EP1342922B1 - Pressure accumulator - Google Patents

Pressure accumulator Download PDF

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Publication number
EP1342922B1
EP1342922B1 EP03001475A EP03001475A EP1342922B1 EP 1342922 B1 EP1342922 B1 EP 1342922B1 EP 03001475 A EP03001475 A EP 03001475A EP 03001475 A EP03001475 A EP 03001475A EP 1342922 B1 EP1342922 B1 EP 1342922B1
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EP
European Patent Office
Prior art keywords
piston
pressure
main piston
main
sealing medium
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP03001475A
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German (de)
French (fr)
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EP1342922A3 (en
EP1342922A2 (en
Inventor
Helmfried Kany
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Hydac Technology GmbH
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Hydac Technology GmbH
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Publication date
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Publication of EP1342922A2 publication Critical patent/EP1342922A2/en
Publication of EP1342922A3 publication Critical patent/EP1342922A3/en
Application granted granted Critical
Publication of EP1342922B1 publication Critical patent/EP1342922B1/en
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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
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/04—Accumulators
    • F15B1/08—Accumulators using a gas cushion; Gas charging devices; Indicators or floats therefor
    • F15B1/24—Accumulators using a gas cushion; Gas charging devices; Indicators or floats therefor with rigid separating means, e.g. pistons
    • 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
    • F15B2201/00—Accumulators
    • F15B2201/20—Accumulator cushioning means
    • F15B2201/205—Accumulator cushioning means using gas
    • 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
    • F15B2201/00—Accumulators
    • F15B2201/20—Accumulator cushioning means
    • F15B2201/21—Accumulator cushioning means using springs
    • 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
    • F15B2201/00—Accumulators
    • F15B2201/30—Accumulator separating means
    • F15B2201/31—Accumulator separating means having rigid separating means, e.g. pistons
    • F15B2201/312—Sealings therefor, e.g. piston rings
    • 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
    • F15B2201/00—Accumulators
    • F15B2201/30—Accumulator separating means
    • F15B2201/32—Accumulator separating means having multiple separating means, e.g. with an auxiliary piston sliding within a main piston, multiple membranes or combinations thereof
    • 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
    • F15B2201/00—Accumulators
    • F15B2201/40—Constructional details of accumulators not otherwise provided for
    • F15B2201/41—Liquid ports
    • F15B2201/411—Liquid ports having valve means
    • 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
    • F15B2201/00—Accumulators
    • F15B2201/40—Constructional details of accumulators not otherwise provided for
    • F15B2201/41—Liquid ports
    • F15B2201/413—Liquid ports having multiple liquid ports
    • 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
    • F15B2201/00—Accumulators
    • F15B2201/40—Constructional details of accumulators not otherwise provided for
    • F15B2201/415—Gas ports
    • F15B2201/4155—Gas ports having valve means

Definitions

  • the invention relates to a pressure accumulator with a longitudinally displaceable within a storage housing, from main piston and relative to this movable auxiliary piston piston assembly which sealingly separates a fluid side of the memory from its gas side via a sealing device, which latter a release agent with depth filtration properties, other sealing elements and has a chamber adjacent to the inner wall of the storage housing for a flowable sealing medium, which is biased by the auxiliary piston, which is acted upon for a volume of the chamber reducing relative movement with the pressure of the gas side and the force of an energy accumulator.
  • a pressure accumulator is known with a cylinder tube as a storage enclosure, being as a separating member between a working gas located on one side and the located on the opposite side of the storage housing working fluid, preferably in the form of hydraulic oil, two pistons are longitudinally displaceably guided.
  • the one piston in the manner of a main piston has an inner bore and the other second piston in the manner of an auxiliary piston with a diameter corresponding to the diameter of this inner bore part in the same feasible and with another part on the cylinder wall of the storage housing.
  • a sealing medium which has a much higher viscosity than the working medium and preferably consists of fat.
  • the sealing medium enclosed between the double piston arrangement is biased in order to achieve such an increased seal from the gas to the fluid side of the pressure accumulator.
  • the known accumulator solution builds large in the axial direction, because the two pistons must have a greater length so that they do not tilt in the cylinder tube and od an additional guidance by a piston rod. Like. Is not provided.
  • An additionally formed on the inner wall of the storage enclosure pressure pad of a flowable sealing medium reduces the risk of gas losses, especially during downtime, where there is no operating pressure on the fluid side.
  • the known solution comprises a main and an auxiliary piston, which are arranged in the storage housing at an axial distance from each other, so that a gap in the form of an adjacent to the inner wall of the storage chamber chamber is formed, which is filled with a sealing medium.
  • An attached to the auxiliary piston connecting rod passes through the main piston and is guided in this displaceable.
  • a clamped between the main piston and an end stop of the connecting rod spring serves as a force storage, the auxiliary piston and the main piston to reduce the volume of the space located between them seeks to approach each other.
  • the structure of the piston assembly of separate pistons with guide of the auxiliary piston on a displaceable in the main piston connecting rod on the one hand represents a complex construction and is on the other hand with regard to the reliability little satisfactory.
  • the reliability is at risk because of the close fit of the leadership of the connecting rod of the separate piston even slight deformations can lead to jamming.
  • the movable with the main piston along the inner wall of the storage housing auxiliary piston is subject to the same Verschl constitubeiastung as the main piston.
  • the formation of the piston assembly with two separate piston with connecting rod guide a construction that is neither inexpensive to produce nor easy to install.
  • the known accumulator solution has no release agent with depth filtration property and the rest of the auxiliary piston is held in the main piston exclusively by a snap ring, which reduces the sealing effect accordingly, to which also contributes that both the guide for the auxiliary piston in the main piston and the auxiliary piston itself the fluid side facing and thus have to seal a high fluid pressure during storage operation.
  • the invention has the object to provide a pressure accumulator, which, although it is simple and inexpensive to produce, has improved performance, especially long-term behavior, even under very severe conditions.
  • this object is achieved in that the auxiliary piston is fully integrated in an open to the gas side guide of the main piston and that in this means of the auxiliary piston, a space can be enclosed, which forms part of the flowable sealing medium receiving chamber ,
  • auxiliary piston within the main piston allows a particularly cost-effective production and easy installation. Problems with fits, as they occur with separate piston and their leadership via a connecting rod are avoided.
  • provided for guiding the auxiliary piston within the main piston results in a special robustness against mechanical loads, so that the pressure accumulator according to the invention for special applications, for example for defense applications, is particularly suitable, for example for use in battle tanks.
  • the release agent with the depth filtration property which forms part of the sealing device, arranged on the piston assembly to the fluid side last, so that from the fluid side to the other sealing elements towards migrating liquid, for example, contaminated by metal particles hydraulic fluid undergoes depth filtering, so that a Danger to the axially subsequent, further sealing elements is avoided.
  • a release agent is preferably a felt, in particular in the form of at least one felt ring, use.
  • Felt here in the context of the invention for a compacted scrim with random arrangement of fibers, especially natural and man-made fibers. It can be used both needle felting and felting, in which the initial lap similar fiber layer is entangled by means of felted needles barbs or are solidified in the fiber webs by pressure and movement under heat and moisture.
  • woven felt materials can be used made of woven, gewalkten and matted fabrics.
  • the use of felt materials of relatively high density, such as materials with density values in the range of 0.36 g / cm 3 , corresponding to hardness group F 2 according to DIN 61200, has proven favorable. It is understood that, depending on the nature, type of contamination and degree of liquid side fluid any suitable filtration materials other density and / or hardness groups can be selected.
  • Fig. 1 shows the fluid-side portion of the storage case of the embodiment of the accumulator according to the invention, with a cylinder tube 1 and the fluid-side conclusion forming cylinder cover 3.
  • the latter is fixed at the end of the cylinder tube 1 by means of a split retaining ring 5, which in turn is secured by an annular disc 7 , which is bolted to the cylinder cover 3 by means of three screws 9 of which in Fig. 1, only one is visible.
  • the cylinder cover 3 has a bore 12 concentric with the cylinder axis 11 for the connection of a fluid line.
  • the gas-side end (not shown) of the cylinder tube 3 is closed by a cylinder cover, which has corresponding fittings, such as a gas filling valve, in the manner customary for such pressure accumulators.
  • a gasket is also provided on the cylinder cover, not shown, on the gas side end of the cylinder tube 1.
  • a piston assembly along the axis 11 is guided longitudinally displaceable.
  • This piston assembly which is shown separately in Fig. 2 and designated as a whole by 15, is formed of a main piston 17 and an auxiliary piston 19, which latter is movably guided in a guide 21 which extends concentrically in the main piston 17 to the axis 11 and to the right in Fig. 1 located gas side 23 is open.
  • the piston assembly 15 formed from the main piston 17 and auxiliary piston 19 separates within the cylinder tube 1, the gas side designated by 23 of the in Fig. 1 with 25 designated fluid side, which is in communication with the fluid port 12.
  • the guide 21 of the main piston 17 is limited by an annular body 27 which is axially secured by a Segerring 29.
  • the auxiliary piston 19 located in the guide 21 of the main piston 17 is secured against the exit from the guide 21 by contact with the annular body 27.
  • Fig. 1 shows the piston position of the auxiliary piston 19, in which this rests on the annular body 27.
  • the auxiliary piston 19 is designed trough-shaped, wherein in the concentric with the longitudinal axis 11 interior 31 a helical compression spring 33 is seated, which is supported on the one hand at the bottom of the interior 31 and on the other hand on the annular body 27.
  • the reduction the volume of the space 35 corresponds, which is located between the auxiliary piston 19 and the closed end of the guide 21 in the main piston 17.
  • the space 35 which is explained in more detail below, is provided for receiving a flowable sealing medium forms part of a chamber which adjoins the inner wall of the cylinder tube 1 to form a pressure pad applied to this inner wall of the sealing medium.
  • the space 35 is connected via a plurality of connecting channels 37 with a recess 39 incorporated in the circumference of the main piston 17, which extends annularly over the entire circumference of the main piston 17.
  • the axis 41 of the connecting channels 37 extends obliquely to the main longitudinal axis 11.
  • the bottom of the recess 39 has over its axial extent to a different depth. More specifically, the bottom of the recess 39 has contiguous planar and concave bottom surface portions 38 and 40, respectively, with the junction of the connection channels 37 located in the recess 39 in a flat bottom surface portion 38 whose plane is perpendicular to the axis 41 of the connection channels 37 ,
  • the sealing means effecting the separation between the gas side 23 and the fluid side 35 is entirely formed on the circumference of the main piston 17.
  • the sealing device has a release agent with depth filtration properties, namely in the embodiment a felt ring 43 which sits in the region of the end of the inner guide 21 forming piston crown 45 in an annular groove of the main piston 17.
  • a piston seal 47 of the type commonly used in pressure accumulators is provided, for example, an elastomeric seal.
  • Axially further offset to the gas side 23 is located after the recess 39 a further piston seal 47.
  • a piston guide rail 49 is provided at the gas-side end region of the main piston 17.
  • a filling channel 51 Centrally located in the piston head 45 is a filling channel 51 for introducing the sealing medium into the space 35, which forms the chamber for the voltage applied to the inner wall of the cylinder tube 1 pressure pad of the sealing medium via the connecting channels 37 together with the recess 39.
  • a check valve 53 In the filling channel 51 is a check valve 53.
  • a closable vent hole 55 is provided in the piston head 45.
  • the auxiliary piston 19 is sealed relative to the guide 21 in the main piston 17 by means of a sealing ring 57.
  • a sealing element of simple design can be used here, because the seal to be formed is not exposed to great loads during operation, especially since during operation virtually no displacement movement of the auxiliary piston 19 takes place.
  • Fig. 2 shows the piston assembly 15 in a relaxed state, the auxiliary piston 19 is displaced by the force of the compression spring 33 until it rests against the piston head 45.
  • the vent hole 55 is opened and the piston assembly 15 is inserted into the cylinder tube 1 with the cylinder cover 3 removed.
  • the intended for use sealing medium is now filled in the space 35 until the state of the vent is reached.
  • the vent hole 55 is now closed and built by further supply of the sealing medium via the check valve 53, a pressure in the space 35 until the auxiliary piston moves against the force of the spring 33 against the annular body 27, such as this is shown in Fig. 1.
  • the piston seals 47 are both biased outward with a small differential pressure, so that ingress of dirt from the outside is not possible.
  • the piston seals 47 are lubricated by the sealing medium, which is preferably a fluid used on the fluid or oil side.
  • the sealing medium is preferably a fluid used on the fluid or oil side.
  • the sealing medium virtually all flowable substances can be used, including gas.
  • the use of the hydraulic fluid present on the fluid side is advantageous, because thus no foreign oils are present in the system.
  • a gas-biasing pressure is built up, for example, N 2 is entered, wherein in a practical application, for example, a biasing pressure of 60 bar can be provided, then the pressure in the space 35 and in the recess 39 increases in this example to a pressure value of 60 bar plus the pressure generated by the force of the spring 33 by means of the auxiliary piston 19, so in the example mentioned to about 65 bar.
  • the pressure in the recess 39 is higher than on the gas side 23, no migration of Gas on the gas side closest to the gasket 23 47 possible.
  • the pressure in the storage enclosure so loaded the fluid side 25 with the fluid pressure increases in a corresponding manner, the pressure in the storage enclosure, so that the pressure on the gas side 23 increases accordingly, as thought game assumed, for example, to 150 bar.
  • This increases the Pressure in the space containing the sealing medium 35 and in the recess 39 to a pressure value corresponding to the gas pressure on the gas side 23 plus the pressure generated by the spring 33 on the auxiliary piston 19 pressure, ie in the example mentioned to about 155 bar
  • the piston seals 47 applied differential pressure also only about 5 bar, ie In operation, the piston seals 47 are loaded exclusively with the mentioned, low differential pressure.
  • the pressure accumulator according to the invention is in particular protected against gas losses at standstill times, ie in the absence of fluid pressure, because the prevailing in the space 35 and the recess 39 pressure of the sealing medium is always higher than the pressure on the gas side 23rd

Abstract

The pressure reservoir has a housing (1) with a main piston (17) and a sub piston (15) which separates the liquid side and the gas side of the piston using seals. There is a separator with a high degree of filtering and an auxiliary piston (19) pressurizes the seal fluid. The auxiliary piston is fully integrated into a gas side open guide (21) of the main piston.

Description

Die Erfindung bezieht sich auf einen Druckspeicher mit einer innerhalb eines Speichergehäuses längs verfahrbahren, aus Hauptkolben und relativ zu diesem bewegbarem Hilfskolben gebildeten Kolbenanordnung, die eine Fluidseite des Speichers von seiner Gasseite über eine Dichteinrichtung abdichtend trennt, welch letztere ein Trennmittel mit Tiefenfiltrationseigenschaften, weitere Dichtelemente sowie eine an die Innenwand des Speichergehäuses angrenzende Kammer für ein strömungsfähiges Dichtmedium aufweist, das durch den Hilfskolben vorspannbar ist, der für eine das Volumen der Kammer verkleinernde Relativbewegung mit dem Druck der Gasseite und der Kraft eines Kraftspeichers beaufschlagt ist.The invention relates to a pressure accumulator with a longitudinally displaceable within a storage housing, from main piston and relative to this movable auxiliary piston piston assembly which sealingly separates a fluid side of the memory from its gas side via a sealing device, which latter a release agent with depth filtration properties, other sealing elements and has a chamber adjacent to the inner wall of the storage housing for a flowable sealing medium, which is biased by the auxiliary piston, which is acted upon for a volume of the chamber reducing relative movement with the pressure of the gas side and the force of an energy accumulator.

Durch die CH 591 020 A5 ist ein Druckspeicher bekannt mit einem Zylinderrohr als Speichergehäuse, wobei als Trennorgan zwischen einem auf der einen Seite befindlichen Arbeitsgas und dem auf der gegenüberliegenden Seite des Speichergehäuses befindlichen Arbeitsmedium, vorzugsweise in Form von Hydrauliköl, zwei Kolben längsverschiebbar geführt sind. Der eine Kolben in der Art eines Hauptkolbens besitzt eine Innenbohrung und der weitere zweite Kolben in der Art eines Hilfskolbens ist mit einem im Durchmesser dem Durchmesser dieser Innenbohrung entsprechenden Teil in derselben führbar und mit einem anderen Teil an der Zylinderwand des Speichergehäuses. Zwischen den beiden Kolben befindet sich ein Dichtmedium, das eine wesentlich höhere Viskosität aufweist als das Arbeitsmedium und vorzugsweise aus Fett besteht. In Abhängigkeit vom Befüllungs- und Betriebszustand des bekannten Druckspeichers wird das Dichtmedium eingeschlossen zwischen der Doppelkolbenanordnung vorgespannt, um dergestalt eine erhöhte Abdichtung von der Gas- zur Fluidseite des Druckspeichers zu erreichen. Es hat sich jedoch gezeigt, dass insbesondere bei harten Einsatzbedingungen, hoher Verschmutzungsgrad, hohe Beschleunigungskräfte, tiefe Temperaturen etc., die dahingehende Dichtanordnung nicht geeignet ist, um diesen Anforderungen gerecht zu werden. Darüber hinaus baut die bekannte Druckspeicherlösung in axialer Richtung groß auf, denn die beiden Kolben müssen eine größere Länge haben, damit sie sich im Zylinderrohr nicht verkanten und eine zusätzliche Führung durch eine Kolbenstange od. dgl. ist nicht vorgesehen.By the CH 591 020 A5 a pressure accumulator is known with a cylinder tube as a storage enclosure, being as a separating member between a working gas located on one side and the located on the opposite side of the storage housing working fluid, preferably in the form of hydraulic oil, two pistons are longitudinally displaceably guided. The one piston in the manner of a main piston has an inner bore and the other second piston in the manner of an auxiliary piston with a diameter corresponding to the diameter of this inner bore part in the same feasible and with another part on the cylinder wall of the storage housing. Between the two pistons there is a sealing medium, which has a much higher viscosity than the working medium and preferably consists of fat. Depending on the filling and operating state of the known pressure accumulator, the sealing medium enclosed between the double piston arrangement is biased in order to achieve such an increased seal from the gas to the fluid side of the pressure accumulator. However, it has been shown that, especially in harsh operating conditions, high degree of contamination, high acceleration forces, low temperatures, etc., the pertinent sealing arrangement is not suitable to meet these requirements. In addition, the known accumulator solution builds large in the axial direction, because the two pistons must have a greater length so that they do not tilt in the cylinder tube and od an additional guidance by a piston rod. Like. Is not provided.

Ein Druckspeicher dieser Art ist bereits bekannt, siehe DE 197 40 150 A1. Für den Einsatz derartiger Druckspeicher, auch Kolbenspeicher genannt, sind an die Funktionstüchtigkeit hohe Anforderungen zu stellen, und zwar über weite Temperaturbereiche, beispielsweise zwischen minus 40°C bis plus 150°C. Um ein zufriedenstellendes Langzeitverhalten derartiger Speicher zu erreichen, muß besonderes Augenmerk auf die sorgfältige Ausbildung der Dichteinrichtung gelegt werden, um ein Entweichen von Gas zur Fluid- oder Ölseite zu vermeiden, wenn auf der Fluidseite kein Druck ansteht. In Verwendungsbereichen, wo auf der Fluidseite eine Verschmutzung entsteht, beispielsweise in Form von Metallpartikeln, wie es bei Getriebekonstruktionen grundsätzlich der Fall ist, muß der Gefahr entgegengewirkt werden, dass Dichtungen der Dichteinrichtung, insbesondere Elastomerdichtungen, durch Verschmutzungspartikel beschädigt oder gar zerstört werden. Durch der Dichteinrichtung zugeordnete Trennmittel mit Tiefenfiltrationseigenschaften soll dieser Gefahr begegnet werden. Ein an der Innenwand des Speichergehäuses zusätzlich ausgebildetes Druckpolster eines strömungsfähigen Dichtmediums verringert die Gefahr von Gasverlusten, insbesondere auch bei Stillstandszeiten, wo auf der Fluidseite kein Betriebsdruck herrscht.An accumulator of this type is already known, see DE 197 40 150 A1. For the use of such pressure accumulator, also called piston accumulator, high demands are placed on the functionality, and indeed over wide temperature ranges, for example between minus 40 ° C to plus 150 ° C. In order to achieve a satisfactory long-term performance of such reservoirs, special attention must be given to the careful design of the sealing device in order to avoid the escape of gas to the fluid or oil side when there is no pressure on the fluid side. In areas of use where contamination occurs on the fluid side, for example in the form of metal particles, as is generally the case in gearbox designs, the danger must be counteracted that seals of the sealing device, in particular elastomeric seals, are damaged or even destroyed by contamination particles. By the sealing device associated release agent with depth filtration properties of this risk is to be met. An additionally formed on the inner wall of the storage enclosure pressure pad of a flowable sealing medium reduces the risk of gas losses, especially during downtime, where there is no operating pressure on the fluid side.

Als Kolbenanordnung weist die bekannte Lösung einen Haupt- und einen Hilfskolben auf, die im Speichergehäuse in einem axialen Abstand voneinander angeordnet sind, so dass ein Zwischenraum in Form einer an die Innenwand des Speichergehäuses angrenzenden Kammer gebildet wird, die mit einem Dichtmedium befüllbar ist. Eine am Hilfskolben befestigte Verbindungsstange durchgreift den Hauptkolben und ist in diesem verschiebbar geführt. Eine zwischen Hauptkolben und einem Endanschlag der Verbindungsstange eingespannte Feder dient als Kraftspeicher, der Hilfskolben und Hauptkolben zur Verringerung des Volumens des zwischen ihnen befindlichen Raumes einander anzunähern sucht.As a piston assembly, the known solution comprises a main and an auxiliary piston, which are arranged in the storage housing at an axial distance from each other, so that a gap in the form of an adjacent to the inner wall of the storage chamber chamber is formed, which is filled with a sealing medium. An attached to the auxiliary piston connecting rod passes through the main piston and is guided in this displaceable. A clamped between the main piston and an end stop of the connecting rod spring serves as a force storage, the auxiliary piston and the main piston to reduce the volume of the space located between them seeks to approach each other.

Der Aufbau der Kolbenanordnung aus getrennten Kolben mit Führung des Hilfskolbens an einer im Hauptkolben verschiebbaren Verbindungsstange stellt zum einen eine aufwendige Bauweise dar und ist zum anderen hinsichtlich der Funktionssicherheit wenig zufriedenstellend. Insbesondere bei harten Einsatzbedingungen, wo Unempfindlichkeit gegen mechanische Belastungen, beispielsweise gegen hohe Beschleunigungskräfte, gefordert wird, wie dies insbesondere bei einem Einsatz in Fahrzeugen für wehrtechnische Zweck gefordert wird, ist die Funktionssicherheit gefährdet, weil wegen der engen Passungen der Führung der Verbindungsstange der gesonderten Kolben bereits geringfügige Verformungen zu einem Verklemmen führen können. Der mit dem Hauptkolben längs der Innenwand des Speichergehäuses bewegbare Hilfskolben unterliegt der gleichen Verschleißbeiastung wie der Hauptkolben. Auch stellt die Ausbildung der Kolbenanordnung mit zwei gesonderten Kolben mit Verbindungsstangenführung eine Bauweise dar, die weder kostengünstig herstellbar noch einfach montierbar ist.The structure of the piston assembly of separate pistons with guide of the auxiliary piston on a displaceable in the main piston connecting rod on the one hand represents a complex construction and is on the other hand with regard to the reliability little satisfactory. Especially in harsh operating conditions, where insensitivity to mechanical loads, for example, against high acceleration forces is required, as is required in particular for use in vehicles for defense technology purpose, the reliability is at risk because of the close fit of the leadership of the connecting rod of the separate piston even slight deformations can lead to jamming. The movable with the main piston along the inner wall of the storage housing auxiliary piston is subject to the same Verschleißbeiastung as the main piston. Also, the formation of the piston assembly with two separate piston with connecting rod guide a construction that is neither inexpensive to produce nor easy to install.

Durch die US-A-2 754 847 ist es des weiteren bekannt, bei einem Druckspeicher einen Hilfskolben vollständig integriert in einem Hauptkolben längs dessen Führung aufzunehmen, wobei in dem Hauptkolben mittels des Hilfskolbens ein Raum einschließbar ist, der Teil einer das strömungsfähige Dichtmedium aufnehmenden Kammer ist, die über einen Verbindungskanal fluidführend mit weiteren Kammerteilen verbunden ist, die an die Innenwand des Speichergehäuses des Druckspeichers angrenzt und in dem das strömungsfähige Dichtmedium geführt ist. Die bekannte Druckspeicherlösung weist keine Trennmittel mit Tiefenfiltrationseigenschaft auf und im übrigen wird der Hilfskolben im Hauptkolben ausschließlich von einem Sprengring gehalten, was die Dichtwirkung entsprechend reduziert, wozu auch mit beiträgt, dass sowohl die Führung für den Hilfskolben im Hauptkolben als auch der Hilfskolben selbst der Fluidseite zugewandt sind und demgemäß einen hohen Fluiddruck während des Speicherbetriebes abzudichten haben.It is further known from US-A-2 754 847 to incorporate, in a pressure accumulator, an auxiliary piston fully integrated in a main piston along the guide thereof, wherein a space can be enclosed in the main piston by means of the auxiliary piston, the part of a chamber receiving the flowable sealing medium is, which is fluidly connected via a connecting channel with further chamber parts, which adjoins the inner wall of the storage housing of the pressure accumulator and in which the flowable sealing medium is guided. The known accumulator solution has no release agent with depth filtration property and the rest of the auxiliary piston is held in the main piston exclusively by a snap ring, which reduces the sealing effect accordingly, to which also contributes that both the guide for the auxiliary piston in the main piston and the auxiliary piston itself the fluid side facing and thus have to seal a high fluid pressure during storage operation.

Ausgehend von diesem Stand der Technik stellt sich die Erfindung die Aufgabe, einen Druckspeicher zu schaffen, der, obwohl er einfach und kostengünstig herstellbar ist, ein verbessertes Betriebsverhalten, insbesondere Langzeitverhalten, besitzt, selbst bei besonders harten Einsatzbedingungen.Based on this prior art, the invention has the object to provide a pressure accumulator, which, although it is simple and inexpensive to produce, has improved performance, especially long-term behavior, even under very severe conditions.

Bei einem Druckspeicher der Eingangs genannten Art ist diese Aufgabe erfindungsgemäß dadurch gelöst, dass der Hilfskolben vollständig integriert in einer zur Gasseite offenen Führung des Hauptkolbens geführt ist und dass in diesem mittels des Hilfskolbens ein Raum einschließbar ist, der Teil der das strömungsfähige Dichtmedium aufnehmenden Kammer bildet.In an accumulator of the type mentioned input, this object is achieved in that the auxiliary piston is fully integrated in an open to the gas side guide of the main piston and that in this means of the auxiliary piston, a space can be enclosed, which forms part of the flowable sealing medium receiving chamber ,

Die integrierte Anordnung des Hilfskolbens innerhalb des Hauptkolbens ermöglicht eine besonders kostengünstige Fertigung und einfache Montage. Probleme mit Passungen, wie sie bei gesonderten Kolben und deren Führung über eine Verbindungsstange auftreten, sind vermieden. Bei der erfindungsgemäß vorgesehenen Führung des Hilfskolbens innerhalb des Hauptkolbens ergibt sich eine besondere Robustheit gegen mechanische Belastungen, so dass der erfindungsgemäße Druckspeicher für spezielle Einsatzgebiete, zum Beispiel für wehrtechnische Anwendungen, in besonders hohem Maße geeignet ist, etwa für eine Verwendung bei Kampfpanzern.The integrated arrangement of the auxiliary piston within the main piston allows a particularly cost-effective production and easy installation. Problems with fits, as they occur with separate piston and their leadership via a connecting rod are avoided. In accordance with the invention provided for guiding the auxiliary piston within the main piston results in a special robustness against mechanical loads, so that the pressure accumulator according to the invention for special applications, for example for defense applications, is particularly suitable, for example for use in battle tanks.

An die Ausbildung der Abdichtung des Hilfskolbens relativ zu seiner Führung im Hauptkolben sind keinerlei besondere Anforderungen zu stellen, weil im Unterschied zu dem erwähnten, bekannten Druckspeicher der Hilfskolben nicht längs der Innenwand des Speichergehäuses zusammen mit der Bewegung des Hauptkolbens beweglich ist. Eine Beeinträchtigung des Hilfskolbens durch Verschleiß oder durch Schmutz an der Innenwand des Speichergehäuses ist somit ausgeschlossen. Die Standzeit der aus einer einfachen Kolbendichtung bestehenden Abdichtung zwischen Hilfskolben und Führung im Hauptkolben ist außerordentlich lang, weil im Betrieb praktisch keine ins Gewicht fallende Verschiebebewegung zwischen Hilfskolben und Hauptkolben erfolgt. Zudem ist diese Abdichtung zwischen Hilfskolben und Hauptkolben im Betrieb nur durch einen der Vorspannkraft des Kraftspeichers entsprechenden Differenzdruck belastet.At the formation of the sealing of the auxiliary piston relative to its leadership in the main piston are no special requirements to make, because unlike the mentioned, known pressure accumulator of the auxiliary piston is not along the inner wall of the storage housing along with the movement of the main piston movable. An impairment the auxiliary piston due to wear or dirt on the inner wall of the storage enclosure is thus excluded. The service life of existing from a simple piston seal between auxiliary piston and guide in the main piston is extremely long, because during operation practically no significant displacement movement between the auxiliary piston and the main piston takes place. In addition, this seal between auxiliary piston and main piston is loaded in operation only by one of the biasing force of the force accumulator corresponding differential pressure.

Vorzugsweise ist das Trennmittel mit der Tiefenfiltrationseigenschaft, welches Teil der Dichteinrichtung bildet, an der Kolbenanordnung zur Fluidseite hin zuletzt angeordnet, so dass von der Fluidseite her zu den weiteren Dichtelementen hin wandernde Flüssigkeit, beispielsweise durch Metallpartikel verschmutzte Hydraulikflüssigkeit, eine Tiefenfilterung erfährt, so dass eine Gefährdung der sich axial anschließenden, weiteren Dichtelemente vermieden ist.Preferably, the release agent with the depth filtration property, which forms part of the sealing device, arranged on the piston assembly to the fluid side last, so that from the fluid side to the other sealing elements towards migrating liquid, for example, contaminated by metal particles hydraulic fluid undergoes depth filtering, so that a Danger to the axially subsequent, further sealing elements is avoided.

Als Trennmittel findet bevorzugt ein Filz, insbesondere in Form mindestens eines Filzringes, Verwendung. Filz steht hierbei im Sinne der Erfindung für ein verdichtetes Gelege mit regelloser Anordnung von Fasern, insbesondere von Natur- und Chemiefasern. Es kann sowohl Nadelfilz als auch Walkfilz eingesetzt werden, bei dem die Anfangswatte ähnliche Faserschicht mittels Filznadeln mit Widerhaken verschlungen wird bzw. bei dem Faservliese durch Druck und Bewegung unter Wärme und Feuchtigkeit verfestigt werden. Des weiteren können Webfilzmaterialien eingesetzt werden aus gewebten, gewalkten und verfilzten Stoffen. Als günstig hat sich die Verwendung von Filzmaterialien relativ hoher Dichte erwiesen, etwa Materialien mit Dichtewerten im Bereich von 0,36 g/cm3, entsprechend Härtegruppe F2 nach DIN 61200. Es versteht sich, dass je nach Beschaffenheit, Verschmutzungsart und -grad der Flüssigkeit der Fluidseite beliebige geeignete Filtrationsmaterialien anderer Dichte und/oder Härtegruppen gewählt werden können.As a release agent is preferably a felt, in particular in the form of at least one felt ring, use. Felt here in the context of the invention for a compacted scrim with random arrangement of fibers, especially natural and man-made fibers. It can be used both needle felting and felting, in which the initial lap similar fiber layer is entangled by means of felted needles barbs or are solidified in the fiber webs by pressure and movement under heat and moisture. Furthermore, woven felt materials can be used made of woven, gewalkten and matted fabrics. The use of felt materials of relatively high density, such as materials with density values in the range of 0.36 g / cm 3 , corresponding to hardness group F 2 according to DIN 61200, has proven favorable. It is understood that, depending on the nature, type of contamination and degree of liquid side fluid any suitable filtration materials other density and / or hardness groups can be selected.

Nachstehend ist die Erfindung anhand eines in der Zeichnung dargestellten Ausführugnsbeispieles im einzelnen beschrieben. Es zeigen:

  • Fig. 1 einen abgebrochen gezeichneten und nur den fluidseitigen Endbereich zeigenden Längsschnitt eines Druckspeichers gemäß einem Ausführungsbeispiel der Erfindung und
  • Fig. 2 einen Längsschnitt nur der Kolbenanordnung des Druckspeichers von Fig. 1, wobei die Kolbenanordnung jedoch im Unterschied zu Fig. 1 in entspanntem Zustand gezeigt ist.
The invention with reference to a Ausführugnsbeispieles shown in the drawing is described in detail. Show it:
  • Fig. 1 is a broken drawn and only the fluid-side end region facing longitudinal section of a pressure accumulator according to an embodiment of the invention and
  • Fig. 2 is a longitudinal section only of the piston assembly of the pressure accumulator of Fig. 1, wherein the piston assembly, however, is shown in contrast to Fig. 1 in a relaxed state.

Fig. 1 zeigt den fluidseitigen Abschnitt des Speichergehäuses des Ausführungsbeispieles des erfindungsgemäßen Druckspeichers, mit einem Zylinderrohr 1 und einem den fluidseitigen Abschluß bildenden Zylinderdeckel 3. Letzterer ist am Ende des Zylinderrohres 1 mittels eines geteilten Sicherungsringes 5 fixiert, welcher wiederum durch eine Ringscheibe 7 gesichert ist, die mit dem Zylinderdeckel 3 mittels dreier Schrauben 9 verschraubt ist von denen in Fig. 1 lediglich eine sichtbar ist. Der Zylinderdeckel 3 weist eine zur Zylinderachse 11 konzentrische Bohrung 12 für den Anschluß einer Fluidleitung auf.Fig. 1 shows the fluid-side portion of the storage case of the embodiment of the accumulator according to the invention, with a cylinder tube 1 and the fluid-side conclusion forming cylinder cover 3. The latter is fixed at the end of the cylinder tube 1 by means of a split retaining ring 5, which in turn is secured by an annular disc 7 , which is bolted to the cylinder cover 3 by means of three screws 9 of which in Fig. 1, only one is visible. The cylinder cover 3 has a bore 12 concentric with the cylinder axis 11 for the connection of a fluid line.

In ähnlicher Weise ist das nicht dargestellte gasseitige Ende des Zylinderrohres 3 durch einen Zylinderdeckel geschlossen, der in der bei derartigen Druckspeichern üblichen Art entsprechende Armaturen, wie ein Gasfüllventil, aufweist.Similarly, the gas-side end (not shown) of the cylinder tube 3 is closed by a cylinder cover, which has corresponding fittings, such as a gas filling valve, in the manner customary for such pressure accumulators.

Entsprechend der am Zylinderdeckel 3 vorgesehenen, mit 13 bezeichneten Dichtpackung ist auch am nicht dargestellten Zylinderdeckel am gasseitigen Ende des Zylinderrohres 1 eine Dichtpackung vorgesehen.According to the provided on the cylinder cover 3, denoted by 13 seal packing a gasket is also provided on the cylinder cover, not shown, on the gas side end of the cylinder tube 1.

Im Zylinderrohr 1, das beim vorliegenden Beispiel kreiszylindrisch ist, ist eine Kolbenanordnung entlang der Achse 11 längs verschiebbar geführt. Diese Kolbenanordnung, die in Fig. 2 gesondert dargestellt und als Ganzes mit 15 bezeichnet ist, ist aus einem Hauptkolben 17 und einem Hilfskolben 19 gebildet, welch letzterer in einer Führung 21 bewegbar geführt ist, welche sich im Hauptkolben 17 konzentrisch zur Achse 11 erstreckt und zu der in Fig. 1 rechtsseitig gelegenen Gasseite 23 hin offen ist. Die aus Hauptkolben 17 und Hilfskolben 19 gebildete Kolbenanordnung 15 trennt innerhalb des Zylinderrohres 1 die mit 23 bezeichnete Gasseite von der in Fig. 1 mit 25 bezeichneten Fluidseite, die mit dem Fluidanschluß 12 in Verbindung ist.In the cylinder tube 1, which is circular-cylindrical in the present example, a piston assembly along the axis 11 is guided longitudinally displaceable. This piston assembly, which is shown separately in Fig. 2 and designated as a whole by 15, is formed of a main piston 17 and an auxiliary piston 19, which latter is movably guided in a guide 21 which extends concentrically in the main piston 17 to the axis 11 and to the right in Fig. 1 located gas side 23 is open. The piston assembly 15 formed from the main piston 17 and auxiliary piston 19 separates within the cylinder tube 1, the gas side designated by 23 of the in Fig. 1 with 25 designated fluid side, which is in communication with the fluid port 12.

An dem der Gasseite 23 zugewandten Ende ist die Führung 21 des Hauptkolbens 17 durch einen Ringkörper 27 begrenzt, der durch einen Segerring 29 axial gesichert ist. Der in der Führung 21 des Hauptkolbens 17 befindliche Hilfskolben 19 ist gegen den Austritt aus der Führung 21 durch Anlage am Ringkörper 27 gesichert. Fig. 1 zeigt die Kolbenstellung des Hilfskolbens 19, in der dieser am Ringkörper 27 anliegt. Der Hilfskolben 19 ist trogförmig gestaltet, wobei in dem zur Längsachse 11 konzentrischen Innenraum 31 eine Schrauben-Druckfeder 33 sitzt, die sich einerseits am Boden des Innenraumes 31 und andererseits am Ringkörper 27 abstützt. Zusätzlich zu dem am Hilfskolben 19 wirkenden Druck der Gasseite 23 erzeugt die als Kraftspeicher dienende Druckfeder 33 am Hilfskolben 19 eine Vorspannkraft für eine Bewegung nach links, entsprechend der Blickrichtung der Fig. 1 und 2, d.h. für die Bewegung in einer Richtung, die einer Verringerung des Volumens des Raumes 35 entspricht, der sich zwischen dem Hilfskolben 19 und dem geschlossenen Ende der Führung 21 im Hauptkolben 17 befindet. Der Raum 35, der wie nachstehend näher erläutert wird, für die Aufnahme eines strömungsfähigen Dichtmediums vorgesehen ist, bildet Teil einer Kammer, die an die Innenwand des Zylinderrohres 1 angrenzt, um ein an dieser Innenwand anliegendes Druckpolster aus dem Dichtmedium zu bilden. Zu diesem Zweck ist der Raum 35 über mehrere Verbindungskanäle 37 mit einer in den Umfang des Hauptkolbens 17 eingearbeiteten Vertiefung 39 verbunden, die sich ringförmig über den gesamten Umfang des Hauptkolbens 17 erstreckt. Wie aus den Fig. ersichtlich, verläuft die Achse 41 der Verbindungskanäle 37 zur Hauptlängsachse 11 schräg. Der Boden der Vertiefung 39 weist über seine axiale Erstreckung eine unterschiedliche Tiefe auf. Genauer gesagt weist der Boden der Vertiefung 39 aneinander angrenzende ebene und konkav gewölbte Bodenflächenteile 38 bzw. 40 auf, wobei die Einmündung der Verbindungskanäle 37 in die Vertiefung 39 in einem ebenen Bodenflächenteil 38 gelegen ist, dessen Ebene sich senkrecht zur Achse 41 der Verbindungskanäle 37 erstreckt.At the end 23 facing the gas side, the guide 21 of the main piston 17 is limited by an annular body 27 which is axially secured by a Segerring 29. The auxiliary piston 19 located in the guide 21 of the main piston 17 is secured against the exit from the guide 21 by contact with the annular body 27. Fig. 1 shows the piston position of the auxiliary piston 19, in which this rests on the annular body 27. The auxiliary piston 19 is designed trough-shaped, wherein in the concentric with the longitudinal axis 11 interior 31 a helical compression spring 33 is seated, which is supported on the one hand at the bottom of the interior 31 and on the other hand on the annular body 27. In addition to acting on the auxiliary piston 19 pressure of the gas side 23 serving as energy accumulator compression spring 33 generates on the auxiliary piston 19 a biasing force for a movement to the left, corresponding to the viewing direction of Fig. 1 and 2, ie for the movement in one direction, the reduction the volume of the space 35 corresponds, which is located between the auxiliary piston 19 and the closed end of the guide 21 in the main piston 17. The space 35, which is explained in more detail below, is provided for receiving a flowable sealing medium forms part of a chamber which adjoins the inner wall of the cylinder tube 1 to form a pressure pad applied to this inner wall of the sealing medium. For this purpose, the space 35 is connected via a plurality of connecting channels 37 with a recess 39 incorporated in the circumference of the main piston 17, which extends annularly over the entire circumference of the main piston 17. As can be seen from the figures, the axis 41 of the connecting channels 37 extends obliquely to the main longitudinal axis 11. The bottom of the recess 39 has over its axial extent to a different depth. More specifically, the bottom of the recess 39 has contiguous planar and concave bottom surface portions 38 and 40, respectively, with the junction of the connection channels 37 located in the recess 39 in a flat bottom surface portion 38 whose plane is perpendicular to the axis 41 of the connection channels 37 ,

Die die Trennung zwischen der Gasseite 23 und der Fluidseite 35 bewirkende Dichteinrichtung ist zur Gänze am Umfang des Hauptkolbens 17 ausgebildet. Als der Fluidseite 25 nächstgelegenes Bauelement weist die Dichteinrichtung ein Trennmittel mit Tiefenfiltrationseigenschaften auf, nämlich beim Ausführungsbeispiel einen Filzring 43, der im Bereich des den Abschluß der inneren Führung 21 bildenden Kolbenbodens 45 in einer Ringnut des Hauptkolbens 17 sitzt. Axial gegen die Vertiefung 39 hin versetzt ist eine Kolbendichtung 47 der bei Druckspeichern üblicherweise verwendeten Art vorgesehen, beispielsweise eine Elastomerdichtung. Axial weiter zur Gasseite 23 hin versetzt befindet sich nach der Vertiefung 39 eine weitere Kolbendichtung 47. Schließlich ist am gasseitigen Endbereich des Hauptkolbens 17 eine Kolbenführungsleiste 49 vorgesehen.The sealing means effecting the separation between the gas side 23 and the fluid side 35 is entirely formed on the circumference of the main piston 17. As the fluid side 25 nearest component, the sealing device has a release agent with depth filtration properties, namely in the embodiment a felt ring 43 which sits in the region of the end of the inner guide 21 forming piston crown 45 in an annular groove of the main piston 17. Axially offset against the recess 39 toward a piston seal 47 of the type commonly used in pressure accumulators is provided, for example, an elastomeric seal. Axially further offset to the gas side 23 is located after the recess 39 a further piston seal 47. Finally, a piston guide rail 49 is provided at the gas-side end region of the main piston 17.

Zentral im Kolbenboden 45 angeordnet befindet sich ein Füllkanal 51 für das Einbringen des Dichtmediums in den Raum 35, der über die Verbindungskanäle 37 zusammen mit der Vertiefung 39 die Kammer für das an der Innenwand des Zylinderrohres 1 anliegende Druckpolster des Dichtmediums bildet. Im Füllkanal 51 befindet sich ein Rückschlagventil 53. Außerdem ist im Kolbenboden 45 eine verschließbare Entlüftungsbohrung 55 vorgesehen.Centrally located in the piston head 45 is a filling channel 51 for introducing the sealing medium into the space 35, which forms the chamber for the voltage applied to the inner wall of the cylinder tube 1 pressure pad of the sealing medium via the connecting channels 37 together with the recess 39. In the filling channel 51 is a check valve 53. In addition, a closable vent hole 55 is provided in the piston head 45.

Der Hilfskolben 19 ist gegenüber der Führung 21 im Hauptkolben 17 mittels eines Dichtringes 57 abgedichtet. Ein Dichtelement einfacher Bauart kann hier benutzt werden, weil die zu bildende Abdichtung im Betrieb keinen großen Belastungen ausgesetzt ist, zumal im Betrieb praktisch keine Verschiebebewegung des Hilfskolbens 19 erfolgt.The auxiliary piston 19 is sealed relative to the guide 21 in the main piston 17 by means of a sealing ring 57. A sealing element of simple design can be used here, because the seal to be formed is not exposed to great loads during operation, especially since during operation virtually no displacement movement of the auxiliary piston 19 takes place.

Nachstehend ist die Funktionsweise des erfindungsgemäßen Druckspeichers näher erläutert. Fig. 2 zeigt die Kolbenanordnung 15 in entspanntem Zustand, wobei der Hilfskolben 19 durch die Kraft der Druckfeder 33 bis zur Anlage am Kolbenboden 45 verschoben ist. Für die Montage des Druckspeichers wird die Entlüftungsbohrung 55 geöffnet und die Kolbenanordnung 15 bei abgenommenem Zylinderdeckel 3 in das Zylinderrohr 1 eingesetzt. Über den Füllkanal 51 und das Rückschlagventil 53 wird nun das zur Verwendung vorgesehene Dichtmedium in den Raum 35 eingefüllt, bis der Zustand der Entlüftung erreicht ist. Die Entlüftungsbohrung 55 wird nun geschlossen und durch weitere Zufuhr des Dichtmediums über das Rückschlagventil 53 ein Druck im Raum 35 aufgebaut, bis sich der Hilfskolben gegen die Kraft der Feder 33 gegen den Ringkörper 27 bewegt, wie dies in Fig. 1 dargestellt ist. Die Zufuhr des Dichtmediums wird nun beendet, so dass im Raum 35, und damit über die Verbindungskanäle 37 in der Vertiefung 39, ein Druckpolster des Dichtmediums vorhanden ist, wobei der Druck von der Federkraft der Druckfeder 33 abhängig ist und bei einem praktischen Beispiel etwa 5 Bar beträgt. Durch Anbringen des Zylinderdekkels 3 wird nun das Speichergehäuse geschlossen.The operation of the pressure accumulator according to the invention is explained in more detail below. Fig. 2 shows the piston assembly 15 in a relaxed state, the auxiliary piston 19 is displaced by the force of the compression spring 33 until it rests against the piston head 45. For the assembly of the accumulator, the vent hole 55 is opened and the piston assembly 15 is inserted into the cylinder tube 1 with the cylinder cover 3 removed. About the filling channel 51 and the check valve 53, the intended for use sealing medium is now filled in the space 35 until the state of the vent is reached. The vent hole 55 is now closed and built by further supply of the sealing medium via the check valve 53, a pressure in the space 35 until the auxiliary piston moves against the force of the spring 33 against the annular body 27, such as this is shown in Fig. 1. The supply of the sealing medium is now terminated, so that in the space 35, and thus via the connecting channels 37 in the recess 39, a pressure cushion of the sealing medium is present, the pressure of the spring force of the compression spring 33 is dependent and in a practical example about 5 Bar amounts to. By attaching the Zylinderdekkels 3 now the storage enclosure is closed.

Entsprechend dem im Raum 35 und in der Vertiefung 39 herrschenden geringen Druck von beispielsweise 5 Bar sind die Kolbendichtungen 47 beide jeweils nach außen mit einem geringen Differenzdruck vorgespannt, so dass ein Eindringen von Schmutz von außen her nicht möglich ist. Zudem sind die Kolbendichtungen 47 durch das Dichtmedium geschmiert, bei dem es sich vorzugsweise um eine auf der Fluid- oder Ölseite eingesetzte Flüssigkeit handelt. Als Dichtmedium können jedoch praktisch sämtliche strömungsfähigen Stoffe eingesetzt werden, auch Gas. Die Verwendung der auf der Fluidseite vorliegenden Hydraulikflüssigkeit ist jedoch vorteilhaft, weil somit keine Fremdöle im System vorhanden sind.According to the prevailing in the space 35 and in the recess 39 low pressure of, for example, 5 bar, the piston seals 47 are both biased outward with a small differential pressure, so that ingress of dirt from the outside is not possible. In addition, the piston seals 47 are lubricated by the sealing medium, which is preferably a fluid used on the fluid or oil side. As a sealing medium, however, virtually all flowable substances can be used, including gas. However, the use of the hydraulic fluid present on the fluid side is advantageous, because thus no foreign oils are present in the system.

Wird auf der Gasseite 23 nunmehr ein Gas-Vorspanndruck aufgebaut, indem beispielsweise N2 eingegeben wird, wobei bei einer praktischen Anwendung beispielsweise ein Vorspanndruck von 60 Bar vorgesehen sein kann, dann erhöht sich der Druck im Raum 35 und in der Vertiefung 39 bei diesem Beispiel auf einen Druckwert von 60 Bar zuzüglich des durch die Kraft der Feder 33 mittels des Hilfskolben 19 erzeugten Druckes, also beim genannten Beispiel auf etwa 65 Bar. Da somit der Druck in der Vertiefung 39 höher ist als auf der Gasseite 23, ist kein Durchwandern von Gas über die der Gasseite 23 nächstgelegene Kolbendichtung 47 möglich.If now on the gas side 23, a gas-biasing pressure is built up, for example, N 2 is entered, wherein in a practical application, for example, a biasing pressure of 60 bar can be provided, then the pressure in the space 35 and in the recess 39 increases in this example to a pressure value of 60 bar plus the pressure generated by the force of the spring 33 by means of the auxiliary piston 19, so in the example mentioned to about 65 bar. Thus, since the pressure in the recess 39 is higher than on the gas side 23, no migration of Gas on the gas side closest to the gasket 23 47 possible.

Wird der Speicher in Betrieb genommen, also die Fluidseite 25 mit dem Fluiddruck belastet, erhöht sich in entsprechender Weise der Druck im Speichergehäuse, so dass der Druck auf der Gasseite 23 entsprechend steigt, als Gedankenspiel angenommen beispielsweise auf 150 Bar. Dadurch erhöht sich wiederum der Druck in dem das Dichtmedium enthaltenden Raum 35 und in der Vertiefung 39 auf einen Druckwert, der dem Gasdruck auf der Gasseite 23 zuzüglich des durch die Feder 33 am Hilfskolben 19 erzeugten Druckes entspricht, also beim erwähnten Beispiel auf etwa 155 Bar. Dadurch ist der an den Kolbendichtungen 47 anliegende Differenzdruck ebenfalls lediglich etwa 5 Bar, d.h. im Betrieb sind die Kolbendichtungen 47 ausschließlich mit dem erwähnten, geringen Differenzdruck belastet.If the memory is put into operation, so loaded the fluid side 25 with the fluid pressure increases in a corresponding manner, the pressure in the storage enclosure, so that the pressure on the gas side 23 increases accordingly, as thought game assumed, for example, to 150 bar. This in turn increases the Pressure in the space containing the sealing medium 35 and in the recess 39 to a pressure value corresponding to the gas pressure on the gas side 23 plus the pressure generated by the spring 33 on the auxiliary piston 19 pressure, ie in the example mentioned to about 155 bar The piston seals 47 applied differential pressure also only about 5 bar, ie In operation, the piston seals 47 are loaded exclusively with the mentioned, low differential pressure.

In Zusammenwirkung mit der durch den Filzring 43 bewirkten Filtration des Hydraulikfluides und der geringen Belastung der Kolbendichtungen 47, wie sie durch das Druckpolster des Dichtmediums in der Vertiefung 39 erreicht ist, ergeben sich für den erfindungsgemäßen Druckspeicher außerordentlich lange Standzeiten selbst bei harten Betriebsbedingungen. Der Filzring 43 schützt nicht nur die Dichteinrichtung vor Verunreinigungen, sondern schützt auch die nachfolgende Kolbendichtung 47 vor Druckschlägen, da das in dem hinter dem Filzring 43 und vor der nachfolgenden Kolbendichtung 47 sitzende Ölvolumen einen Differenzdruck erzeugtIn conjunction with the effected by the felt ring 43 filtration of the hydraulic fluid and the low load on the piston seals 47, as achieved by the pressure cushion of the sealing medium in the recess 39, resulting for the pressure accumulator invention extremely long service life even under harsh operating conditions. The felt ring 43 not only protects the sealing device against contamination, but also protects the subsequent piston seal 47 from pressure surges, since the seated in the behind the felt ring 43 and before the subsequent piston seal 47 oil volume creates a differential pressure

Der erfindungsgemäße Druckspeicher ist insbesondere gegen Gasverluste bei Stillstandszeiten, d.h. bei fehlendem Fluiddruck, geschützt, weil der in dem Raum 35 und der Vertiefung 39 herrschende Druck des Dichtmediums immer höher ist als der Druck auf der Gasseite 23.The pressure accumulator according to the invention is in particular protected against gas losses at standstill times, ie in the absence of fluid pressure, because the prevailing in the space 35 and the recess 39 pressure of the sealing medium is always higher than the pressure on the gas side 23rd

Selbst wenn nach langer Betriebslebensdauer das Dichtmedium in der Kammer 35 verbraucht worden sein sollte, bleibt die Funktionsfähigkeit des Systems erhalten. In diesem Falle führt ein Durchwandern der der Gasseite 23 nächstgelegenen Kolbendichtung 47 durch das Gas zu einer Ansammlung des Gases im Raum 35. Wird der Druckspeicher nun außer Betrieb gesetzt, indem die Fluidseite 25 drucklos gemacht wird, ergibt sich im Raum 35 aufgrund der auf den Hilfskolben 19 wirkenden Kraft der Feder 33 wieder ein Druckniveau, in diesem Falle ein Gasdruckniveau, das der Federkraftwirkung entsprechend höher ist als der Druck auf der Gasseite 23, so dass auch in diesem Betriebszustand Sicherheit gegen Gasverluste gegeben ist.Even if after a long service life, the sealing medium in the chamber 35 should have been consumed, the functionality of the system is maintained. In this case, a migration of the gas side nearest the piston seal 47 47 through the gas leads to an accumulation of the gas in the space 35. If the accumulator now put out of operation by the fluid side 25 is depressurized, results in the space 35 due to the on the Auxiliary piston 19 acting force of the spring 33 again a pressure level, in this case a gas pressure level corresponding to the spring force action is higher than the pressure on the gas side 23, so that security is given in this operating state against gas losses.

Claims (9)

  1. Pressure store with a piston arrangement (15) consisting of a main piston (17) and an secondary piston (19) moveable relative to the former and longitudinally displaceable within a store housing (1), separating a fluid side (25) of the store from its gas side (23) by means of a sealing device, whereby the latter comprises a separating means (43) with depth filtration characteristics, additional sealing elements (47) as well as a chamber (35, 39) adjacent to the inside wall of the store housing (1) for a flowable sealing medium, which can be pre-tensioned by means of the secondary piston (19) which is subjected to the pressure of the gas side (23) and the force of a force store (33) for reducing the volume of the chamber with a relative movement, characterised in that the secondary piston (19) is completely integrated into a guide (21) of the main piston (17) that is open on the gas side (23), and in that a space (35) which forms a part of the chamber (35, 39) receiving the flowable medium can be enclosed in the same by means of the secondary piston (19).
  2. Pressure store according to Claim 1, characterised in that the chamber for the flowable sealing medium comprises an annular recess (39) worked into the circumference of the main piston (17), which is connected with the space (35) in the main piston (17) adjacent to the secondary piston (19) via at least one connecting channel (37).
  3. Pressure store according to Claim 2, characterised in that the recess (39) on the circumference of the main piston (17) envisaged for the sealing medium comprises areas of different depth along its axial expansion, which are formed by level (38) and concavely arced (40) floor surface parts arranged adjacent to each other, and in that the at least one connecting channel (37) extends diagonally to the longitudinal axis (11) of the main piston and opens into the circumferential recess (39) in a level floor surface part (38) extending vertical to the diagonal axis (41) of the connection channel (37).
  4. Pressure store according to Claim 2 or 3, characterised in that the circumferential recess (39) of the main piston (17) forming a part of the chamber for the flowable sealing medium is situated between two piston seals (47) arranged at an axial distance from each other.
  5. Pressure store according to one of the Claims 1 to 4, characterised in that the secondary piston (19) is secured against falling out of the guide (21) of the main piston (17) by means of a cover (27) located at the opening, and in that a pressure spring (33) tensioned between the cover (27) and the secondary piston (19) is envisaged as the force store.
  6. Pressure store according to one of the Claims 1 to 5, characterised in that the separating means with the depth filtration characteristics consists of a fleece, in particular in the form of a fleece ring (43).
  7. Pressure store according to one of the Claims 1 to 6, characterised in that the separating means with the depth filtration characteristics is positioned last on the fluid side (25) as a part of the sealing device, and in that the additional sealing elements (47) of the sealing device in the direction of the gas side (23) are located along the outer circumference of the main piston (17).
  8. Pressure store according to one of the Claims 1 to 7, characterised in that the space (35) enclosed between the main (17) and the secondary piston (19) can be filled with the flowable sealing medium via a filler opening (51) comprising a non-return valve (53) envisaged in the end of the main piston (17) facing the fluid side (25).
  9. Pressure store according to Claim 8, characterised in that a venting possibility (55) for the space (35) receiving the flowable sealing medium is envisaged in the end (45) of the main piston (17) facing the fluid side (25).
EP03001475A 2002-03-05 2003-01-23 Pressure accumulator Expired - Lifetime EP1342922B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10209663A DE10209663C1 (en) 2002-03-05 2002-03-05 Pressure reservoir for fluid actuator has separator with filter and auxiliary piston to pressurize seal fluid around main piston
DE10209663 2002-03-05

Publications (3)

Publication Number Publication Date
EP1342922A2 EP1342922A2 (en) 2003-09-10
EP1342922A3 EP1342922A3 (en) 2004-05-26
EP1342922B1 true EP1342922B1 (en) 2006-11-29

Family

ID=7714024

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03001475A Expired - Lifetime EP1342922B1 (en) 2002-03-05 2003-01-23 Pressure accumulator

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Country Link
EP (1) EP1342922B1 (en)
AT (1) ATE347039T1 (en)
DE (2) DE10209663C1 (en)
DK (1) DK1342922T3 (en)
ES (1) ES2275955T3 (en)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004008768A1 (en) * 2004-02-23 2005-09-08 Albrecht, Friedhelm Hydraulic cylinder has a first circular groove and the cover has a surrounding second ring groove
DE102004048822A1 (en) * 2004-10-07 2006-04-13 Continental Teves Ag & Co. Ohg Electro hydraulic module especially for vehicle brakes has a compact layout with two coaxial pistons and a damping chamber
DE102011089951A1 (en) * 2011-12-27 2013-06-27 Robert Bosch Gmbh Hydraulically controlled storage chamber valve
CN109854561A (en) * 2019-02-12 2019-06-07 广西玉柴重工有限公司 A kind of fluid path appearance change valve

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2754847A (en) * 1951-07-20 1956-07-17 Electrol Inc Piston-type accumulators
CH591020A5 (en) * 1975-08-15 1977-08-31 Gfeller Hans High pressure storage reservoir - has separator of two longitudinally displaceable pistons
DE3930557A1 (en) * 1989-09-13 1991-03-14 Bosch Gmbh Robert PRINT MEDIA STORAGE, ESPECIALLY FOR VEHICLE BRAKING SYSTEMS
DE19701303A1 (en) * 1997-01-16 1998-07-23 Hydac Technology Gmbh Piston accumulator with sealing device
DE19740150A1 (en) * 1997-09-12 1999-03-25 Hydac Technology Gmbh Piston accumulator with depth filtration seal

Also Published As

Publication number Publication date
ES2275955T3 (en) 2007-06-16
DE50305803D1 (en) 2007-01-11
EP1342922A3 (en) 2004-05-26
ATE347039T1 (en) 2006-12-15
EP1342922A2 (en) 2003-09-10
DE10209663C1 (en) 2003-07-31
DK1342922T3 (en) 2007-03-26

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