 ist eine Flügelzellenpumpe bekannt, bei der Antriebswelle und Rotor über eine Verzahnung miteinander verbunden sind. Die Kopplung ist dabei so ausgelegt, dass die beiden Elemente miteinander fluchten und Winkelfehler ausgeschlossen sind.
Aus der DE 10011065 A1 ist eine Kupplung zwischen zwei Wellen bekannt, wobei eine Anzahl von Mantelflächen mit Kontaktflächen eines Hohlraums zusammenwirken.
Die EP 0458449 A1 zeigt ein Antriebswerkzeug, das einen schafft und konkave und konvexe Oberflächen aufweist, wobei keine Schiefstellung ausgeglichen wird.Such pumps are known. The pumps have, for example, toothed shaft connections with involute flanks according to DIN 5480 or splined shaft connections with straight flanks according to DIN 5463. Both types of connections do not have an axial crown on the teeth, so that it is not possible to compensate for a misalignment between the drive partners. Due to the small clearance between the tooth flanks also torsional shocks from the drive shaft are passed undamped to the drive partners, so that the wear on the drive partners is favored.
From the US 4231727B1 is a vane pump known in the drive shaft and rotor are connected to each other via a toothing. The coupling is designed so that the two elements are aligned and angle errors are excluded.
From the DE 10011065 A1 is a coupling between two waves known, wherein a number of lateral surfaces cooperate with contact surfaces of a cavity.
The EP 0458449 A1 shows a driving tool that creates one and has concave and convex surfaces, with no skewing is compensated.

Aus der DE 2849994A1 ist eine Rotation-Kolbenmaschine bekannt, bei der die Kraftübertragung durch eine Keilzahnverbindung hergestellt wird. Es handelt sich dabei um eine Pumpe, bei der ein Ritzel in einem Hohlrad gedreht wird, wodurch sich eine Mehrzahl von Verdrängerzellen bilden. Bewegt wird die Pumpe über eine Gelenkwelle, die ballige Außenkeilzähne trägt. Diese steht in Eingriff mit dem Ritzel. In einer solchen Pumpenanordnung ist keine Zentrierung vorgesehen.
Auch die US 3606598 A zeigt eine Rotationspumpe mit einer Gelenkwelle. Auch hier findet keine Zentrierung des Antriebs zwischen Gelenkwelle und Ritzel statt.
Aus dem Stand der Technik beispielsweise dem, Kupplungsatlas, Schalitz, AGT Verlag Georg Thun, 1. Januar 1969, Seite 9 ist bekannt, dass bei Zahnkupplungen verschiedene Arten der Abstützung der Hülse gegenüber der Nabe eingesetzt werden.From the DE 2849994A1 a rotary piston machine is known in which the power transmission is produced by a splined connection. It is a pump in which a pinion is rotated in a ring gear, thereby forming a plurality of displacement cells. The pump is moved via a cardan shaft, which carries spherical outer splines. This is engaged with the pinion. In such a pump arrangement, no centering is provided.
Also the US 3606598 A shows a rotary pump with a propeller shaft. Again, there is no centering of the drive between PTO and pinion.
From the state of Technik for example, the clutch Atlas, Schalitz, AGT Verlag Georg Thun, January 1, 1969, page 9 It is known that in toothed couplings different types of support of the sleeve relative to the hub are used.

Eine Lösung mit einer außenzentrierten Verzahnung eines Pumpenrads wird in der DE 10235279 A1 vorgestellt.A solution with an externally centered toothing of a pump wheel is in the DE 10235279 A1 presented.

Keine der vorgestellten Lösung erlaubt es eine Pumpe zu betreiben, wobei die Schiefstellung zwischen Antriebswelle und Rotor auf effiziente Weise ausgeglichen wird.None of the proposed solution makes it possible to operate a pump, wherein the misalignment between the drive shaft and rotor is compensated in an efficient manner.

Es ist Aufgabe der Erfindung, eine Pumpe darzustellen, die Schiefstellungen effizient auch unter schwierigen Bedingungen ausgleichen kann.It is an object of the invention to present a pump that can compensate for misalignments efficiently even under difficult conditions.

Die Aufgabe wird gelöst durch eine Pumpe, insbesondere eine Flügetzellenpumpe oder Rollenzellenpumpe, mit einer Rotationsgruppe, welche unter anderem einen Rotor mit radial verschiebbaren Flügeln oder Rollen aufweist, und mit einer Antriebswelle, wobei die Antriebswelle und der Rotor durch eine Verzahnung an der Antriebswelle und am Rotor zur Drehmitnahme miteinander verbunden sind, wobei erfindungsgemäß die Verzahnung axial ballig und radial außenzentriert ausgeführt ist.The object is achieved by a pump, in particular a winged-cell pump or roller-cell pump, with a rotation group which, inter alia, has a rotor with radially displaceable vanes or rollers, and with a drive shaft, wherein the drive shaft and the rotor by a toothing on the drive shaft and on Rotor are connected to the rotational drive, wherein according to the invention, the toothing is designed to be axially convex and radially outwardly centered.

Die Außenzentrierung hat den Vorteil, dass sie Querkräfte abstützen kann. Bei zweihübigen Flügelzellenpumpen sorgt die Außenzentrierung für eine bessere Zentrierung.The outer centering has the advantage that it can support transverse forces. For two-hull vane pumps, the outer centering ensures better centering.

Bevorzugt wird eine Pumpe, bei welcher die Verzahnung zusätzlich ein Umfangsspiel zwischen den Zahnflanken aufweist. Eine erfindungsgemäße Pumpe zeichnet sich dadurch aus, dass das Umfangsspiel einen Winkelbereich von 3° bis 12°, vorzugsweise 6° umfasst.Preference is given to a pump in which the toothing additionally has a circumferential clearance between the tooth flanks. A pump according to the invention is characterized in that the circumferential clearance comprises an angle range of 3 ° to 12 °, preferably 6 °.

Bevorzugt wird auch eine Pumpe, bei welcher die Verzahnung zusätzlich mit einer Querkraft beaufschlagbar ist.Also preferred is a pump in which the toothing can be additionally acted upon by a transverse force.

Eine erfindungsgemäße Pumpe zeichnet sich dadurch aus, dass die Querkraft an den Außenzentrierflächen tangentiale Reibungskräfte zwischen der Antriebswelle und dem Rotor bzw. dem Zahnrad erzeugt. Das hat den Vorteil, dass durch das Umfangsspiel und die Reibungskräfte Torsionsstöße gedämpft werden können. Bevorzugt wird weiterhin eine Pumpe, bei welcher die Zahnflanken der Verzahnung die Form einer Evolventenverzahnung aufweisen. Auch wird eine Pumpe bevorzugt, bei welcher die Flanken in axialer Richtung ballig ausgeführt sein können.A pump according to the invention is characterized in that the transverse force generates tangential frictional forces on the outer centering surfaces between the drive shaft and the rotor or the toothed wheel. This has the advantage that torsional impacts can be dampened by the circumferential play and the frictional forces. Furthermore, a pump is preferred in which the tooth flanks of the toothing have the shape of an involute toothing. Also, a pump is preferred in which the flanks can be made spherical in the axial direction.

Eine erfindungsgemäße Pumpe zeichnet sich dadurch aus, dass die Zähne der Welle breiter ausgeführt sind als die Zähne des Rotors. Das hat den Vorteil, dass die Zähne der Welle, welche die Querkraft aufnehmen und das Reibungsmoment erzeugen müssen, dafür eine entsprechend höhere Festigkeit aufweisen können. Bevorzugt wird auch eine Pumpe, bei welcher die Zähne der Welle mehr als doppelt so breit sind wie die Zähne des Rotors.A pump according to the invention is characterized in that the teeth of the shaft are made wider than the teeth of the rotor. This has the advantage that the teeth of the shaft, which must absorb the transverse force and generate the frictional torque, can have a correspondingly higher strength. Also preferred is a pump, where the teeth of the shaft are more than twice as wide as the teeth of the rotor.

Die Pumpe wird nun anhand der Figuren beschrieben.

Figur 1
zeigt in Aufsicht einen Rotor mit einer erfindungsgemäßen Verzahnung.
Figur 2
zeigt eine Vergrößerung der Rotorverzahnung.
Figur 3
zeigt ein Ende einer Antriebswelle mit der erfindungsgemäßen Verzahnung.
Figur 4
zeigt vergrößert im Querschnitt die Verzahnung der Antriebswelle.
Figur 5
zeigt in Aufsicht den Zusammenbau einer Flügelzellenpumpe mit der erfindungsgemäßen Verzahnung zwischen Antriebswelle und Rotor.
The pump will now be described with reference to the figures.
FIG. 1
shows in plan view a rotor with a toothing according to the invention.
FIG. 2
shows an enlargement of the rotor toothing.
FIG. 3
shows one end of a drive shaft with the toothing according to the invention.
FIG. 4
shows enlarged in cross section, the teeth of the drive shaft.
FIG. 5
shows in plan the assembly of a vane pump with the inventive toothing between the drive shaft and rotor.

In Figur 1 ist ein Rotor 1 einer sechsflügeligen Flügelzellenpumpe mit einer erfindungsgemäßen Innenverzahnung dargestellt. Der Rotor enthält sechs Schlitze 3, in welchen hier nicht dargestellte Flügel radial verschieblich gelagert sind, welche mit ihren Flügelköpfen an einer entsprechenden Hubringkontur der Flügelzellenpumpe entlang gleiten. Der Rotor enthält in seiner Mitte eine Verzahnung mit vier Zähnen 7, welche vom Rotor nach innen mit einer Fase dargestellt sind.In FIG. 1 is a rotor 1 of a six-bladed vane pump with an internal toothing according to the invention shown. The rotor contains six slots 3, in which wings, not shown here, are mounted so as to be radially displaceable, which slide with their wing heads along a corresponding stroke contour of the vane pump. The rotor contains in its center a toothing with four teeth 7, which are represented by the rotor inwardly with a chamfer.

In Figur 2 ist die Rotorverzahnung vergrößert dargestellt. Die vier Zähne 7 weisen Flanken 9 auf, welche in ihrer Form als Evolventenverzahnung ausgeführt sind. Die Zahnfüße 13 münden in einen Fußkreisdurchmesser 11, welcher als Außenzentrierkreis zwischen der Rotorverzahnung und der Wellenverzahnung dient.In FIG. 2 the rotor toothing is shown enlarged. The four teeth 7 have flanks 9, which are designed in their shape as involute. The tooth roots 13 open into a root diameter 11, which serves as Außenzentrierkreis between the rotor toothing and the shaft toothing.

In Figur 3 ist das verzahnte Ende 15 einer Antriebswelle 17 dargestellt. Das verzahnte Wellenende 15 weist vier Zähne 19 auf, welche in axialer Richtung an ihren Zahnköpfen 21 leicht ballig ausgeführt sind, was in der Darstellung schwer zu erkennen ist. Das Wellenende 15 läuft in einer Zentrier- und Montagespitze 22 aus, wodurch das Montieren der Welle in den Rotor entsprechend erleichtert wird. Die Zähne 19 weisen eine entsprechend große Breite auf, wie in Figur 4 besser zu erkennen ist.In FIG. 3 the toothed end 15 of a drive shaft 17 is shown. The toothed shaft end 15 has four teeth 19 which are slightly convex in the axial direction of their tooth heads 21, which is difficult to see in the illustration. The shaft end 15 extends in a centering and mounting tip 22, whereby the mounting of the shaft is facilitated in the rotor accordingly. The teeth 19 have a correspondingly large width, as in FIG. 4 is better to recognize.

In Figur 4 ist die Verzahnung der Welle im Querschnitt dargestellt. Die vier Zähne 19 weisen eine relativ große Breite mit einer Zahnkopfoberfläche 24 auf, wobei diese Oberfläche einen kreisförmigen Außendurchmesser darstellt, welcher für die Zentrierung des Rotors auf der Welle sorgt. Der kreisförmige Außendurchmesser 23 der Wellenverzahnung geht in den Punkten 25 in eine Evolventenzahnflanke 27 über, welche dann in einen Fußkreis 29 der Verzahnung übergeht. Es ist klar erkennbar, dass die Breite der Wellenzähne 19 entschieden größer ist als die Breite der Rotorzähne 7. Das ist erfindungsgemäß so gewollt, da die Wellenverzahnung festigkeitsmäßig sowohl die Querkräfte, welche auf den Rotor wirken, aufnehmen muss, als auch das Antriebsmoment von der Welle in den Rotor einbringen muss. Dazu bedarf es eines entsprechenden Materialquerschnitts der Welle, insbesondere der Wellenverzahnung. Bekannte Verzahnungen haben gerade bei der Aufnahme von Querkräften hier entsprechende Probleme.In FIG. 4 the toothing of the shaft is shown in cross section. The four teeth 19 have a relatively large width with a tooth tip surface 24, which surface presents a circular outer diameter, which provides for the centering of the rotor on the shaft. The circular outer diameter 23 of the shaft toothing merges at the points 25 into an involute tooth flank 27, which then merges into a root circle 29 of the toothing. It is clearly seen that the width of the shaft teeth 19 is decidedly greater than the width of the rotor teeth 7. The invention is so intentional, since the shaft teeth strength must absorb both the transverse forces acting on the rotor, and the drive torque of the Shaft must bring in the rotor. This requires a corresponding material cross-section of the shaft, in particular the shaft toothing. Known teeth have just in the absorption of shear forces here corresponding problems.

In Figur 5 ist der Zusammenbau einer entsprechenden Flügelzellenpumpe 31 dargestellt. Innerhalb eines Pumpengehäuses 33 ist ein Hubkonturring 35 gelagert, welcher innerhalb des Gehäuses durch einen Stift 39 in einer Rundlochbohrung und mittels eines weiteren Stiftes 37 in einer Langlochbohrung gelagert ist. Der Hubkonturring 35 enthält eine Hubkontur 41, welche in diesem Fall kreisförmig ist, in anderen Fällen, beispielsweise bei zweihübigen Flügelzellenpumpen, aber auch beliebige andere Konturen aufweisen kann. Sechs Flügel 43, welche radial gleitend in den Schlitzen des Rotors 1 gelagert sind, gleiten mit ihren Flügelköpfen an der Hubkontur 41 entlang und erzeugen somit Ansaug- und Verdrängerräume. Die Funktion einer derartigen Flügelzellenpumpe ist bekannt und bedarf hier keiner weiteren Erläuterung. Für die Funktion der Pumpe wichtig ist in diesem Falle, dass die Pumpe als einhubige Flügelzellenpumpe durch die Position ihrer mit Druck beaufschlagten Zelle, beispielsweise der Zelle 45, eine Radialkraft 47, hier durch einen Pfeil dargestellt, auf den Rotor erzeugt, welche durch die Rotorverzahnung auf die Welle übertragen wird und von der Welle 17 aufgefangen werden muss. Dabei wird die Radialkraft über die kreisförmige Verzahnungsoberfläche 11 des Rotors auf die kreisförmige Verzahnungsoberfläche 24 der Welle übertragen, wobei diese beiden Anteile der Verzahnungsform eine Außendurchmesserzentrierung auf der Welle darstellen.In FIG. 5 the assembly of a corresponding vane pump 31 is shown. Within a pump housing 33, a Hubkonturring 35 is mounted, which is mounted within the housing by a pin 39 in a round hole bore and by means of a further pin 37 in a slot. The Hubkonturring 35 includes a stroke contour 41, which is circular in this case, in other cases, for example, in zwehübigen vane pumps, but may also have any other contours. Six wings 43, which are mounted radially slidably in the slots of the rotor 1, slide with their wing heads along the stroke contour 41 along and thus produce suction and displacement chambers. The function of such a vane pump is known and requires no further explanation here. Important for the function of the pump in this case is that the pump as a one-stroke vane pump by the position of its pressurized cell, such as the cell 45, a radial force 47, shown here by an arrow, generated on the rotor, which through the rotor toothing is transmitted to the shaft and must be absorbed by the shaft 17. In this case, the radial force is transmitted via the circular tooth surface 11 of the rotor to the circular tooth surface 24 of the shaft, these two parts of the tooth form an outer diameter centering on the shaft.

Ein weiteres Merkmal der erfindungsgemäßen Verzahnung ist, dass sich zwischen den Zähnen 7 des Rotors und den Zähnen 19 der Welle ein Spiel ergibt, welches einen Winkelbereich von 3° bis 12°, vorzugsweise von 6° umfassen kann. Dieses Spiel hat den Vorteil, dass bei geringen Torsionsstößen der Welle innerhalb dieses Spielbereiches die Torsionsstöße nicht formschlüssig auf den Rotor übertragen werden. Die zwischen dem Außendurchmesser 23 der Wellenverzahnung 19 und dem Innendurchmesser 11 der Rotorverzahnung 7 auftretenden Reibungskräfte wirken dabei als dämpfende Kräfte zwischen den beiden Bewegungen von Rotor und Welle. Die erfinderische Lösung dieser Verzahnung besteht also in der Kombination der Vorteile einer außendurchmesserzentrierten Keilwellen-Verbindung, einer Zahnwellenverbindung mit Evolventenflanken, der Balligkeit der Verzahnung in axialer Richtung zum Abfangen von Winkelfehlern zwischen Rotor und Welle und einem erhöhten Spiel zwischen den Zahnflanken. Die Erfindung ist insbesondere nützlich für Pumpen, welche durch ihren Einbauort mit Torsionsschwingungen beansprucht werden, wie z. B. bei Dieselvorförderpumpen, bei welchen der Dieselmotor entsprechende Schwingungen an der Antriebswelle verursacht. Die axiale Balligkeit der Verzahnung dient zum Ausgleich der möglichen Schiefstellungen des Rotors gegenüber der Antriebswelle, welche beispielsweise an einer Nockenwelle des Verbrennungsmotors befestigt ist. Die Außendurchmesserzentrierung der Verzahnung auf der Welle stützt im Betrieb die Querkräfte ab. Damit wird eine Relativbewegung der Antriebspartner entlang der Verzahnungsflanken verhindert und damit der Verschleiß der Verzahnung gegenüber einer herkömmlichen Verzahnung - reduziert. Zugleich wird die Reibung an der Außendurchmesserzentrierung der Verzahnung der Antriebspartner zur Dämpfung der Torsionsschwingungen verwendet. Durch das erhöhte Spiel zwischen den Zahnflanken wird den Antriebspartnern die Möglichkeit gegeben, sich relativ zueinander zu verdrehen und mit der Reibung an der Außendurchmesserzentrierung die Einwirkungen der Torsionsschwingungen zu dämpfen. Dadurch werden die Kontaktstöße an den Zahnflanken aufgrund von Torsionsschwingungen minimiert oder aufgehoben, was zur Minimierung des Verschleißes führt.Another feature of the toothing according to the invention is that between the teeth 7 of the rotor and the teeth 19 of the shaft results in a game, which may include an angular range of 3 ° to 12 °, preferably 6 °. This game has the advantage that at low torsional shocks of the shaft within this range of play, the torsional impacts are not transmitted to the rotor form-fitting manner. The friction forces occurring between the outer diameter 23 of the shaft toothing 19 and the inner diameter 11 of the rotor toothing 7 act as damping forces between the two movements of the rotor and shaft. The inventive solution of this gearing is therefore the combination of the advantages of an outer diameter-centered spline connection, a spline connection with involute flanks, the crown of the teeth in the axial direction for intercepting angular errors between rotor and shaft and increased clearance between the tooth flanks. The invention is particularly useful for pumps which are stressed by their installation location with torsional vibrations, such as. As in Dieselvorförderpumpen in which the diesel engine causes corresponding vibrations on the drive shaft. The axial crowning of the toothing serves to compensate for the possible misalignment of the rotor relative to the drive shaft, which is fastened, for example, to a camshaft of the internal combustion engine. The external diameter centering of the toothing on the shaft supports the transverse forces during operation. Thus, a relative movement of the drive partners along the tooth flanks is prevented and thus the wear of the toothing over a conventional toothing - reduced. At the same time the friction is used at the Außendurchmesserzentrierung the teeth of the drive partners for damping the torsional vibrations. Due to the increased clearance between the tooth flanks, the drive partners are given the opportunity to rotate relative to each other and dampen with the friction at the Außendurchmesserzentrierung the effects of torsional vibrations. As a result, the contact impacts on the tooth flanks due to torsional vibrations are minimized or eliminated, resulting in the minimization of wear.

Die Erfindung kann sinngemäß auch für andere Pumpen verwendet werden, bei welchen die Drehmomentmitnahme zwischen der Antriebswelle und dem durch die Welle angetriebenen Zahnrad auch mit entsprechenden Querkräften beaufschlagt ist. Aber auch für nicht querkraftbeaufschlagte Pumpen wie z. B. zweihübige Flügelzellenpumpen ist diese Verzahnung von Vorteil, da die Außendurchmesserzentrierung der Wellenverzahnung und die Innendurchmesserzentrierung des Rotors für eine bessere Zentrierung der Welle sorgt als bekannte Verzahnungen. Auch hier ist eine evtl. Schiefstellung des Rotors gegenüber der Welle durch die axiale Balligkeit dieser erfindungsgemäßen Verzahnung kompensierbar.The invention can be used mutatis mutandis for other pumps in which the torque entrainment between the drive shaft and the driven by the shaft gear is also acted upon with corresponding transverse forces. But also for not querkraftbeaufschlagte pumps such. B. zweihübige vane pumps, this gearing is advantageous because the outer diameter centering of the shaft teeth and the inner diameter centering of the rotor for a better centering of the shaft as known gears. Again, a possible skewing of the rotor relative to the shaft by the axial crowning of this toothing according to the invention can be compensated.

BezugszeichenlisteLIST OF REFERENCE NUMBERS

11
Rotorrotor
33
Schlitzeslots
77
Zähne der RotorverzahnungTeeth of the rotor toothing
99
Zahnflanken der RotorverzahnungTooth flanks of the rotor toothing
1111
Fußkreisdurchmesser der RotorverzahnungRoot diameter of the rotor toothing
1313
Zahnfuß der RotorverzahnungTooth base of the rotor toothing
1515
Verzahntes Ende der AntriebswelleSerrated end of the drive shaft
1717
Antriebswelledrive shaft
1919
Zähne der AntriebswelleTeeth of the drive shaft
2121
Zahnköpfe der AntriebswelleTeeth of the drive shaft
2222
Montagespitze der AntriebswelleMounting tip of the drive shaft
2323
Außendurchmesser der WellenverzahnungOuter diameter of the shaft toothing
2424
Zahnkopfoberfläche der AntriebswelleTooth surface of the drive shaft
2525
Übergang der Wellenverzahnung in EvolventenzahnflankeTransition of the serration into the involute tooth flank
2727
Evolventenzahnflanke der WellenverzahnungInvolute tooth flank of the shaft toothing
2929
Fußkreis der WellenverzahnungRoot circle of the shaft toothing
3131
FlügelzellenpumpeVane pump
3333
Pumpengehäusepump housing
3535
Hubkonturringstroke contour ring
3737
Stift für HubkonturringPin for Hubkonturring
3939
Stift für HubkonturringPin for Hubkonturring
4141
Hubkontur des HubkonturringesHub contour of Hubkonturringes
4343
Flügelwing
4545
Zelle der FlügelzellenpumpeCell of the vane pump
4747
Radialkraft auf den RotorRadial force on the rotor

Claims (8)

  1. Pump, in particular vane cell pump or roller cell pump, having a rotational group which has, inter alia, a rotor (1) with radially displaceable vanes (43) or rollers, and having a drive shaft (17), the drive shaft (17) and the rotor (1) being connected to one another for rotary driving by way of a toothing system on the drive shaft and on the rotor, characterized in that the toothing system having rotor teeth (7) and drive shaft teeth (19) is configured so as to be axially crowned and externally centred radially, wherein the drive shaft teeth (19) have a width which is greater than the width of the rotor teeth (7).
  2. Pump according to Claim 1, characterized in that the toothing system (7, 19) additionally has a circumferential play between the tooth flanks.
  3. Pump according to either of the preceding claims, characterized in that the circumferential play comprises an angular range from 3° to 12°, preferably 6°.
  4. Pump according to one of the preceding claims, characterized in that the toothing system (7, 19) can additionally be loaded with a transverse force (47).
  5. Pump according to Claim 4, characterized in that the transverse force (47) generates tangential frictional forces between the drive shaft and the rotor on the outer centring faces (11, 24).
  6. Pump according to one of the preceding claims, characterized in that the tooth flanks (9, 27) of the toothing system (7, 19) have the shape of an involute toothing system.
  7. Pump according to one of the preceding claims, characterized in that the tooth flanks (9, 27) can also be of crowned configuration in the axial direction.
  8. Pump according to one of the preceding claims, characterized in that the teeth (19) of the shaft (17) are configured so as to be more than twice as wide as the teeth (7) of the rotor (1).
EP05746325.9A 2004-05-07 2005-04-30 Pumps Active EP1756426B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004022670 2004-05-07
PCT/DE2005/000800 WO2005108791A1 (en) 2004-05-07 2005-04-30 Pumps

Publications (2)

Publication Number Publication Date
EP1756426A1 EP1756426A1 (en) 2007-02-28
EP1756426B1 true EP1756426B1 (en) 2017-04-05

Family

ID=34968623

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05746325.9A Active EP1756426B1 (en) 2004-05-07 2005-04-30 Pumps

Country Status (4)

Country Link
US (1) US7695262B2 (en)
EP (1) EP1756426B1 (en)
DE (1) DE112005001635A5 (en)
WO (1) WO2005108791A1 (en)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2005108791A1 (en) 2004-05-07 2005-11-17 Luk Fahrzeug-Hydraulik Gmbh & Co. Kg Pumps
DE102006012868B4 (en) * 2006-03-21 2021-02-04 Robert Bosch Gmbh Positive displacement pump
AU2013295781B2 (en) 2012-07-24 2017-10-05 Blephex, Llc Device for treating an ocular disorder
FR3033370B1 (en) * 2015-03-02 2017-03-24 Peugeot Citroen Automobiles Sa VANE PUMP
CN106762857A (en) * 2015-11-23 2017-05-31 李世福 Dial type fluid mover
CN109012958B (en) * 2018-08-01 2020-11-03 阜阳市顺亚智能设备有限公司 Flexible crushing device of metal crusher
WO2020082010A1 (en) 2018-10-18 2020-04-23 Nebraska Irrigation, Inc. Improved inline coupler

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1063036B (en) 1954-07-26 1959-08-06 Jabsco Pump Company Fixing a pump impeller on its shaft
US3606598A (en) * 1970-04-08 1971-09-20 Eaton Yale & Towne Fluid operated motor
DE2146972A1 (en) 1971-09-20 1973-04-05 Trw Inc HYDRAULIC MACHINE LIKE PUMP, MOTOR OR MEASURING DEVICE
US3862814A (en) 1973-08-08 1975-01-28 Eaton Corp Lubrication system for a hydraulic device
DE2849994A1 (en) * 1977-11-21 1979-05-23 Eaton Corp ROTARY PISTON MACHINE
DE3780158T2 (en) 1985-08-24 1993-02-25 Shen Peiji CYCLLOIDED AQUIDISTANT CURVE TRANSMISSION MECHANISM AND ITS DEVICE.
DE19957886A1 (en) 1998-12-07 2000-07-20 Bosch Braking Systems Co Displacement pump eg for power assisted vehicle steering systems
EP1196699B1 (en) 1999-07-20 2003-02-12 ZF FRIEDRICHSHAFEN Aktiengesellschaft Power distribution transmission
DE10235279A1 (en) * 2002-08-02 2004-02-19 Zf Friedrichshafen Ag Drive train for motor vehicle has pumpwheel mounted directly on off-center teeth of its drive shaft
WO2005108791A1 (en) 2004-05-07 2005-11-17 Luk Fahrzeug-Hydraulik Gmbh & Co. Kg Pumps

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2182072A (en) * 1937-10-11 1939-12-05 Eddington Metal Specialty Co Rotary pump
US2297390A (en) * 1939-01-18 1942-09-29 Burger Peter Splined connection
US2389728A (en) * 1943-10-14 1945-11-27 Myron F Hill Elliptical contour for rotor teeth
US2989951A (en) * 1959-04-29 1961-06-27 Germane Corp Rotary fluid pressure device
US3247803A (en) * 1963-03-20 1966-04-26 Chrysler Corp Hydraulic pump
US3288078A (en) * 1964-08-25 1966-11-29 Trw Inc Hydraulic device
DE2631152C2 (en) 1976-07-10 1985-08-08 Volkswagenwerk Ag, 3180 Wolfsburg Vane vacuum pump
US4424013A (en) * 1981-01-19 1984-01-03 Bauman Richard H Energized-fluid machine
DE3242274C1 (en) * 1982-11-15 1984-05-30 Danfoss A/S, Nordborg Tooth coupling between pinion and cardan shaft of an internal-axis rotary piston machine
US5237893A (en) * 1990-05-22 1993-08-24 Textron Inc. Driver with fastener retention means
US5083909A (en) * 1990-11-29 1992-01-28 The United States Of America As Represented By The Secretary Of The Navy Seawater hydraulic vane type pump
DE10011065A1 (en) 2000-03-07 2001-09-13 Delphi Tech Inc Torque transmission coupling for two steering column sections in road vehicle, with one end of first shaft having face-side hollow space enclosed by at least three abutting contact surfaces
DE10053938A1 (en) 2000-10-31 2002-05-16 Nord Micro Ag & Co Ohg Shaft and shaft-hub connection for the transmission of torques
US6932587B2 (en) * 2002-09-13 2005-08-23 Parker-Hannifin Corporation Gerotor motor with valve in rotor
DE102004009838A1 (en) 2004-02-28 2005-09-22 Zf Lenksysteme Gmbh Fluid vane pump has rotor mounted onto shaft by toothed joint with centre aligning head flank on tooth

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1063036B (en) 1954-07-26 1959-08-06 Jabsco Pump Company Fixing a pump impeller on its shaft
US3606598A (en) * 1970-04-08 1971-09-20 Eaton Yale & Towne Fluid operated motor
DE2146972A1 (en) 1971-09-20 1973-04-05 Trw Inc HYDRAULIC MACHINE LIKE PUMP, MOTOR OR MEASURING DEVICE
US3862814A (en) 1973-08-08 1975-01-28 Eaton Corp Lubrication system for a hydraulic device
DE2849994A1 (en) * 1977-11-21 1979-05-23 Eaton Corp ROTARY PISTON MACHINE
DE3780158T2 (en) 1985-08-24 1993-02-25 Shen Peiji CYCLLOIDED AQUIDISTANT CURVE TRANSMISSION MECHANISM AND ITS DEVICE.
DE19957886A1 (en) 1998-12-07 2000-07-20 Bosch Braking Systems Co Displacement pump eg for power assisted vehicle steering systems
EP1196699B1 (en) 1999-07-20 2003-02-12 ZF FRIEDRICHSHAFEN Aktiengesellschaft Power distribution transmission
DE10235279A1 (en) * 2002-08-02 2004-02-19 Zf Friedrichshafen Ag Drive train for motor vehicle has pumpwheel mounted directly on off-center teeth of its drive shaft
WO2005108791A1 (en) 2004-05-07 2005-11-17 Luk Fahrzeug-Hydraulik Gmbh & Co. Kg Pumps

Non-Patent Citations (7)

* Cited by examiner, † Cited by third party
Title
AUGUST SCHALITZ: "KUPPLUNGS-ATLAS", 1 January 1969, A.G.T - VERLAG GEORG THUM, Ludwigsburg, pages: 9 *
AUGUST SCHALITZ: "Kupplungsatlas", 1969, article "Zahnkupplungen", pages: 9, XP055277047
DEUTSCHE NORM: "Zahnwellen-verbindungen mit evolventenflanken", DEUTSCHE NORM DIN 5480, October 1991 (1991-10-01), pages 1 - 5, XP055452713
FRANZ. G. KOLLMANN: "Welle-Nabe-Verbindungen, Konstruktionsbücher", vol. 3, 1984, article "Welle-Nabe-Verbindungen, Konstruktionsbücher", pages: 135, XP055277060
KÖHLER ET AL.: "Maschinenteile Teil 1, 3", 1992, Stuttgart, pages: 223 und 224, XP055277067
WIKIPEDIA AUSDRUCK ZAHNRÄDER, pages 2
ZAHNRÄDER, 1932, Berlin, pages 55

Also Published As

Publication number Publication date
WO2005108791A1 (en) 2005-11-17
US7695262B2 (en) 2010-04-13
US20080260563A1 (en) 2008-10-23
EP1756426A1 (en) 2007-02-28
DE112005001635A5 (en) 2007-05-31

Similar Documents

Publication Publication Date Title
EP1756426B1 (en) Pumps
EP1523610B1 (en) Device for modifying the control times of an internal combustion engine
EP3415238B1 (en) Vertical mill gear
DE3338737A1 (en) FLOWING MACHINE IN SPIRAL DESIGN
EP1915553B1 (en) Adapter, planetary gear, drive unit, and method
EP2569525B1 (en) Auxiliary drive
DE202007013982U1 (en) Starter device for a power unit with improved damping
WO2018215227A1 (en) Differential for a motor vehicle
DE3419194C2 (en)
DE102019205608B4 (en) Parking lock wheel
DE10302192B4 (en) Planetary gear with a compensating coupling
EP3050194B1 (en) Assembly with an electric machine
DE102005020232A1 (en) Pump, with a drive shaft and rotor, has meshing teeth at the shaft and rotor to key them together using teeth with an axial camber and which are radially off-center
DE102011008703B4 (en) Device for driving connection
DE102017217215A1 (en) Gear combination with fail-safe, in particular for use for driving an oil pump
DE102016216670B4 (en) Camshaft adjuster
DE102015223903A1 (en) The wave gear
DE102006035228B4 (en) Adapter, planetary gear, drive and procedure
EP2302255B1 (en) Drive device for at least one auxiliary drive
DE102011013918A1 (en) Coupling device for use in drive in housing part of transmission of engine, has flat key formed, particularly integrally with outer toothing of coupling hub portion, where flat key is connected with driven shaft in form-fit manner
DE102009028411A1 (en) Eccentric-differential-reduction gear for use in e.g. wind mill, has auxiliary crank shaft arranged within ring and partially affiliates with output cam members that are coupled to pivotal gear wheel during rotation of gear wheel
DE102004041769A1 (en) Camshaft adjusting device for adjusting the relative angle of a camshaft to a crankshaft of an I.C. engine transfers the driving torque via a coupling star of a first coupling half
DE10352904B4 (en) Differential arrangement with integrated sliding joint
DE19613277A1 (en) Shaft coupling for diesel engine of boat
EP3330483B1 (en) Vacuum pump with a joint assembly allowing compensation of shaft eccentricities

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

17P Request for examination filed

Effective date: 20061207

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU MC NL PL PT RO SE SI SK TR

RIN1 Information on inventor provided before grant (corrected)

Inventor name: REFENIUS, VIKTOR

Inventor name: GEBHARD, BERND

Inventor name: LAUTH, HANS, JUERGEN

Inventor name: SCHNEIDER, BERND

DAX Request for extension of the european patent (deleted)
17Q First examination report despatched

Effective date: 20120206

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: MAGNA POWERTRAIN BAD HOMBURG GMBH

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

TPAC Observations filed by third parties

Free format text: ORIGINAL CODE: EPIDOSNTIPA

INTG Intention to grant announced

Effective date: 20160426

INTC Intention to grant announced (deleted)
GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20161111

GRAJ Information related to disapproval of communication of intention to grant by the applicant or resumption of examination proceedings by the epo deleted

Free format text: ORIGINAL CODE: EPIDOSDIGR1

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTC Intention to grant announced (deleted)
GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

INTG Intention to grant announced

Effective date: 20170215

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU MC NL PL PT RO SE SI SK TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: DE

Ref legal event code: R081

Ref document number: 502005015549

Country of ref document: DE

Owner name: HANON SYSTEMS EFP DEUTSCHLAND GMBH, DE

Free format text: FORMER OWNER: IXETIC BAD HOMBURG GMBH, 61352 BAD HOMBURG, DE

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 882108

Country of ref document: AT

Kind code of ref document: T

Effective date: 20170415

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502005015549

Country of ref document: DE

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20170405

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170405

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170405

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170405

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170405

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170706

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170405

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170705

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170405

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170805

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

REG Reference to a national code

Ref country code: DE

Ref legal event code: R026

Ref document number: 502005015549

Country of ref document: DE

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

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170405

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170405

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170405

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170405

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170405

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170405

26 Opposition filed

Opponent name: GANAHL, BERNHARD

Effective date: 20180105

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 FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170405

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170430

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170430

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170430

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20170430

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20170705

PLBB Reply of patent proprietor to notice(s) of opposition received

Free format text: ORIGINAL CODE: EPIDOSNOBS3

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20180309

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: 20170705

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170430

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170405

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170430

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170606

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 882108

Country of ref document: AT

Kind code of ref document: T

Effective date: 20170430

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170430

PLAB Opposition data, opponent's data or that of the opponent's representative modified

Free format text: ORIGINAL CODE: 0009299OPPO

REG Reference to a national code

Ref country code: DE

Ref legal event code: R100

Ref document number: 502005015549

Country of ref document: DE

R26 Opposition filed (corrected)

Opponent name: GANAHL, BERNHARD

Effective date: 20180105

PLCK Communication despatched that opposition was rejected

Free format text: ORIGINAL CODE: EPIDOSNREJ1

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20050430

REG Reference to a national code

Ref country code: DE

Ref legal event code: R082

Ref document number: 502005015549

Country of ref document: DE

Representative=s name: HOFFMANN - EITLE PATENT- UND RECHTSANWAELTE PA, DE

PLBN Opposition rejected

Free format text: ORIGINAL CODE: 0009273

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: OPPOSITION REJECTED

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170405

27O Opposition rejected

Effective date: 20190509

REG Reference to a national code

Ref country code: DE

Ref legal event code: R082

Ref document number: 502005015549

Country of ref document: DE

Representative=s name: HOFFMANN - EITLE PATENT- UND RECHTSANWAELTE PA, DE

Ref country code: DE

Ref legal event code: R081

Ref document number: 502005015549

Country of ref document: DE

Owner name: HANON SYSTEMS EFP DEUTSCHLAND GMBH, DE

Free format text: FORMER OWNER: MAGNA POWERTRAIN BAD HOMBURG GMBH, 61352 BAD HOMBURG, DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170405

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170405

P01 Opt-out of the competence of the unified patent court (upc) registered

Effective date: 20230613

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20230420

Year of fee payment: 19