EP1715194B1 - Hydraulic actuator - Google Patents

Hydraulic actuator Download PDF

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Publication number
EP1715194B1
EP1715194B1 EP05027904.1A EP05027904A EP1715194B1 EP 1715194 B1 EP1715194 B1 EP 1715194B1 EP 05027904 A EP05027904 A EP 05027904A EP 1715194 B1 EP1715194 B1 EP 1715194B1
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EP
European Patent Office
Prior art keywords
seal
rod
cylinder
piston
internal
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EP05027904.1A
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German (de)
French (fr)
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EP1715194A3 (en
EP1715194A2 (en
Inventor
Marcus Dr. Fischer
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Weber Hydraulik GmbH Germany
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Weber Hydraulik GmbH Germany
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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
    • F15B15/1447—Pistons; Piston to piston rod assemblies
    • F15B15/1452—Piston sealings
    • 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 a hydraulic cylinder unit according to the preamble of the main claim.
  • Seals used in generic hydraulic cylinder units are known in a variety of embodiments ( DE 197 17 652 A1 ; US 4,566,703 A . 2,349,170 A ; DE 2 325 000 and US2004 / 0164496 A1 ).
  • cylinder units For various applications, particularly low-friction cylinder units are of interest. These include cylinders for suspension and steering functions, or cylinders with high demands on sensitivity and positioning. Increased friction has a negative effect on the effective force, that is, the useful force of the cylinder, and the theoretical pressure. This leads inter alia to the fact that the cylinder must be designed larger than theoretically necessary in order to provide a sufficient effective force available.
  • the ratio of static friction to sliding friction is also of interest because large differences between the two values can lead to undesirable vibrations or vibrations (so-called stick-slip effect).
  • the invention is therefore based on the object to design a hydraulic cylinder unit according to the preamble of the main claim particularly low friction.
  • the inventively provided rotationally symmetrical rod seal so touches along a circumferentially closed line, hereinafter called inner equator, on its inner seal jacket the outer surface of the piston, and the likewise rotationally symmetrical piston seal also touches along a likewise circumferentially closed line, hereinafter called outer equator, on its seal outer jacket the inner jacket of the cylinder tube.
  • the gap to be converged in the direction of the equator thus has, with decreasing distance from the equator, a preferably continuously smaller free cross-section for the passage of the displaced hydraulic fluid.
  • the shape of that gap-limiting region which deviates from the shape of the shell of a vertical (straight) circular cylinder, not only due to its rotational symmetry in the circumferential direction, but also additionally curved in the axial direction. But it is also a wedge-shaped gap without additional curvature in axial direction possible.
  • the inventive principle uses the hydrodynamic effect of the hydraulic fluid in the converging gap to minimize the frictional forces between the piston seal and the cylinder tube on the one hand, the rod seal and the piston rod on the other hand.
  • the nature of the tread is not the subject of the invention, it must be designed so that they in cooperation of the running surface (inner shell of the cylinder tube or outer shell of the piston rod) with the seal for optimum friction and wear behavior provides.
  • the piston seal comprises two substantially wedge-shaped gaps deviating from the shell of a vertical circular cylinder, of which one gap is open to the cylinder space and the other to the rod-side cylinder space.
  • the gap in the rod seal with respect to its center plane is asymmetrical and open to the piston rod side cylinder chamber so that at least in the extension direction of the piston rod results in the hydrodynamic, the friction-reducing Aufschwimm bin.
  • a total of 5 designated cylinder unit has a cylinder tube 6, on whose inner shell 7, an outer jacket 9 having a piston 8 is guided.
  • a piston rod generally designated 10
  • a rod surface 11 which is extended by a cylinder head, designated as a whole by 12, out of the cylinder unit 5 upon pressurization of the cylinder space 14 formed between the piston 8 and the cylinder bottom 13 with pressurized hydraulic fluid , If the cylinder unit 5 is double-acting, so can the piston rod-side annular space cylinder chamber 15 which is formed by the piston rod 10, the cylinder head 12 and the piston 8, be pressurized, whereby the piston rod 10 is retracted.
  • a total of 16 designated piston seal is provided on the piston 8. Accordingly, between the outer environment of the cylinder unit 5 and the piston rod-side cylinder chamber 15 on the cylinder head 12, a total of 17 designated rod seal provided.
  • the piston seal 16 is in FIG. 2 shown in more detail.
  • the piston 8 in this case has three circumferential, spaced-apart grooves 181, 182 on the outer casing 9 of the piston.
  • the two outer, outwardly open grooves 181 each have a guide ring 19 is inserted.
  • the middle groove 182 the total designated 16 seal is provided, which consists of two parts, namely designed as a sliding and sealing element piston seal 161 and arranged therebelow biasing element 162, for example in the form of an elastomeric ring, which already in the assembled state ensures a certain Grundanpressung of the sliding and sealing element 161 to the cylinder inner circumferential surface 7.
  • the piston seal 161 has a sealing outer jacket 163 which, with respect to the center plane 164 (FIG. FIG. 4 ) of the piston seal 161 symmetrically forming with respect to the cylinder inner shell 7 of the cylinder tube 6 - deviating from the mantle of a Kreiszylinders- two converging column 165 ( FIG. 4 ) is trained.
  • the center plane 164 (FIG. FIG. 4 ) of the piston seal 161 symmetrically forming with respect to the cylinder inner shell 7 of the cylinder tube 6 - deviating from the mantle of a Kreiszylinders- two converging column 165 ( FIG. 4 ) is trained.
  • In the area of the median plane 164 is the highest point and at the same time the longest circumferential, closed contact line, the outer equator 166, the seal outer shell 163 with the inner shell 7 of the cylinder tube 6.
  • FIG. 4 shows this part of the piston 8 of FIG. 2 closer.
  • the rod seal used in the cylinder head 12, denoted overall by 17, is in FIG. 3 shown in more detail.
  • a scraper 20 and in the piston rod side cylinder chamber 15 closest groove a rod guide 21 are provided in the outermost groove.
  • the rod seal 17 is also provided in two parts with a designed as a sliding and sealing element seal 171 and an underlying biasing member 172, which according to the FIG. 2 already discussed element 162 corresponds.
  • the inner sealing jacket 173 of the rod seal 171 is formed asymmetrically with respect to the center plane and has either only a wedge-shaped gap, or two columns with different gap angles and / or their length. In the former case, the gap to the piston rod side cylinder chamber 15 is open.
  • a total of 22 designated additional seal is arranged between the rod seal 171 and the outer periphery of the cylinder unit. Between this and the rod seal 171 serving as a reservoir for the hydraulic fluid recess 23 is arranged in the cylinder head, in the hydraulic fluid, which is towed out during the extension stroke of the piston rod as a lubricating film under the rod seal 171, is collected. This quantity of oil can in turn be dragged back into the rod-side cylinder chamber 15 via the return capacity of the stand seal during the subsequent retraction stroke of the piston with its piston rod.
  • the asymmetric shape of the seal inner wall 173 is provided by which the return conveyance of the previously extracted amount of hydraulic fluid is ultimately ensured.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
  • Sealing Devices (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)

Description

Die Erfindung betrifft eine hydraulische Zylindereinheit nach dem Oberbegriff des Hauptanspruchs.The invention relates to a hydraulic cylinder unit according to the preamble of the main claim.

Bei gattungsgemässen hydraulischen Zylindereinheiten eingesetzte Dichtungen sind in einer Vielzahl von Ausführungeformen bekannt ( DE 197 17 652 A1 ; US 4,566,703 A , 2,349,170 A ; DE 2 325 000 und US2004/0164496 A1 ).Seals used in generic hydraulic cylinder units are known in a variety of embodiments ( DE 197 17 652 A1 ; US 4,566,703 A . 2,349,170 A ; DE 2 325 000 and US2004 / 0164496 A1 ).

Für verschiedene Einsatzzwecke sind besonders reibungsarme Zylindereinheiten von Interesse. Zu diesen gehören unter anderem Zylinder für Federungs- und Lenkfunktionen, oder aber Arbeitszylinder mit hohen Ansprüchen an die Feinfühlig- sowie Positionierbarkeit. Eine erhöhte Reibung wirkt sich in einem schlechten Verhältnis zwischen effektiver Kraft, das heisst Nutzkraft des Zylinders, und der theoretischen Druckkraft aus. Dies führt unter anderem dazu, dass der Zylinder grösser als theoretisch notwendig ausgelegt werden muss, um eine hinreichende Effektivkraft zur Verfügung zu stellen.For various applications, particularly low-friction cylinder units are of interest. These include cylinders for suspension and steering functions, or cylinders with high demands on sensitivity and positioning. Increased friction has a negative effect on the effective force, that is, the useful force of the cylinder, and the theoretical pressure. This leads inter alia to the fact that the cylinder must be designed larger than theoretically necessary in order to provide a sufficient effective force available.

In Federungszylindern wirkt die Reibkraft wie eine zusätzliche Dämpfung. Je grösser jedoch die Grunddämpfung des Zylinder selbst ist, desto geringer ist der Anteil, der effektiv bei der Steuerung beeinflussbar ist. Gerade die Möglichkeit der Beeinflussung einer Dämpfung ist jedoch die Grundlage eines modernen, aktiven Federungs- und Dämpfungssystems.In suspension cylinders, the frictional force acts as an additional cushioning. But the bigger the Basic damping of the cylinder itself, the lower is the proportion that can be influenced effectively in the control. But the possibility of influencing a damping is the basis of a modern, active suspension and damping system.

Neben der betragsmässigen Höhe der Reibung ist das Verhältnis von Haft- zu Gleitreibung ebenfalls von Interesse, weil grosse Unterschiede zwischen den beiden Werten zu unerwünschten Schwingungen beziehungsweise Vibrationen führen können (sogenannter Stick-Slip-Effekt).In addition to the magnitude of the amount of friction, the ratio of static friction to sliding friction is also of interest because large differences between the two values can lead to undesirable vibrations or vibrations (so-called stick-slip effect).

Von Nachteil bei den bekannten hydraulischen Zylindereinheiten sind deren letztlich doch nicht befriedigenden Reibungswerte und die relativ grosse Streuung in der serie.A disadvantage of the known hydraulic cylinder units whose ultimately not satisfactory friction values and the relatively large dispersion in the series.

Der Erfindung liegt deshalb die Aufgabe zugrunde, eine hydraulische Zylindereinheit gemäss dem Oberbegriff des Hauptanspruchs besonders reibungsarm auszugestalten.The invention is therefore based on the object to design a hydraulic cylinder unit according to the preamble of the main claim particularly low friction.

Diese Aufgabe wird erfindungsgemäss durch den Gegenstand des Hauptanspruchs gelöst.This object is achieved according to the invention by the subject of the main claim.

Die erfindungsgemäss vorgesehene rotationssymmetrische Stangendichtung berührt also längs einer umlaufend geschlossenen Linie, nachfolgend innerer Äquator genannt, auf ihrem Dichtungsinnenmantel den Aussenmantel des Kolbens, und die ebenfalls rotationssymmetrisch ausgebildete Kolbendichtung berührt also auch längs einer ebenfalls umlaufend geschlossenen Linie, nachfolgend äusserer Äquator genannt, auf ihrem Dichtungsaussenmantel den Innenmantel des Zylinderrohrs. Der in Richtung auf den Äquator zu konvergierende Spalt weist also mit abnehmenden Abstand von dem Äquator einen vorzugsweise stetig kleiner werdenen freien Querschnitt für den Durchtritt der verdrängten Hydraulikflüssigkeit auf. Hierbei kann die Form jenes den Spalt begrenzenden Bereichs, der von der Form des Mantels eines senkrechten (geraden) Kreiszylinders abweicht, nicht nur infolge seiner Rotationssymmetrie in Umfangsrichtung, sondern zusätzlich auch in axialer Richtung gekrümmt ausgebildet sein. Es ist aber auch ein keilförmig ausgebildeter Spalt ohne zusätzliche Krümmung in axialer Richtung möglich.The inventively provided rotationally symmetrical rod seal so touches along a circumferentially closed line, hereinafter called inner equator, on its inner seal jacket the outer surface of the piston, and the likewise rotationally symmetrical piston seal also touches along a likewise circumferentially closed line, hereinafter called outer equator, on its seal outer jacket the inner jacket of the cylinder tube. The gap to be converged in the direction of the equator thus has, with decreasing distance from the equator, a preferably continuously smaller free cross-section for the passage of the displaced hydraulic fluid. In this case, the shape of that gap-limiting region, which deviates from the shape of the shell of a vertical (straight) circular cylinder, not only due to its rotational symmetry in the circumferential direction, but also additionally curved in the axial direction. But it is also a wedge-shaped gap without additional curvature in axial direction possible.

Das erfindungsgemässe Prinzip nutzt dabei den hydrodynamischen Effekt der Hydraulikflüssigkeit in dem konvergierenden Spalt, um die Reibkräfte zwischen der Kolbendichtung und dem Zylinderrohr einerseits, der Stangendichtung und der Kolbenstange andererseits zu minimieren. Die Beschaffenheit der Lauffläche (Rauhigkeit, Werkstoff, Oberflächenbehandlung) ist zwar nicht Gegenstand der Erfindung, sie muss jedoch so ausgestaltet sein, dass sie im Zusammenwirken der Lauffläche (Innenmantel des Zylinderrohrs oder Aussenmantel der Kolbenstange) mit der Dichtung für ein optimales Reibungs- sowie Verschleissverhalten sorgt.The inventive principle uses the hydrodynamic effect of the hydraulic fluid in the converging gap to minimize the frictional forces between the piston seal and the cylinder tube on the one hand, the rod seal and the piston rod on the other hand. Although the nature of the tread (roughness, material, surface treatment) is not the subject of the invention, it must be designed so that they in cooperation of the running surface (inner shell of the cylinder tube or outer shell of the piston rod) with the seal for optimum friction and wear behavior provides.

Es hat sich herausgestellt, dass sich die Reibkraft beziehungsweise dämpfenden Eigenschaften der hydraulischen Zylindereinheit durch die Verwendung der Kolben- und Stangendichtung beträchtlich reduzieren lassen. Hierdurch bedingt ergeben sich vielfältige Möglichkeiten und Vorteile. So kann die Reduktion der Baugrösse von Zylindern aufgrund der besseren Kraftausnutzung zu vielfältigeren Einsatzmöglichkeiten sowie zu einer Kostenersparnis führen. Ferner führt die Verbesserung der Eigenschaften von Federungszylindern durch reduzierte Grunddämpfung dazu, dass ein grösserer Anteil für die aktive Beeinflussung der Systemdämpfung zur Verfügung steht. Bei Arbeitszylindern kann die Steuerbarkeit sowie Feinfühligkeit beträchtlich verbessert werden. Daneben eröffnen sich neue Anwendungsbereiche für Zylinder, die bisher aufgrund unzureichender Effektivkraft, zu hoher Reib- und damit Störkraft oder zu hoher Dämpfung verschlossen geblieben sind. Als hydraulische Zylindereinheit können auch Gleichgangzylinder dienen.It has been found that the frictional force or damping properties of the hydraulic cylinder unit can be considerably reduced by the use of the piston and rod seal. As a result, there are many possibilities and advantages. Thus, the reduction of the size of cylinders due to the better use of force can lead to more diverse applications and cost savings. Furthermore, the improvement in the properties of suspension cylinders by means of reduced basic damping means that a larger proportion is available for actively influencing the system damping. With working cylinders, the controllability and sensitivity can be considerably improved. In addition, new areas of application for cylinders, previously due to insufficient effective force, too high friction and thus disruptive power or have remained closed to high attenuation. As a hydraulic cylinder unit and synchronous cylinder can serve.

Gemäss der Erfindung weist die Kolbendichtung zwei -von dem Mantel eines senkrechten Kreiszylinders abweichende- im wesentlichen keilförmige Spalte auf, von den der eine Spalt zu dem Zylinderraum und der ander zu dem stangenseitigen Zylinderraum offen ist.According to the invention, the piston seal comprises two substantially wedge-shaped gaps deviating from the shell of a vertical circular cylinder, of which one gap is open to the cylinder space and the other to the rod-side cylinder space.

Erfindungsgemäss ist der Spalt bei der Stangendichtung bezüglich deren Mittelebene asymmetrisch ausgeführt und zu dem kolbenstangenseitigen Zylinderraum hin offen, sodass zumindest in der Ausfahrrichtung der Kolbenstange sich der hydrodynamische, die Reibung verringernde Aufschwimmeffekt ergibt.According to the invention, the gap in the rod seal with respect to its center plane is asymmetrical and open to the piston rod side cylinder chamber so that at least in the extension direction of the piston rod results in the hydrodynamic, the friction-reducing Aufschwimmeffekt.

Weil darüber hinaus zwischen der Stangendichtung und der Umgebung der Zylindereinheit eine Zusatzdichtung angeordnet und zwischen dieser und der Stangendichtung eine als Reservoir für die ausgeschleppte Hydraulikflüssigkeit dienende Aussnehmung in dem Zylinderkopf angeordnet ist, kann dort die erhöht als Schmierfilm ausgetragene Hydraulikflüssigkeit gesammelt werden und auch in Einfahrrichtung der Kolbenstange der hydrodynamische, die Reibung verringernde Aufschwimmeffekt erzeugt werden.Moreover, because an additional seal is disposed between the rod seal and the vicinity of the cylinder unit and disposed between this and the rod seal serving as a reservoir for the towed hydraulic fluid recess in the cylinder head, there can be collected increased as a lubricating film discharged hydraulic fluid and also in the retraction of the Piston rod hydrodynamic, the friction-reducing floating effect are generated.

Weitere zweckmässige Ausgestaltungen und Weiterbildungen der Erfindung sind in den Unteransprüchen gekennzeichnet. Ein Ausführungsbeispiel der Erfindung wird nachfolgend unter Bezugnahme auf die Zeichnung näher erläutert.Further expedient refinements and developments of the invention are characterized in the subclaims. An embodiment of the invention will be explained in more detail with reference to the drawing.

In dieser zeigt:

Figur 1
einen schematischen Querschnitt durch eine Zylindereinheit in teilweise abgebrochener Darstellung;
Figur 2
die Einzelheit II gemäss Figur 1, in grösserem Massstab;
Figur 3
die Einzelheit III gemäss Figur 1, in grösserer Darstellung und
Figur 4
Figur 2 in grösserem Massstab.
In this shows:
FIG. 1
a schematic cross section through a cylinder unit in a partially broken representation;
FIG. 2
the detail II according to FIG. 1 on a larger scale;
FIG. 3
the detail III according to FIG. 1 , in a larger scale and
FIG. 4
FIG. 2 on a larger scale.

Die in Figur 1 insgesamt mit 5 bezeichnete Zylindereinheit weist ein Zylinderrohr 6 auf, an dessen Innenmantel 7 ein einen Aussenmantel 9 aufweisender Kolben 8 geführt ist. An dem Kolben ist eine insgesamt mit 10 bezeichnete Kolbenstange mit einer Stangenoberfläche 11 verbunden, die über einen insgesamt mit 12 bezeichneten Zylinderkopf aus der Zylindereinheit 5 bei Beaufschlagung des zwischen dem Kolben 8 und dem Zylinderboden 13 gebildeten Zylinderraums 14 mit einer unter Druck stehenden Hydraulikflüssigkeit ausgefahren wird. Wenn die Zylindereinheit 5 doppelt wirkend ausgebildet ist, so kann auch der kolbenstangenseitige ringraumförmige Zylinderraum 15, der durch die Kolbenstange 10, den Zylinderkopf 12 und dem Kolben 8 gebildet ist, mit Druck beaufschlagt werden, wodurch die Kolbenstange 10 eingefahren wird.In the FIG. 1 A total of 5 designated cylinder unit has a cylinder tube 6, on whose inner shell 7, an outer jacket 9 having a piston 8 is guided. On the piston, a piston rod, generally designated 10, is connected to a rod surface 11, which is extended by a cylinder head, designated as a whole by 12, out of the cylinder unit 5 upon pressurization of the cylinder space 14 formed between the piston 8 and the cylinder bottom 13 with pressurized hydraulic fluid , If the cylinder unit 5 is double-acting, so can the piston rod-side annular space cylinder chamber 15 which is formed by the piston rod 10, the cylinder head 12 and the piston 8, be pressurized, whereby the piston rod 10 is retracted.

Zwischen dem Zylinderraum 14 und dem kolbenstangenseitigen Zylinderraum 15 ist an dem Kolben 8 eine insgesamt mit 16 bezeichnete Kolbendichtung vorgesehen. Entsprechend ist zwischen der äusseren Umgebung der Zylindereinheit 5 und dem kolbenstangenseitigen Zylinderraum 15 an dem Zylinderkopf 12 eine insgesamt mit 17 bezeichnete Stangendichtung vorgesehen.Between the cylinder chamber 14 and the piston rod-side cylinder chamber 15 is a total of 16 designated piston seal is provided on the piston 8. Accordingly, between the outer environment of the cylinder unit 5 and the piston rod-side cylinder chamber 15 on the cylinder head 12, a total of 17 designated rod seal provided.

Die Kolbendichtung 16 ist in Figur 2 näher dargestellt. Der Kolben 8 weist hierbei drei umlaufende, voneinander beabstandete Nuten 181, 182 an dem Aussenmantel 9 des Kolbens auf. In die beiden äusseren, nach aussen offenen Nuten 181 ist je ein Führungsring 19 eingelegt. In die mittlere Nut 182 ist die insgesamt mit 16 bezeichnete Dichtung vorgesehen, die aus zwei Teilen, nämlich dem als Gleit- und Dichtelement ausgebildeten Kolbendichtung 161 und dem darunter angeordneten Vorspannelement 162, z.B. in Form eines Elastomerrings, angeordnet ist, der bereits im montierten Zustand für eine gewisse Grundanpressung des Gleit- und Dichtelements 161 an die Zylinderinnenmantelfläche 7 sorgt.The piston seal 16 is in FIG. 2 shown in more detail. The piston 8 in this case has three circumferential, spaced-apart grooves 181, 182 on the outer casing 9 of the piston. In the two outer, outwardly open grooves 181 each have a guide ring 19 is inserted. In the middle groove 182, the total designated 16 seal is provided, which consists of two parts, namely designed as a sliding and sealing element piston seal 161 and arranged therebelow biasing element 162, for example in the form of an elastomeric ring, which already in the assembled state ensures a certain Grundanpressung of the sliding and sealing element 161 to the cylinder inner circumferential surface 7.

Die Kolbendichtung 161 weist einen Dichtungsaussenmantel 163 auf, der bezüglich der Mittelebene 164 (Figur 4) der Kolbendichtung 161 symmetrisch unter Bildung bezüglich des Zylinderinnenmantels 7 des Zylinderrrohrs 6 -unter Abweichung von dem Mantel eines Kreiszylinders- zweier konvergierender Spalte 165 (Figur 4) ausgebildet ist. Im Bereich der Mittelebene 164 befindet sich die höchste Stelle und zugleich die längste umlaufende, geschlossene Berührungslinie, der äussere Äquator 166, des Dichtungsaussenmantels 163 mit dem Innenmantel 7 des Zylinderrohrs 6. Die in Richtung auf den äusseren Äuquator 166 zu konvergierenden beiden Spalte 165 weisen also mit abnehmendem Abstand von diesem Äuquator 166 einen stetig kleiner werdenen freien Querschnitt für den Durchtritt der verdrängten Hydraulikflüssigkeit auf. Hierbei ist jener den Spalt 165 begrenzende Bereich, der von der Form des Mantels eines Kreiszylinders abweicht, beim wiedergegebenen Ausführungsbeispiel keilförmig mit Krümmung in axialer Richtung ausgebildet. Durch die keilförmigen Spalte 165 zwischen dem Dichtungsaussenmantel 163 und dem Zylinderinnenmantel 7 des Zylinderrohrs 6 ergibt sich ein hydrodynamischer Effekt dergestalt, dass die Kolbendichtung 161 von der in den keilförmigen Spalt 165 eingeschleppten Hydraulikflüssigkeit über die höchste Stelle, den äusseren Äuquator 166, der insgesamt also ballig ausgebildeten Dichtungsaussenmantel 163 von dem Zylinderinnenmantel 7 des Zylinderrohrs 6 abhebt. Hierdurch werden die mechanischen Reibkräfte der Dichtung erheblich reduziert. Figur 4 zeigt diesen Teil des Kolbens 8 von Figur 2 näher.The piston seal 161 has a sealing outer jacket 163 which, with respect to the center plane 164 (FIG. FIG. 4 ) of the piston seal 161 symmetrically forming with respect to the cylinder inner shell 7 of the cylinder tube 6 - deviating from the mantle of a Kreiszylinders- two converging column 165 ( FIG. 4 ) is trained. In the area of the median plane 164 is the highest point and at the same time the longest circumferential, closed contact line, the outer equator 166, the seal outer shell 163 with the inner shell 7 of the cylinder tube 6. The converging in the direction of the outer Äuquator 166 two column 165 thus have with decreasing distance from this 166 one steadily smaller free cross section for the passage of the displaced hydraulic fluid. In this case, that region which delimits the gap 165 and which deviates from the shape of the jacket of a circular cylinder is wedge-shaped with curvature in the axial direction in the exemplary embodiment shown. Due to the wedge-shaped gap 165 between the seal outer shell 163 and the cylinder inner shell 7 of the cylinder tube 6, a hydrodynamic effect results such that the piston seal 161 of the introduced into the wedge-shaped gap 165 hydraulic fluid on the highest point, the outer Äuquator 166, the total so convex formed Dichtungsaussenmantel 163 of the cylinder inner shell 7 of the cylinder tube 6 lifts. As a result, the mechanical friction forces of the seal are significantly reduced. FIG. 4 shows this part of the piston 8 of FIG. 2 closer.

Die in dem Zylinderkopf 12 eingesetzte, insgesamt mit 17 bezeichnete Stangendichtung ist in Figur 3 näher dargestellt. In voneinander beabstandeten, innenliegenden, umlaufenden Nuten sind in der äussersten Nut ein Abstreifer 20 und in der dem kolbenstangenseitigen Zylinderraum 15 am nächsten liegenden Nut eine Stangenführung 21 vorgesehen. Die Stangendichtung 17 ist ebenfalls zweiteilig mit einer als Gleit- und Dichtelement ausgebildeten Dichtung 171 und einem darunter liegenden Vorspannelement 172 versehen, welches dem gemäss Figur 2 schon diskutierten Element 162 entspricht.The rod seal used in the cylinder head 12, denoted overall by 17, is in FIG. 3 shown in more detail. In spaced, inner, circumferential grooves, a scraper 20 and in the piston rod side cylinder chamber 15 closest groove, a rod guide 21 are provided in the outermost groove. The rod seal 17 is also provided in two parts with a designed as a sliding and sealing element seal 171 and an underlying biasing member 172, which according to the FIG. 2 already discussed element 162 corresponds.

In Abweichung von der Kolbendichtung 161 ist der Dichtungsinnenmantel 173 der Stangendichtung 171 bezüglich der Mittelebene asymmetrisch ausgebildet und weist entweder nur einen keilförmigen Spalt, oder aber zwei Spalte mit unterschiedlichen Spaltwinkeln und/oder ihrer Länge auf. Im erstgenannten Fall ist der Spalt zu dem kolbenstangenseitigen Zylinderraum 15 hin offen.In deviation from the piston seal 161, the inner sealing jacket 173 of the rod seal 171 is formed asymmetrically with respect to the center plane and has either only a wedge-shaped gap, or two columns with different gap angles and / or their length. In the former case, the gap to the piston rod side cylinder chamber 15 is open.

Zwischen der Stangendichtung 171 und der äusseren Umgebung der Zylindereinheit ist eine insgesamt mit 22 bezeichnete Zusatzdichtung angeordnet. Zwischen dieser und der Stangendichtung 171 ist ein als Reservoir für die Hydraulikflüssigkeit dienende Ausnehmung 23 in dem Zylinderkopf angeordnet, in die Hydraulikflüssigkeit, welche während des Ausfahrhubes der Kolbenstange als Schmierfilm unter der Stangendichtung 171 ausgeschleppt wird, gesammelt wird. Diese Oelmenge kann beim anschliessenden Einfahrhub des Kolbens mit seiner Kolbenstange wiederum über das Rückfördervermögen der Standendichtung in den stangenseitigen Zylinderraum 15 zurückgeschleppt werden.Between the rod seal 171 and the outer periphery of the cylinder unit, a total of 22 designated additional seal is arranged. Between this and the rod seal 171 serving as a reservoir for the hydraulic fluid recess 23 is arranged in the cylinder head, in the hydraulic fluid, which is towed out during the extension stroke of the piston rod as a lubricating film under the rod seal 171, is collected. This quantity of oil can in turn be dragged back into the rod-side cylinder chamber 15 via the return capacity of the stand seal during the subsequent retraction stroke of the piston with its piston rod.

Um die Rückförderung durch die Stangendichtung 171 zu begünstigen, ist die asymmetrische Form der Dichtungsinnenwandung 173 vorgesehen, durch die das Rückfördern der zuvor ausgeschleppten Menge an Hydraulikflüssigkeit letztlich sichergestellt wird.In order to promote the return conveyance through the rod seal 171, the asymmetric shape of the seal inner wall 173 is provided by which the return conveyance of the previously extracted amount of hydraulic fluid is ultimately ensured.

Claims (9)

  1. A hydraulic cylinder unit (5) with a cylinder barrel (6) comprising an internal surface (7), with piston (8) comprising an external surface (9) guided within the former, with a piston rod (10) connected to the latter, of which the rod surface (11) is guided in a cylinder head (12) closing off the rod-end cylinder chamber (15), with at least one rod seal (17, 171) sealing off the piston-rod-end cylinder chamber (15) from the surroundings of the cylinder unit (5), by means of a rotationally symmetrical internal seal surface (173), between the rod surface (11) and the cylinder head (12) and arranged within the latter, and with at least one piston seal (16, 161) sealing off the piston-rod-end cylinder chamber (15) and the cylinder chamber (14) formed by the cylinder base (13) and the piston (8), by means of a rotationally symmetrical gasket external lateral-face (162), between the cylinder's internal lateral-face (7) and the external surface (9) of the piston (8) and arranged within the latter, wherein the rod seal (17, 171) comprises on its internal seal surface (173) a shape differing from the surface of a circular cylinder and forms a gap converging with reference to the rod surface (11) towards a closed contact line, of the seal internal surface (173) with the rod surface (11) of the piston rod (10), encircling the region of the midplane as the longest contact line - referred to in the following as the internal equator - wherein the piston seal (16, 161) provides on its external seal surface (163) a shape differing from the surface of a circular cylinder and forms two gaps (165) converging with reference to the internal surface (7) of the cylinder barrel (6) to form a closed contact line, of the external seal surface (163) with the internal surface (7) of the cylinder barrel (6), encircling the region of the mid-plane (164) as the longest contact line - referred to in the following as the external equator (166) - of which the one gap (165) is open towards the cylinder chamber (14) and the other towards the rod-end cylinder chamber (15), and wherein, during the outward, or respectively inward, travel of the piston rod (10), the internal seal surface (173) or respectively the external seal surface (163) is lifted by the hydraulic fluid drawn into the converging gap (165) bringing about a hydro-dynamic buoyancy effect reducing the friction above the equator (165) of the internal surface (7) of the cylinder barrel (6), or the rod surface (11) of the piston rod (10), because of the constantly diminishing free cross-section towards the equator (166) during the passage of the displaced hydraulic fluid, wherein the gap in the case of the rod seal (17, 171) is embodied asymmetrically with reference to the mid-plane and is open towards the piston-rod-end cylinder chamber (15),
    characterised in that
    the piston seal (16, 161) is embodied symmetrically with regard to its mid-plane (164), and
    that a supplementary seal (22) is arranged between the rod seal (17, 171) and the surroundings of the cylinder unit (5), wherein a recess (23) in the cylinder head (12) serving as a reservoir for the hydraulic fluid is arranged between the rod seal (17, 171) and the supplementary seal (22).
  2. The cylinder unit according to claim 1,
    characterised in that,
    in addition to the curvature in the peripheral direction, the rod seal (17, 171) and/or the piston seal (16, 161) is also curved in the axial direction because of its rotati-onal symmetry in that region which provides a shape differing from the surface of a circular cylinder.
  3. The cylinder unit according to claim 1,
    characterised in that,
    without additional curvature in the axial direction in that region which provides a shape differing from the surface of a circular cylinder, the rod seal (17, 171) and/or the piston seal (16, 161) forms a wedge-shaped gap with the lateral-face of a circular cylinder.
  4. The cylinder unit according to any one of claims 1 to 3,
    characterised in that
    the rod seal (17, 171) provides a further gap, that the two gaps are embodied asymmetrically with regard to their mid-plane and that the further gap is open towards the recess (23) in the cylinder head (12) serving as a reservoir for the hydraulic fluid.
  5. The cylinder unit according to any one of claims 1 to 4,
    characterised in that
    the rod seal (17, 171) and/or the piston seal (16, 161) comprises PU or a structurally-stable material.
  6. The cylinder unit according to claim 5,
    characterised in that
    the rod seal (17, 171) and/or the piston seal (16, 161) comprises PTFE, PA, PE or POM.
  7. The cylinder unit according to claim 5 or 6,
    characterised in that
    fillers are added to the rod seal (17, 171) and/or the piston seal (16, 161).
  8. The cylinder unit according to claim 7,
    characterised in that
    the fillers are bronze or graphite.
  9. The cylinder unit according to any one of claims 1 to 8,
    characterised in that
    a pre-tensioning element (162, 172) is arranged under the rod seal (17, 171) and/or under the piston seal (16, 161).
EP05027904.1A 2005-04-20 2005-12-20 Hydraulic actuator Active EP1715194B1 (en)

Applications Claiming Priority (1)

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DE102005018442A DE102005018442A1 (en) 2005-04-20 2005-04-20 Hydraulic cylinder unit

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EP1715194A3 EP1715194A3 (en) 2008-05-21
EP1715194B1 true EP1715194B1 (en) 2014-06-04

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US7607383B2 (en) * 2007-05-01 2009-10-27 Nagel Robert W System for backup rod seal for hydraulic cylinder
DE102009021170A1 (en) * 2009-05-13 2010-12-16 Compart Compressor Technology Gmbh Cylinder and piston rod seal of a linear compressor
CN102782376B (en) * 2010-03-04 2015-09-02 Nok株式会社 Seal arrangement
DE102011119181A1 (en) 2011-11-23 2013-05-23 Robert Bosch Gmbh Cylinders, in particular hydraulic cylinders for the deep sea
US10330187B2 (en) * 2014-04-11 2019-06-25 Eaton Corporation Hydraulic control unit for a limited slip differential
JP2016080115A (en) * 2014-10-21 2016-05-16 株式会社鷺宮製作所 Fluid control valve
US9702382B2 (en) * 2014-12-16 2017-07-11 World Friendship Co., Ltd. Oil hydraulic cylinder and spindle thereof
DE112017000496T5 (en) 2016-02-23 2018-11-15 Eaton Intelligent Power Limited HYDRDAULIC CONTROL UNIT WITH INFEED OPENING
FR3054277B1 (en) 2016-07-19 2018-07-13 Airbus Helicopters RESONATOR, AND AIRCRAFT PROVIDED WITH THIS RESONATOR
US10272891B2 (en) * 2016-07-28 2019-04-30 Kelsey-Hayes Company Compliant torque coupler for a dual acting plunger assembly of a vehicle brake system
EP3290719B1 (en) * 2016-08-31 2019-07-17 Goodrich Actuation Systems SAS Seal arrangement for an actuator
DE102017204810A1 (en) * 2017-03-22 2018-09-27 Robert Bosch Gmbh Fluid cylinder with improved sealing element and manufacturing method therefor
DE102021111383A1 (en) 2021-05-03 2022-11-03 Elringklinger Ag sealing arrangement
CN113494610B (en) * 2021-07-08 2023-06-27 西华大学 Floating ring structure with damping support and mechanical sealing device

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Also Published As

Publication number Publication date
DE102005018442A1 (en) 2006-10-26
EP1715194A3 (en) 2008-05-21
US7762177B2 (en) 2010-07-27
US20060272498A1 (en) 2006-12-07
EP1715194A2 (en) 2006-10-25

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