EP3014129B1 - Hydraulic cylinder with piston rod - Google Patents
Hydraulic cylinder with piston rod Download PDFInfo
- Publication number
- EP3014129B1 EP3014129B1 EP14731955.2A EP14731955A EP3014129B1 EP 3014129 B1 EP3014129 B1 EP 3014129B1 EP 14731955 A EP14731955 A EP 14731955A EP 3014129 B1 EP3014129 B1 EP 3014129B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- piston rod
- hydraulic cylinder
- split
- pressure chamber
- seal
- 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
Links
- 238000007789 sealing Methods 0.000 claims description 9
- 239000011248 coating agent Substances 0.000 claims description 3
- 238000000576 coating method Methods 0.000 claims description 3
- 230000004323 axial length Effects 0.000 description 2
- 230000003247 decreasing effect Effects 0.000 description 2
- 238000011982 device technology Methods 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 229910001141 Ductile iron Inorganic materials 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000000284 resting effect Effects 0.000 description 1
- 230000000717 retained effect Effects 0.000 description 1
- 239000000725 suspension Substances 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
- F15B15/1423—Component parts; Constructional details
- F15B15/1457—Piston rods
- F15B15/1461—Piston rod sealings
Definitions
- the invention relates to the guidance and mounting of a piston rod in a hydraulic cylinder and the sealing of an annular pressure chamber of the hydraulic cylinder surrounding the piston rod.
- Hydraulic cylinders with a tubular cylinder housing in which a piston is moved, to which a piston rod is fastened at least on one side, with a cylinder base and with a cylinder head through which the piston rod protrudes to the outside are known from the prior art.
- an annular pressure chamber is arranged between the cylinder housing and the piston rod and, viewed axially, between the piston and the end face.
- One from the DE 102010033869A1 known linear unit has a piston with a piston body and a rigid sliding sleeve seated on the piston body, a rubber-elastic support ring being arranged between the sliding sleeve and the piston body.
- the sliding sleeve is mounted on the piston body spaced apart with radial play via the support ring. In this way, the sliding sleeve can tilt in connection with the support ring with respect to the piston body, the support ring being elastically reversibly deformed.
- the flexible suspension of the sliding sleeve causes an automatic adjustment to tolerance-related positional deviations between a housing and the piston body.
- the split bush When the pressure in the annular pressure chamber increases, there is an increasing radial load on the split bushing towards the outside. In order to avoid a corresponding expansion of the split bush and thus an enlargement of the precisely manufactured fit, the split bush must be very dimensionally stable. This can only be achieved with materials with a large E-module or with a large radial expansion or thickness of the split bushing.
- the invention is based on the object of creating a hydraulic cylinder with a piston rod, the ring-shaped pressure chamber of which is sealed with a split bushing, the outlay on device technology being minimized.
- the aim is to create a sealing system that brings about only a low and pressure-independent friction between the piston rod and the components that guide and support it.
- the claimed hydraulic cylinder has a piston rod which is surrounded by an annular pressure chamber and which is guided in a through recess of the hydraulic cylinder.
- a gap bushing forms a gap seal with the piston rod through a precise fit with the piston rod over a certain axial length. This structurally separates the functions of mounting the piston rod and pressure reduction of the chamber pressure in the gap seal.
- the split bushing is inserted with radial play in the hydraulic cylinder, in particular in the cylinder housing, so that a first circular cylindrical annular gap is formed on the outer circumference of the split bushing and is fluidically connected to the pressure chamber.
- a seal is arranged on the outer circumference of the split bush, which is at an axial distance from a first end face of the split sleeve facing the pressure chamber, and the axial distance between the seal and the end face is selected such that the split sleeve is compensated for compressive force in the radial direction.
- the working pressure of the pressure chamber can generate radially inward opposing forces on the gap sleeve on a section of the outer circumference extending from the pressure chamber to the seal, which counterforces are generated in the gap seal between the piston rod and the gap sleeve due to the pressure there on the gap sleeve and radially counteract outwardly directed forces.
- the position of the seal is selected as a function of various parameters of the split bushing, for example as a function of the width, thickness and modulus of elasticity. Then there are no total radial forces on the split bush, so that this is mechanically optimally relieved.
- the mechanically relieved split bushing can be made relatively simple.
- the split bush is preferably circular-cylindrical.
- the seal is preferably inserted into an outer circumferential groove of the split bush.
- a second annular gap is preferably formed between the piston rod and the through recess, the radial dimension of which is smaller than the radial dimension of the first annular gap.
- the seal can adapt to ring gaps of different widths particularly well if it has an outer sealing ring (e.g. piston sealing ring) and an inner O-ring. The latter is compressed in its cross-section and thus tensions the sealing ring outwards against the hydraulic cylinder. In the case of the seal, this results in a "division of tasks" between the sealing function and the elastic application of force radially outwards.
- an outer sealing ring e.g. piston sealing ring
- inner O-ring e.g. piston sealing ring
- the hydraulic cylinder has a cylinder head which is attached to a, for example, tubular cylinder housing of the hydraulic cylinder and in which the through recess for the piston rod is formed, it is particularly preferred if the split bushing rests against the cylinder head with a second end face.
- the second end face can be ground or provided with a coating, for example made of plastic, in order to keep the friction between the split liner and the cylinder head low and to ensure easy radial displaceability of the split liner.
- the gap bushing can easily be accommodated between the cylinder head and a radial projection or a radial step on the inside of the cylinder housing.
- the first end face of the split bushing can delimit the annular pressure chamber.
- a working connection of the pressure chamber should open into the pressure chamber adjacent to the radial projection or the radial step, so that the piston can come as close as possible to the projection or the step and the working range of the hydraulic cylinder according to the invention is maximized.
- a separate slide bearing can be provided for the piston rod in the through recess.
- FIG. 1 A section of a tubular cylinder housing 1 of the hydraulic cylinder according to the invention can be seen.
- a cylinder head 2 is attached to the end of the cylinder housing 1, the radial collar 4 of which protrudes into the cylinder housing 1 in such a way that the two parts 1 and 2 are centered.
- annular pressure chamber 6 In the interior of the cylinder housing 1, an annular pressure chamber 6 is provided which - viewed radially - is delimited by the cylinder housing 1 and a piston rod 8, while - viewed axially - is delimited by a split bushing 10 and a piston (not shown).
- a working connection 12 When pressure medium is applied to the pressure chamber 6 via a working connection 12, the piston moves (in Figure 1 ) to the right and takes the attached piston rod 8 with it. The piston rod retracts. Seen from the cylinder head 2 beyond the piston is a second pressure chamber, not shown in detail. When this pressure medium is supplied, the piston rod extends.
- the piston rod 8 penetrates a through recess 14 of the cylinder head 2, with some play being provided between the piston rod 8 and the through recess 14.
- the piston rod 8 can thus move within narrow limits into an eccentric position with respect to a longitudinal axis 16 of the hydraulic cylinder.
- the cylinder head 2 is made from a material with good sliding properties, for example from a nodular cast iron, the guide and a bearing 18 of the piston rod are formed directly in the through recess 14.
- a spiral groove is introduced over the circumference of the through recess, which into a Figure 1 apparent, but unspecified leakage connection opens on the cylinder head 2.
- the bearing is flushed and cooled by the leakage oil flowing through the spiral groove.
- a pressure-relieved seal package is also provided on the cylinder head 2, which is inserted into the cylinder head 2 and rests on the piston rod 8. More precisely, it is a rod seal 20 which rests against the piston rod 8 and which is tensioned in the direction of the piston rod 8 via an O-ring. Furthermore, a wiper 22 resting on the piston rod 8 is inserted into the cylinder head 2.
- Figure 2 shows an enlarged section of Figure 1 .
- the split sleeve 10 forms a gap seal 24 due to its precisely fitting contact with the piston rod 8.
- On the inner circumference several circumferential and axially spaced grooves are made in the split sleeve 10 over its entire length in order to ensure pressure equalization over the inner circumference.
- a gap 30 also remains between a first end face 38 of the split bushing 10 and the step 28 Hydraulic cylinder always under working pressure p pressure medium from the pressure chamber 6 via the gap 30 into the annular gap on the outer circumference 26 of the gap bushing 10.
- This effect is limited in its axial extent by a piston seal 32 which, together with an O-ring 34, is inserted into a groove on the outer circumference 26 of the split bush 10.
- the O-ring 34 biases the piston seal 32 radially outward against the cylinder housing 1 of the hydraulic cylinder according to the invention.
- the seal of the split bush 10 which consists of the piston seal 32 and the O-ring 34, is arranged on the outer circumference 26 of the split bush 10 at that point at which the working pressure p acting on the outer circumference 26 and the working pressure p1 in acting on the inner circumference compensate for their resulting forces.
- the point is marked with the axial distance 36, which relates to the first end face 38 of the split bushing 10, which the annular channel 6 faces.
- the axial distance 36 can correspond to half the length of the split bush 10, for example.
- a slide bearing can be inserted in the through recess 14 or a coating, for example made of plastic, can be applied in order to guide the piston rod 8 with particularly low friction.
- a hydraulic cylinder is disclosed with a piston rod which is surrounded by an annular pressure chamber and which is guided in a through recess of the hydraulic cylinder.
- a split bushing forms a split seal with the piston rod over a certain axial length and a precise fit with the piston rod.
- a first circular cylindrical annular gap is formed on the outer circumference of the split bush, as a result of which the split bush is inserted into the hydraulic cylinder with radial play.
- the annular gap is fluidically connected to the pressure chamber.
- a seal is arranged on the outer circumference of the split bush and is at an axial distance from a first end face of the split bush facing the pressure chamber.
- the working pressure of the pressure chamber can apply radially inward opposing forces to the split bushing via a section of the outer circumference extending from the pressure chamber to the seal, which counteracts the radially outward forces arising in the gap seal. This relieves the mechanical strain on the split bush.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Actuator (AREA)
Description
Die Erfindung betrifft die Führung und Lagerung einer Kolbenstange in einem Hydraulikzylinder und die Abdichtung einer die Kolbenstange umgebenden ringförmigen Druckkammer des Hydraulikzylinders.The invention relates to the guidance and mounting of a piston rod in a hydraulic cylinder and the sealing of an annular pressure chamber of the hydraulic cylinder surrounding the piston rod.
Aus dem Stand der Technik sind Hydraulikzylinder mit einem rohrförmigen Zylindergehäuse, in dem ein Kolben bewegt wird, an dem zumindest einseitig eine Kolbenstange befestigt ist, mit einem Zylinderboden und mit einem Zylinderkopf, durch den hindurch die Kolbenstange nach außen tritt, bekannt. Dabei ist - radial betrachtet - zwischen dem Zylindergehäuse und der Kolbenstange und - axial betrachtet - zwischen dem Kolben und der Stirnseite eine ringförmige Druckkammer angeordnet.Hydraulic cylinders with a tubular cylinder housing in which a piston is moved, to which a piston rod is fastened at least on one side, with a cylinder base and with a cylinder head through which the piston rod protrudes to the outside are known from the prior art. Here, viewed radially, an annular pressure chamber is arranged between the cylinder housing and the piston rod and, viewed axially, between the piston and the end face.
Im Betrieb des Hydraulikzylinders bewegen sich der Kolben und die Kolbenstange translatorisch, wobei die Kolbenstange im Zylinderkopf des Zylinders geführt und gelagert werden muss, insbesondere wenn Querkräfte auf die Kolbenstange einwirken. Darüber hinausgehend ist zwischen der Kolbenstange und dem Zylinderkopf eine Dichtung nötig, um die unter Arbeitsdruck stehende Druckkammer gegen die Umgebung abzudichten.When the hydraulic cylinder is in operation, the piston and the piston rod move in a translatory manner, with the piston rod having to be guided and supported in the cylinder head of the cylinder, especially when transverse forces act on the piston rod. In addition, a seal is required between the piston rod and the cylinder head in order to seal off the pressure chamber under working pressure from the environment.
Eine aus der
In der Druckschrift
Wenn der Druck in der ringförmigen Druckkammer zunimmt, ergibt sich eine zunehmende radiale Belastung der Spaltbuchse nach außen. Um eine entsprechende Aufweitung der Spaltbuchse und damit eine Vergrößerung der präzise gefertigten Passung zu vermeiden, muss die Spaltbuchse sehr formstabil sein. Dies lässt sich nur durch Materialien mit großem E-Modul oder durch eine große radiale Ausdehnung beziehungsweise Dicke der Spaltbuchse erreichen.When the pressure in the annular pressure chamber increases, there is an increasing radial load on the split bushing towards the outside. In order to avoid a corresponding expansion of the split bush and thus an enlargement of the precisely manufactured fit, the split bush must be very dimensionally stable. This can only be achieved with materials with a large E-module or with a large radial expansion or thickness of the split bushing.
Dem gegenüber liegt der Erfindung die Aufgabe zu Grunde, einen Hydraulikzylinder mit Kolbenstange zu schaffen, dessen ringförmige Druckkammer mit einer Spaltbuchse abgedichtet ist, wobei der vorrichtungstechnische Aufwand minimiert ist. Es soll dabei ein Dichtungssystem geschaffen werden, das eine nur geringe und druckunabhängige Reibung zwischen der Kolbenstange und den diese führenden und lagernden Bauteilen mit sich bringt.In contrast, the invention is based on the object of creating a hydraulic cylinder with a piston rod, the ring-shaped pressure chamber of which is sealed with a split bushing, the outlay on device technology being minimized. The aim is to create a sealing system that brings about only a low and pressure-independent friction between the piston rod and the components that guide and support it.
Diese Aufgabe wird gelöst durch einen Hydraulikzylinder mit den Merkmalen des Patentanspruchs 1.This object is achieved by a hydraulic cylinder with the features of claim 1.
Der beanspruchte Hydraulikzylinder hat eine Kolbenstange, die von einer ringförmigen Druckkammer umgeben ist, und die in einer Durchgangsausnehmung des Hydraulikzylinders geführt ist. Eine Spaltbuchse bildet durch eine präzise Passung mit der Kolbenstange über eine gewisse axiale Länge eine Spaltdichtung mit der Kolbenstange, Dadurch werden die Funktionen Lagerung der Kolbenstange und Druckabbau des Kammerdrucks in der Spaltdichtung baulich getrennt. Die Spaltbuchse ist mit Radialspiel in den Hydraulikzylinder, insbesondere in das Zylindergehäuse eingesetzt, so dass am Außenumfang der Spaltbuchse ein erster kreiszylindrischer Ringspalt gebildet ist, der mit der Druckkammer fluidisch verbunden ist. Erfindungsgemäß ist am Außenumfang der Spaltbuchse eine Dichtung angeordnet, die einen axialen Abstand zu einer der Druckkammer zugewandten ersten Stirnseite der Spaltbuchse hat und der axiale Abstand der Dichtung von der Stirnseite ist derart gewählt, dass die Spaltbuchse in radialer Richtung druckkraftkompensiert ist. Dadurch kann der Arbeitsdruck der Druckkammer an einem sich von der Druckkammer bis zur Dichtung erstreckendem Abschnitt des Außenumfangs radial nach innen gerichtete Gegenkräfte auf die Spaltbuchse erzeugen, die den in der Spaltdichtung zwischen der Kolbenstange und der Spaltbuchse durch den dortigen Druck an der Spaltbuchse erzeugten und radial nach außen gerichteten Kräften entgegenwirken. Die Position der Dichtung wird dabei in Abhängigkeit von verschiedenen Parametern der Spaltbuchse, zum Beispiel in Abhängigkeit von der Breite, Dicke und E-Modul gewählt. Dann ergeben sich in der Summe keine Radialkräfte an der Spaltbuchse, so dass diese mechanisch optimal entlastet ist. Die mechanisch entlastete Spaltbuchse kann relativ einfach ausgeführt werden. Vorzugsweise ist die Spaltbuchse kreiszylindrisch. Vorzugsweise ist die Dichtung in eine äußere Umfangsnut der Spaltbuchse eingesetzt.The claimed hydraulic cylinder has a piston rod which is surrounded by an annular pressure chamber and which is guided in a through recess of the hydraulic cylinder. A gap bushing forms a gap seal with the piston rod through a precise fit with the piston rod over a certain axial length. This structurally separates the functions of mounting the piston rod and pressure reduction of the chamber pressure in the gap seal. The split bushing is inserted with radial play in the hydraulic cylinder, in particular in the cylinder housing, so that a first circular cylindrical annular gap is formed on the outer circumference of the split bushing and is fluidically connected to the pressure chamber. According to the invention, a seal is arranged on the outer circumference of the split bush, which is at an axial distance from a first end face of the split sleeve facing the pressure chamber, and the axial distance between the seal and the end face is selected such that the split sleeve is compensated for compressive force in the radial direction. As a result, the working pressure of the pressure chamber can generate radially inward opposing forces on the gap sleeve on a section of the outer circumference extending from the pressure chamber to the seal, which counterforces are generated in the gap seal between the piston rod and the gap sleeve due to the pressure there on the gap sleeve and radially counteract outwardly directed forces. The position of the seal is selected as a function of various parameters of the split bushing, for example as a function of the width, thickness and modulus of elasticity. Then there are no total radial forces on the split bush, so that this is mechanically optimally relieved. The mechanically relieved split bushing can be made relatively simple. The split bush is preferably circular-cylindrical. The seal is preferably inserted into an outer circumferential groove of the split bush.
Weitere vorteilhafte Ausgestaltungen der Erfindung sind in den abhängigen Patentansprüchen beschrieben.Further advantageous refinements of the invention are described in the dependent claims.
Vorzugsweise ist zwischen der Kolbenstange und der Durchgangsausnehmung ein zweiter Ringspalt gebildet, dessen radiales Maß kleiner ist, als das radiale Maß des ersten Ringspalts. Dadurch ist die Kolbenstange spielbehaftet in der Durchgangsausnehmung aufgenommen. Sie kann durch Querkräfte entsprechende Abweichungen von der konzentrischen Lage aufweisen und sich erfindungsgemäß an der Durchgangsausnehmung abstützen. Dabei verbleibt am Außenumfang der Spaltbuchse stets ein Rest des ersten Ringsspalts, der mit der Drucckammer verbunden ist, so dass radial kein Kontakt zwischen der Spaltbuchse und dem Teil auftreten kann, in das die Spaltbuchse eingesetzt ist. Üblicherweise ist die Spaltbuchse dabei in das Zylindergehäuse eingesetzt, Insbesondere bleibt bei axialem Abstand der Dichtung von der Stirnseite stets die Druckkraftkompensation der Spaltbuchse erhalten.A second annular gap is preferably formed between the piston rod and the through recess, the radial dimension of which is smaller than the radial dimension of the first annular gap. As a result, the piston rod is received in the through recess with play. It can have corresponding deviations from the concentric position due to transverse forces and, according to the invention, can be supported on the passage recess. A remnant of the first annular gap, which is connected to the pressure chamber, always remains on the outer circumference of the split bushing, so that no radial contact can occur between the split bushing and the part into which the split bushing is inserted. The split bushing is usually inserted into the cylinder housing. In particular, the pressure force compensation of the split bushing is always retained when the seal is at an axial distance from the end face.
Besonders gut kann sich die Dichtung an verschieden breite Ringspalten anpassen, wenn sie einen äußeren Dichtring (z.B. Kolbendichtring) und einen inneren O-Ring hat. Letzterer ist in seinem Querschnitt zusammengedrückt und spannt damit den Dichtring nach außen gegen den Hydraulikzylinder. Dadurch ergibt sich bei der Dichtung eine "Aufgabenteilung" zwischen der Dichtfunktion und der elastischen Kraftbeaufschlagung radial nach außen.The seal can adapt to ring gaps of different widths particularly well if it has an outer sealing ring (e.g. piston sealing ring) and an inner O-ring. The latter is compressed in its cross-section and thus tensions the sealing ring outwards against the hydraulic cylinder. In the case of the seal, this results in a "division of tasks" between the sealing function and the elastic application of force radially outwards.
Falls der Hydraulikzylinder einen Zylinderkopf hat, der an einem zum Beispiel rohrförmigen Zylindergehäuse des Hydraulikzylinders befestigt ist und in dem die Durchgangsausnehmung für die Kolbenstange gebildet ist, wird es besonders bevorzugt, wenn die Spaltbuchse mit einer zweiten Stirnseite an dem Zylinderkopf anliegt. Die zweite Stirnseite kann dabei geschliffen oder mit einer Beschichtung zum Beispiel aus Kunststoff versehen sein, um die Reibung zwischen der Spaltbuchse und dem Zylinderkopf gering zu halten und eine leichte radiale Verschiebbarkeit der Spaltbuchse zu gewährleisten.If the hydraulic cylinder has a cylinder head which is attached to a, for example, tubular cylinder housing of the hydraulic cylinder and in which the through recess for the piston rod is formed, it is particularly preferred if the split bushing rests against the cylinder head with a second end face. The second end face can be ground or provided with a coating, for example made of plastic, in order to keep the friction between the split liner and the cylinder head low and to ensure easy radial displaceability of the split liner.
Dabei kann die Spaltbuchse vorrichtungstechnisch einfach zwischen dem Zylinderkopf und einem radialen Vorsprung oder einer radialen Stufe an der Innenseite des Zylindergehäuses aufgenommen sein.In terms of device technology, the gap bushing can easily be accommodated between the cylinder head and a radial projection or a radial step on the inside of the cylinder housing.
Die erste Stirnseite der Spaltbuchse kann die ringförmige Druckkammer begrenzen.The first end face of the split bushing can delimit the annular pressure chamber.
Ein Arbeitsanschluss der Druckkammer sollte benachbart zum radialen Vorsprung beziehungsweise zur radialen Stufe in die Druckkammer münden, damit der Kolben sich dem Vorsprung beziehungsweise der Stufe maximalen annähern kann und der Arbeitsbereich des erfindungsgemäßen Hydraulikzylinders maximiert ist.A working connection of the pressure chamber should open into the pressure chamber adjacent to the radial projection or the radial step, so that the piston can come as close as possible to the projection or the step and the working range of the hydraulic cylinder according to the invention is maximized.
Alternativ zur direkten Lagerung der Kolbenstange in der Durchgangsausnehmung des Zylinderkopfs kann ein gesondertes Gleitlager für die Kolbenstange in der Durchgangsausnehmung vorgesehen sein.As an alternative to the direct mounting of the piston rod in the through recess of the cylinder head, a separate slide bearing can be provided for the piston rod in the through recess.
Im Folgenden wird anhand der Figuren ein Ausführungsbeispiel eines erfindungsgemäßen Hydraulikzylinders mit Kolbenstange detailliert beschrieben.An exemplary embodiment of a hydraulic cylinder according to the invention with a piston rod is described in detail below with reference to the figures.
-
Figur 1 einen Ausschnitt des Ausführungsbeispiels in einem Längsschnitt undFigure 1 a detail of the embodiment in a longitudinal section and -
Figur 2 einen Ausschnitt derFigur 1 .Figure 2 a section of theFigure 1 .
In
Im Inneren des Zylindergehäuses 1 ist eine ringförmige Druckkammer 6 vorgesehen, die - radial betrachtet - durch das Zylindergehäuse 1 und eine Kolbenstange 8 begrenzt ist, während sie - axial betrachtet - von einer Spaltbuchse 10 und von einem (nicht gezeigten) Kolben begrenzt ist. Bei Beaufschlagung der Druckkammer 6 über einen Arbeitsanschluss 12 mit Druckmittel bewegt sich der Kolben (in
Die Kolbenstange 8 durchdringt eine Durchgangsausnehmung 14 des Zylinderkopfs 2, wobei zwischen der Kolbenstange 8 und der Durchgangsausnehmung 14 etwas Spiel vorgesehen ist. Damit kann sich die Kolbenstange 8 in engen Grenzen in eine exzentrische Position bezogen auf eine Längsachse 16 des Hydraulikzylinders bewegen. Da der Zylinderkopf 2 aus einem Werkstoff mit guten Gleiteigenschaften, zum Beispiel aus einem Sphäroguss, gefertigt ist, sind die Führung und eine Lagerung 18 der Kolbenstange direkt in der Durchgangsausnehmung 14 ausgebildet. In der Lagerung 18 ist über den Umfang der Durchgangsausnehmung eine Spiralnut eingebracht, die in einen aus
Auch wenn die Kolbenstange 8 mit Bezug zur Längsachse 16 eine etwas exzentrische Lage einnimmt, bleiben die Stangendichtung 20 und der Abstreifer 22 in Anlage mit dieser. Wenn die Kolbenstange 8 eine etwas exzentrische Lage zur Längsachse 16 einnimmt, wird dabei die Spaltbuchse 10 von der Kolbenstange 8 mitgenommen. Dies wird ermöglicht, da das Radialspiel an einem Außenumfang 26 der Spaltbuchse 10 größer ist, als das Radialspiel der Kolbenstange 8 in der Durchgangsausnehmung 14.Even if the
Erfindungsgemäß ist die Dichtung der Spaltbuchse 10, die aus der Kolbendichtung 32 und dem O-Ring 34 besteht, am Außenumfang 26 der Spaltbuchse 10 an derjenigen Stelle angeordnet, an der sich der am Außenumfang 26 wirkende Arbeitsdruck p mit dem am Innenumfang wirkenden Arbeitsdrücken p1 in ihren resultierenden Kräften kompensieren. Diese Stelle ist mit dem axialen Abstand 36 gekennzeichnet, der sich auf die erste Stirnseite 38 der Spaltbuchse 10 bezieht, die der Ringkanal 6 zugewandt ist.According to the invention, the seal of the
Bei einem linearen Verlauf des reduzierten Drucks p1 am innenumfang der Spaltbuchse 10 kann der axiale Abstand 36 zum Beispiel der halben Länge der Spaltbuchse 10 entsprechen.Given a linear profile of the reduced pressure p1 on the inner circumference of the
Abweichend vom gezeigten Ausführungsbeispiel kann in der Durchgangsausnehmung 14 ein Gleitlager eingesetzt oder eine Beschichtung zum Beispiel aus Kunststoff aufgebracht sein, um die Kolbenstange 8 besonders reibungsarm zu führen.In contrast to the exemplary embodiment shown, a slide bearing can be inserted in the through
Offenbart ist ein Hydraulikzylinder mit einer Kolbenstange, die von einer ringförmigen Drucckammer umgeben ist, und die in einer Durchgangsausnehmung des Hydraulikzylinders geführt ist. Eine Spaltbuchse bildet über eine bestimmte axiale Länge und eine präzise Passung mit der Kolbenstange eine Spaltdichtung mit der Kolbenstange. Am Außenumfang der Spaltbuchse ist ein erster kreiszylindrischer Ringspalt gebildet, wodurch die Spaltbuchse mit Radialspiel in den Hydraulikzylinder eingesetzt ist. Der Ringspalt ist mit der Druckkammer fluidisch verbunden. Am Außenumfang der Spaltbuchse ist eine Dichtung angeordnet und hat einen axialen Abstand zu einer der Druckkammer zugewendeten ersten Stirnseite der Spaltbuchse. Dadurch kann der Arbeitsdruck der Druckkammer über einem sich von der Druckkammer bis zur Dichtung erstreckendem Abschnitt des Außenumfangs radial nach innen gerichtete Gegenkräfte auf die Spaltbuchse aufbringen, die den in der Spaltdichtung entstehenden radial nach außen gerichteten Kräften entgegenwirken. So wird die Spaltbuchse mechanisch entlastet.A hydraulic cylinder is disclosed with a piston rod which is surrounded by an annular pressure chamber and which is guided in a through recess of the hydraulic cylinder. A split bushing forms a split seal with the piston rod over a certain axial length and a precise fit with the piston rod. A first circular cylindrical annular gap is formed on the outer circumference of the split bush, as a result of which the split bush is inserted into the hydraulic cylinder with radial play. The annular gap is fluidically connected to the pressure chamber. A seal is arranged on the outer circumference of the split bush and is at an axial distance from a first end face of the split bush facing the pressure chamber. As a result, the working pressure of the pressure chamber can apply radially inward opposing forces to the split bushing via a section of the outer circumference extending from the pressure chamber to the seal, which counteracts the radially outward forces arising in the gap seal. This relieves the mechanical strain on the split bush.
Claims (8)
- Hydraulic cylinder with a piston rod (8) which is surrounded by an annular pressure chamber (6), with a split bushing (10) which forms a split seal (24) with the piston rod (8) and which has radial play at its outer circumference (26), as a result of which a first annular gap is formed which is fluidically connected to the pressure chamber (6), wherein a seal is fitted on the split bushing (10), wherein the seal is arranged on the outer circumference (26) of the split bushing (10) and is at an axial distance (36) from a first end side (38) of the split bushing (10), the end side facing the pressure chamber (6), characterized in that the axial distance (36) is selected in such a manner that the split bushing (10) has compensation in the radial direction for a compressive force, and wherein the piston rod (8) is guided in a through-aperture (14) of the hydraulic cylinder, on which through-aperture said piston rod is supported.
- Hydraulic cylinder according to Claim 1, characterized in that a second annular gap, the radial size of which is smaller than the radial size of the first annular gap, is formed between the piston rod (8) and the through-aperture (14).
- Hydraulic cylinder according to either of the preceding claims, characterized in that the seal has an outer sealing ring (32) and an inner O ring (34).
- Hydraulic cylinder according to one of the preceding claims with a cylinder head (2) which is fastened to a cylinder housing (1) of the hydraulic cylinder and in which the through-aperture (14) is formed, characterized in that the split bushing (10) lies with a second end side (40) on the cylinder head (2).
- Hydraulic cylinder according to Claim 4, characterized in that the split bushing (10) is accommodated between the cylinder head (2) and a radial step (28) or a radial projection of the inner side of the hydraulic cylinder.
- Hydraulic cylinder according to one of the preceding claims, characterized in that the first end side (38) of the split bushing (10) delimits the pressure chamber (6).
- Hydraulic cylinder according to Claim 5 or 6 with a working connection (12) of the pressure chamber (6), characterized in that the working connection (12) opens adjacent to the step (28) or to the projection into the pressure chamber (6).
- Hydraulic cylinder according to one of the preceding claims, characterized in that a plain bearing or a coating for guiding the piston rod (8) is provided in the through-aperture (14).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE201310212224 DE102013212224A1 (en) | 2013-06-26 | 2013-06-26 | Hydraulic cylinder with piston rod |
PCT/EP2014/063003 WO2014206873A1 (en) | 2013-06-26 | 2014-06-20 | Hydraulic cylinder having a piston rod |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3014129A1 EP3014129A1 (en) | 2016-05-04 |
EP3014129B1 true EP3014129B1 (en) | 2021-02-24 |
Family
ID=50980292
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP14731955.2A Active EP3014129B1 (en) | 2013-06-26 | 2014-06-20 | Hydraulic cylinder with piston rod |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP3014129B1 (en) |
DE (1) | DE102013212224A1 (en) |
WO (1) | WO2014206873A1 (en) |
Families Citing this family (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102017222552A1 (en) * | 2017-12-13 | 2019-06-13 | Robert Bosch Gmbh | hydraulic cylinders |
DE102018123184A1 (en) * | 2018-09-20 | 2020-03-26 | Liebherr-Components Kirchdorf GmbH | Piston-cylinder unit for a work machine |
CN110848203A (en) * | 2019-11-26 | 2020-02-28 | 衡阳市林肯液压设备有限公司 | Guide sleeve for hydraulic cylinder |
CN111043098A (en) * | 2019-11-29 | 2020-04-21 | 张家港宏昌钢板有限公司 | End cover structure for balance oil cylinder of roughing mill |
CN111980987A (en) * | 2020-09-01 | 2020-11-24 | 杨德华 | Connecting mechanism of hydraulic cylinder guide sleeve |
CN112576570A (en) * | 2020-11-19 | 2021-03-30 | 青岛泽昊汽车配件有限公司 | Bearing air pressure bar |
DE102021119611A1 (en) | 2021-07-28 | 2023-02-02 | Liebherr-Components Kirchdorf GmbH | Pitch cylinder and wind turbine with such a pitch cylinder |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS61152805U (en) * | 1985-03-13 | 1986-09-22 | ||
DE4242213A1 (en) * | 1992-12-15 | 1994-06-16 | Teves Gmbh Alfred | Seal for sealing cylinder and rod or shaft inside it - has first sealing on rod side, and second sealing surface on inside of cylinder |
DE19841830A1 (en) | 1998-09-12 | 2000-04-06 | Haenchen Kg Herbert | Low friction seal |
DE102010033869B4 (en) * | 2010-08-10 | 2018-08-30 | Festo Ag & Co. Kg | Fluid operated linear unit |
-
2013
- 2013-06-26 DE DE201310212224 patent/DE102013212224A1/en not_active Withdrawn
-
2014
- 2014-06-20 WO PCT/EP2014/063003 patent/WO2014206873A1/en active Application Filing
- 2014-06-20 EP EP14731955.2A patent/EP3014129B1/en active Active
Non-Patent Citations (1)
Title |
---|
None * |
Also Published As
Publication number | Publication date |
---|---|
WO2014206873A1 (en) | 2014-12-31 |
EP3014129A1 (en) | 2016-05-04 |
DE102013212224A1 (en) | 2014-12-31 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP3014129B1 (en) | Hydraulic cylinder with piston rod | |
EP0268624B1 (en) | Seal arrangement | |
EP2427359B1 (en) | Rack-and-pinion steering | |
DE102015111175A1 (en) | Hydraulic valve and connecting rod with a hydraulic valve | |
DE10228051B4 (en) | Hydraulically actuated release system for automotive friction clutch | |
WO2009059841A1 (en) | Guide ring for a piston pump, and piston pump | |
WO2017137183A1 (en) | Piston-cylinder unit | |
EP2751460B1 (en) | Seal, and control device having said seal | |
DE102014001192A1 (en) | Clamping device and component with such a clamping device | |
EP3299682B1 (en) | Seal ring and its use | |
EP3149321B1 (en) | Nozzle assembly for a fuel injector, and fuel injector | |
AT519652B1 (en) | Sealing device and hydraulic piston with sealing device | |
DE102014110077B4 (en) | Sealing system and method for its assembly | |
DE29711184U1 (en) | Hydro clamping element | |
DE4126897A1 (en) | Hydraulic clamp for vehicle rear wheel - has housing with clamping sleeve to control motion and cage assembly between sleeve and rod. | |
DE102009011224A1 (en) | Linear-mobile piston for sealingly limiting work chamber in piston borehole of fluid linear drive, has spring units deflecting rings along directions and arranged such that neighboring rings are linked along different directions | |
EP0017787B1 (en) | Sealing for a piston-cylinder arrangement | |
DE102015120011A1 (en) | Actuator with a linearly displaceable actuator | |
EP2748042B1 (en) | Arrangement for sealing a master cylinder on the side of the piston rod | |
DE19634014C2 (en) | Vibration damper for vehicles or a similar piston-cylinder arrangement | |
WO2016074869A1 (en) | Sealing/guiding unit | |
EP3749876B1 (en) | Slave cylinder with piston, designed for wear reduction; actuation device; and coupling system | |
DE102019133667A1 (en) | Device for regulating pressures of a fluid with a valve | |
WO2016012136A1 (en) | High-pressure fuel pump, in particular plug-in pump | |
EP3502524A1 (en) | Sliding seal and assembly with such a seal |
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: 20160126 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
AX | Request for extension of the european patent |
Extension state: BA ME |
|
DAX | Request for extension of the european patent (deleted) | ||
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: EXAMINATION IS IN PROGRESS |
|
17Q | First examination report despatched |
Effective date: 20190628 |
|
RAP1 | Party data changed (applicant data changed or rights of an application transferred) |
Owner name: ROBERT BOSCH GMBH |
|
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: GRANT OF PATENT IS INTENDED |
|
INTG | Intention to grant announced |
Effective date: 20201109 |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: THE PATENT HAS BEEN GRANTED |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM 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: CH Ref legal event code: EP |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R096 Ref document number: 502014015293 Country of ref document: DE |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: REF Ref document number: 1364785 Country of ref document: AT Kind code of ref document: T Effective date: 20210315 |
|
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: LT Ref legal event code: MG9D |
|
REG | Reference to a national code |
Ref country code: NL Ref legal event code: MP Effective date: 20210224 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
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: 20210224 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: 20210624 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: 20210525 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: 20210224 Ref country code: HR 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: 20210224 Ref country code: NO 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: 20210524 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: 20210524 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
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: 20210224 Ref country code: LV 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: 20210224 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: 20210224 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: 20210224 Ref country code: RS 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: 20210224 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
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: 20210624 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SM 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: 20210224 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: 20210224 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: 20210224 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R097 Ref document number: 502014015293 Country of ref document: DE |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
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: 20210224 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: 20210224 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: 20210224 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: 20210224 |
|
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: AL 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: 20210224 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: 20210224 |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: PL |
|
26N | No opposition filed |
Effective date: 20211125 |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20210620 |
|
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: 20210224 |
|
REG | Reference to a national code |
Ref country code: BE Ref legal event code: MM Effective date: 20210630 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LU Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20210620 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LI Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20210630 Ref country code: IE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20210620 Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20210620 Ref country code: CH Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20210630 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
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: 20210624 Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20210630 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: BE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20210630 |
|
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: 20140620 |
|
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 FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20210224 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: IT Payment date: 20230630 Year of fee payment: 10 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20230817 Year of fee payment: 10 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MK 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: 20210224 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: AT Payment date: 20240617 Year of fee payment: 11 |