EP3014129B1 - Hydraulic cylinder with piston rod - Google Patents

Hydraulic cylinder with piston rod Download PDF

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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
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EP
European Patent Office
Prior art keywords
piston rod
hydraulic cylinder
split
pressure chamber
seal
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EP14731955.2A
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German (de)
French (fr)
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EP3014129A1 (en
Inventor
Oliver GERHARD
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Robert Bosch GmbH
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Robert Bosch GmbH
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    • 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.

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  • 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 DE 102010033869A1 bekannte Lineareinheit verfügt über einen Kolben mit einem Kolbenkörper und einer auf dem Kolbenkörper sitzenden starren Gleithülse, wobei zwischen der Gleithülse und dem Kolbenkörper ein gummielastischer Stützring angeordnet ist. Die Gleithülse ist über den Stützring beabstandet mit radialem Spiel an dem Kolbenkörper montiert. Auf dieser Weise kann die Gleithülse in Verbindung mit dem Stützring bezügliche des Kolbenkörpers verkippen, wobei der Stützring elastisch reversibel verformt wird. Die nachgiebige Aufhängung der Gleithülse bewirkt eine selbsttätige Anpassung an toleranzbedinge Lageabweichungen zwischen einem Gehäuse und dem Kolbenkörper.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.

In der Druckschrift EP 1 110 017 B1 ist ein derartiger Hydraulikzylinder mit einem Zylinderkopf gezeigt, wobei der Zylinderkopf von der Kolbenstange durchdrungen ist. Zur Abdichtung der ringförmigen Druckkammer ist eine als formstabiler Dichtring bezeichnete Spaltbuchse, die mit der Kolbenstange eine Spaltdichtung bildet, spielbehaftet in eine spezielle Führungsbuchse eingesetzt. Die Spaltbuchse hat zur Erfüllung der Dichtfunktion eine gewisse axiale Ausdehnung und eine präzise gefertigte Passung mit der Kolbenstange. Zur Dichtung des Spalts zwischen der Spaltbuchse und der Führungsbuchse, der sich durch das Spiel ergibt, ist eine weitere Dichtung vorgesehen, die in eine Stirnseite der Spaltbuchse eingesetzt ist und an einer radialen Stufe der Führungsbuchse anliegt.In the pamphlet EP 1 110 017 B1 Such a hydraulic cylinder is shown with a cylinder head, the cylinder head being penetrated by the piston rod. To seal the ring-shaped pressure chamber, a gap bushing called a dimensionally stable sealing ring, which forms a gap seal with the piston rod, is inserted into a special guide bushing with play. To fulfill the sealing function, the split bushing has a certain axial extension and a precisely manufactured fit with the piston rod. To seal the gap between the split bushing and the guide bush, which results from the play, a further seal is provided which is inserted into an end face of the split bush and rests on a radial step of the guide bush.

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.

Es zeigenShow it

  • Figur 1 einen Ausschnitt des Ausführungsbeispiels in einem Längsschnitt und Figure 1 a detail of the embodiment in a longitudinal section and
  • Figur 2 einen Ausschnitt der Figur 1. Figure 2 a section of the Figure 1 .

In Figur 1 erkennbar ist ein Abschnitt eines rohrförmigen Zylindergehäuses 1 des erfindungsgemäßen Hydraulikzylinders. Stirnseitig am Zylindergehäuse 1 ist ein Zylinderkopf 2 befestigt, dessen Radialbund 4 derart in das Zylindergehäuse 1 hineinragt, dass die beiden Teile 1 und 2 zentriert sind.In Figure 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.

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 Figur 1) nach rechts und nimmt dabei die daran befestigte Kolbenstange 8 mit Die Kolbenstange fährt ein. Vom Zylinderkopf 2 aus gesehen jenseits des Kolbens befindet sich eine nicht näher dargestellte zweite Druckkammer. Wenn dieser Druckmittel zugeführt wird, fährt die Kolbenstange aus.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). 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.

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 Figur 1 ersichtlichen, jedoch nicht näher bezeichneten Leckageanschluss am Zylinderkopf 2 mündet. Durch das durch die Spiralnut strömende Leckageöl wird die Lagerung gespült und dadurch auch gekühlt. Mit Bezug zur Druckkammer 6 außen ist am Zylinderkopf 2 weiterhin ein druckentlastetes Dichtungspaket vorgesehen, das in den Zylinderkopf 2 eingesetzt ist und an der Kolbenstange 8 anliegt. Genauer gesagt handelt es sich um eine Stangendichtung 20, die an der Kolbenstange 8 anliegt und die über einen O-Ring in Richtung zur Kolbenstange 8 gespannt ist. Weiterhin ist ein an der Kolbenstange 8 anliegender Abstreifer 22 in den Zylinderkopf 2 eingesetzt.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. Since 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. In the bearing 18, 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. With reference to the pressure chamber 6 on the outside, 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.

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 piston rod 8 assumes a somewhat eccentric position with respect to the longitudinal axis 16, the rod seal 20 and the wiper 22 remain in contact therewith. When the piston rod 8 assumes a somewhat eccentric position with respect to the longitudinal axis 16, the split bush 10 is carried along by the piston rod 8. This is made possible because the radial play on an outer circumference 26 of the split bush 10 is greater than the radial play of the piston rod 8 in the through recess 14.

Figur 2 zeigt einen vergrößerten Ausschnitt der Figur 1. Die Spaltbuchse 10 bildet durch ihre passgenaue Anlage mit der Kolbenstange 8 eine Spaltdichtung 24. Am innenumfang sind in der Spaltbuchse 10 über deren gesamte Länge mehrere umlaufende und axial beabstandete Nuten eingebracht, um einen Druckausgleich über den Innenumfang zu gewährleisten. Am Außenumfang 26 der Spaltbuchse 10 verbleibt auch bei maximaler Lageabweichung der Kolbenstange 8 von der Längsachse 16 stets ein gewisser Abstand zum Zylindergehäuse 1 des Hydraulikzylinders. Da die Spaltbuchse 10 auch mit etwas Axialspiel zwischen dem Radialbund 4 des Zylinderkopfs 2 und eine radiale Stufe 28 des Zylindergehäuses 1 aufgenommen ist, verbleibt auch ein Spalt 30 zwischen einer ersten Stirnseite 38 der Spaltbuchse 10 und der Stufe 28. Somit dringt im Betrieb des erfindungsgemäßen Hydraulikzylinders stets unter Arbeitsdruck p stehendes Druckmittel aus der Druckkammer 6 über den Spalt 30 in den Ringspalt am Außenumfang 26 der Spaltbuchse 10 ein. Dieser Effekt ist in seiner axialen Ausdehnung begrenzt durch eine Kolbendichtung 32, die zusammen mit einem O-Ring 34 in eine Nut am Außenumfang 26 der Spaltbuchse 10 eingesetzt ist. Der O-Ring 34 spannt die Kolbendichtung 32 radial nach außen gegen das Zylindergehäuse 1 des erfindungsgemäßen Hydraulikzylinders vor. Dabei sind deren Elastizitäten derart ausgelegt, dass die Kolbendichtung 32 auch dann in Anlage mit dem Zylindergehäuse 1 bleibt, wenn die Kolbenstange 8 maximal exzentrisch beziehungsweise gekippt gegenüber der Längsachse 16 (vgl. Figur 1) ist. Somit kann am Außenumfang 26 der Spaltbuchse 10 der Arbeitsdruck p über den axialen Abstand 36 stets auf die Spaltbuchse 10 einwirken, während der Arbeitsdruck p über die Spaltdichtung 24 auch am Innenumfang der Spaltbuchse wirkt, allerdings von der ersten Stirnseite 38 über die gesamte Länge der Spaltbuchse 10 zu einer zweiten Stirnseite 40 abnehmend. Dadurch ergeben sich am Innenumfang der Spaltbuchse 10 im Idealfall linear abnehmende reduzierte Arbeitsdrücke p1. 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. On the outer circumference 26 of the split bushing 10, a certain distance from the cylinder housing 1 of the hydraulic cylinder always remains, even with the maximum positional deviation of the piston rod 8 from the longitudinal axis 16. Since the split bushing 10 is also received with some axial play between the radial collar 4 of the cylinder head 2 and a radial step 28 of the cylinder housing 1, 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. Their elasticities are designed in such a way that the piston seal 32 remains in contact with the cylinder housing 1 even when the piston rod 8 is maximally eccentric or tilted relative to the longitudinal axis 16 (cf. Figure 1 ) is. Thus, on the outer circumference 26 of the split sleeve 10, the working pressure p can always act on the split sleeve 10 via the axial distance 36, while the working pressure p also acts on the inner circumference of the split sleeve via the gap seal 24, but from the first end face 38 over the entire length of the split sleeve 10 decreasing to a second end face 40. In the ideal case, this results in linearly decreasing reduced working pressures p1 on the inner circumference of the split bushing 10.

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 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. These 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.

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 split bush 10, the axial distance 36 can correspond to half the length of the split bush 10, for example.

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 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.

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)

  1. 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.
  2. 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).
  3. 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).
  4. 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).
  5. 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.
  6. 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).
  7. 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).
  8. 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).
EP14731955.2A 2013-06-26 2014-06-20 Hydraulic cylinder with piston rod Active EP3014129B1 (en)

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

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EP3014129A1 EP3014129A1 (en) 2016-05-04
EP3014129B1 true EP3014129B1 (en) 2021-02-24

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EP14731955.2A Active EP3014129B1 (en) 2013-06-26 2014-06-20 Hydraulic cylinder with piston rod

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WO (1) WO2014206873A1 (en)

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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

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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

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DE102013212224A1 (en) 2014-12-31
WO2014206873A1 (en) 2014-12-31

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