EP1181457B1 - Hydropneumatic pressure accumulator - Google Patents

Hydropneumatic pressure accumulator Download PDF

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Publication number
EP1181457B1
EP1181457B1 EP00912582A EP00912582A EP1181457B1 EP 1181457 B1 EP1181457 B1 EP 1181457B1 EP 00912582 A EP00912582 A EP 00912582A EP 00912582 A EP00912582 A EP 00912582A EP 1181457 B1 EP1181457 B1 EP 1181457B1
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EP
European Patent Office
Prior art keywords
valve
end plate
metal bellows
tappet
gas chamber
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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
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EP00912582A
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German (de)
French (fr)
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EP1181457A1 (en
Inventor
Norbert Weber
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Hydac Technology GmbH
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Hydac Technology GmbH
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • 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
    • F15B1/22—Liquid port constructions
    • 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
    • F15B1/10—Accumulators using a gas cushion; Gas charging devices; Indicators or floats therefor with flexible separating means
    • F15B1/103—Accumulators using a gas cushion; Gas charging devices; Indicators or floats therefor with flexible separating means the separating means being bellows
    • 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
    • F15B2201/30—Accumulator separating means
    • F15B2201/315—Accumulator separating means having flexible separating means
    • F15B2201/3153—Accumulator separating means having flexible separating means the flexible separating means being bellows
    • 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
    • F15B2201/415—Gas ports

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
  • Pharmaceuticals Containing Other Organic And Inorganic Compounds (AREA)
  • Vehicle Body Suspensions (AREA)

Abstract

A hydropneumatic pressure accumulator, includes a gas chamber, an oil chamber, and a pair of metal bellows separating the chambers. An end plate is displaced according to volume changes in the gas chamber and oil chamber. A valve releases and blocks the flow of hydraulic fluid out of and into the oil chamber and has a valve lifter that controls the valve. During the displacement of the end plate, corresponding to a volume expansion in the gas chamber exceeding a predetermined maximum value, the valve lifter can be displaced by the end plate into a position which blocks the valve. The valve lifter is connected in a fixed manner to the end plate of the metal bellows. The valve can be blocked in two opposing directions by the displacement of the valve lifter.

Description

Die Erfindung bezieht sich auf einen hydropneumatischen Druckspeicher mit den Merkmalen des Oberbegriffs des Patentanspruches 1.The invention relates to a hydropneumatic pressure accumulator with the features of the preamble of claim 1.

Bekanntermaßen ist bei Metallbalgspeichem eine Hubbegrenzung für die dem Ausziehen und dem Zusammenziehen des Metallbalges entsprechenden Bewegungen der Endplatte erforderlich, um den Balg vor Überbelastungen zu schützen. Bei einem bekannten Druckspeicher der obengenannten Art, vergleiche WO 97/46823 A1, ist im Hinblick auf dieses Problem der Ventilstößel des am Ölraum angeschlossenen Ventiles relativ zur Endplatte des Metallbalges in solcher Lagebeziehung angeordnet, daß die Endplatte den Ventilstößel bei Erreichen einer gewünschten Endstellung beaufschlagt und in die Sperrstellung des Ventils verschiebt, so daß der Ausstrom von Hydraulikfluidum aus dem Ölraum bei Erreichen dieser Endstellung der Endplatte unterbunden wird. Bei geschlossenem Ventil bleibt somit, selbst wenn das angeschlossene Hydrauliksystem drucklos werden sollte, im Ölraum des Speichers ein Druck aufrechterhalten, der dem im Gasraum momentan herrschenden Gasdruck entspricht, so daß am Metallbalg beidseits Druckgleichgewicht herrscht.As is known, a stroke limitation for the metal bellows is corresponding to the extension and contraction of the metal bellows End plate movements required to protect the bellows from overloads to protect. In a known pressure accumulator of the above Art, compare WO 97/46823 A1, is with regard to this problem the valve lifter of the valve connected to the oil chamber relative to the end plate the metal bellows arranged in such a relationship that the end plate acts on the valve lifter when a desired end position is reached and moves into the blocking position of the valve, so that the outflow of hydraulic fluid from the oil chamber when this end position is reached End plate is prevented. When the valve is closed, it remains if the connected hydraulic system should become depressurized, in the oil room maintain a pressure in the reservoir that is currently in the gas space prevailing gas pressure, so that on the metal bellows on both sides Pressure equilibrium prevails.

Zwar ist dadurch eine Überbelastung des Balges bei Drucklosigkeit des angeschlossenen Hydrauliksystems verhindert, es besteht jedoch die Gefahr der Beschädigung des Balges bei Zuständen mit auf der Ölseite herrschendem Überdruck oder bei einem Fehlen des Vorfülldruckes auf der Gasseite. This causes an overload of the bellows when the connected one is depressurized Hydraulic system prevents, but there is a risk damage to the bellows in conditions with prevailing on the oil side Overpressure or if there is no pre-filling pressure on the gas side.

In diesem Fall bewegt sich beim Ausziehen des Balges die Endplatte bis zum mechanischen Anschlag am Speichergehäuse. Bei solcher mechanischer Hubbegrenzung wirkt am Balg entsprechend dem einseitig gegebenen Überdruck eine Druckdifferenz, die zu Zerstörungen führen kann. Man ist daher bislang gezwungen, dickere und mehrlagige Metallbälge zur Anwendung zu bringen. In nachteiliger Weise werden dadurch die Federsteifigkeit.stark vergrößert und der Federweg der einzelnen Windungen des Balges verkleinert. Die Anwendung dickerer, mehrlagiger Metallbälge führt nicht nur zu erhöhtem Gewicht, sondern auch zu einem verhältnismäßig schlechten Ansprechverhalten bei Druckänderungen.In this case the end plate moves up to when the bellows is pulled out for mechanical stop on the storage case. With such mechanical Stroke limitation acts on the bellows according to the one-sided Overpressure is a pressure difference that can lead to destruction. you has therefore been forced to use thicker and multi-layer metal bellows bring to. This disadvantageously makes the spring stiffness strong enlarged and the travel of the individual turns of the Bellows downsized. The use of thicker, multi-layer metal bellows leads not only to increased weight, but also to a proportionate poor response to pressure changes.

Durch Fig.4 aus PATENT ABSTRACTS OF JAPAN vol. 1996, no. 09, 30. September 1996, (1996-09-30) & JP 08 121401 A (NOK), 14.Mai 1996 (1996-05-14) ist ein gattungsgemäßer hydropneumatischer Druckspeicher bekannt mit einem Gasraum und einem Ölraum und einem diese Räume trennenden Metallbalg, der eine entsprechend den Volumenänderungen von Gasraum zu Ölraum bewegliche Endplatte aufweist. Innerhalb des Gehäuses mit dem Metallbalg ist dieses von einer Trennplatte mit einem Fluidanschluß durchgriffen, der fluidführend das Innere des Metallbalges mit dem Inneren eines weiteren Fluidraumes innerhalb des Gehäuses begrenzt, wobei der dahingehende zusätzliche Fluidraum nach außen hin über einen Hydraulikanschluß an der Bodenseite des Gehäuses fluidführend mit Teilen eines Hydraulikkreislaufes verbunden ist. Ein mit der Endplatte des Metallbalges verbundener Ventilstößel weist einen Sperrkörper auf, dessen beiden einander gegenüberliegenden Seiten als Ventilkegel ausgebildet sind und in Anlage bringbar sind einmal mit einem Ventilsitz, der an der Trennplatte angeordnet ist, und einmal mit einem Ventilsitz am bodenseitigen Hydraulikanschluß, der in Richtung des Inneren des weiteren Fluidraumes weist. Sowohl die genannten Ventilkegel als auch die Ventilsitze weisen mit den Scheiteln ihrer Kegelflächen voneinander weg, wobei über die Kegelflächen ein gutes Abdichtverhalten erreicht ist. Aufgrund des zusätzlichen Fluidraumes baut die bekannte Vorrichtung groß auf und im Hinblick auf die zu bewegenden Fluidmengen im Metallbalg und zusätzlich im weiteren Fluidraum ist das Ansteuerverhalten für das Ventil verzögert, so daß zumindest kurzfristig Überbelastungen des Metallbalges auftreten können. Ausgehend von diesem Stand der Technik liegt der Erfindung die Aufgabe zugrunde, einen Druckspeicher der betrachteten Art zu schaffen, bei dem Überbelastungen des Metallbalges im Betrieb mit Sicherheit vermieden sind.
Bei einem hydropneumatischen Druckspeicher der eingangs genannten Art ist diese Aufgabe erfindungsgemäß dadurch gelöst, daß der Hydraulikanschluß das Ventil mit seinen beiden Ventilsitzen enthält, daß die Scheitel der Kegelflächen beider Ventilsitze und beider Ventilkegel einander zugewandt sind, und daß die Ventilsitze axial zwischen den Ventilkegeln angeordnet sind. Dergestalt ist ein kompakt aufbauender Hydrospeicher geschaffen und über die Endplatte des Metallbalges ist unmittelbar die Ansteuerung des Ventils im Hydraulikanschluß gegeben, so daß aufgrund des geringen zu beherrschenden Fluidvolumens im Metallbalg selbst neben der Gewichtsverringerung gegenüber bekannten Lösungen auch ein besonders gutes Ansprechverhalten gewährleistet ist. Ferner sind derart Überbelastungen des Metallbalges mit Sicherheit vermieden.
Wenn beim Betrieb des erfindungsgemäßen Druckspeichers einmal das Druck - Gleichgewicht zwischen Gas-Vorfülldruck im Gasraum und Hydraulikdruck im Ölraum hergestellt ist und die Endplatte des Metallbalges bei geöffnetem Ölventil sich zwischen ihren vorgegebenen Endstellungen befindet, dann bleibt dieser Betriebszustand des Druckausgleiches am Balg im Betrieb erhalten, ungeachtet dessen, wie stark der Hydraulikdruck der Ölseite gegenüber dem Gas - Vorfülldruck absinken mag, weil bei Erreichen der gewünschten Endstellung das Ventil schließt und der Abstrom aus dem Ölraum unterbrochen wird, und auch ungeachtet dessen, wie stark der Hydraulikdruck relativ zum Gas - Vorfülldruck ansteigen mag, weil bei Erreichen der diesbezüglichen Endstellung der Endplatte das Ventil wiederum geschlossen wird, so daß kein Zustrom zum Ölraum mehr möglich ist. Fig. 4 from PATENT ABSTRACTS OF JAPAN vol. 1996, no. 09, September 30, 1996, (1996-09-30) & JP 08 121401 A (NOK), May 14, 1996 (1996-05-14) is a generic hydropneumatic pressure accumulator known with a gas space and an oil space and a metal bellows separating these spaces, which has an end plate which can be moved in accordance with the volume changes from gas space to oil space. Inside the housing with the metal bellows is penetrated by a separating plate with a fluid connection which fluidly delimits the interior of the metal bellows with the interior of a further fluid space within the housing, the relevant additional fluid space leading fluidly outwards via a hydraulic connection on the bottom side of the housing is connected to parts of a hydraulic circuit. A valve tappet connected to the end plate of the metal bellows has a locking body, the two opposite sides of which are designed as valve cones and can be brought into contact with a valve seat, which is arranged on the separating plate, and once with a valve seat on the bottom-side hydraulic connection, which in Points towards the interior of the further fluid space. Both the valve cones mentioned and the valve seats point away from one another with the apices of their conical surfaces, a good sealing behavior being achieved via the conical surfaces. Because of the additional fluid space, the known device has a large structure and with regard to the fluid quantities to be moved in the metal bellows and additionally in the further fluid space, the actuation behavior for the valve is delayed, so that overloading of the metal bellows can occur, at least for a short time. Based on this prior art, the invention has for its object to provide a pressure accumulator of the type under consideration, in which overloads of the metal bellows during operation are avoided with certainty.
In a hydropneumatic pressure accumulator of the type mentioned, this object is achieved according to the invention in that the hydraulic connection contains the valve with its two valve seats, that the apex of the conical surfaces of both valve seats and both valve cones face each other, and that the valve seats are arranged axially between the valve cones , In this way, a compact hydraulic accumulator is created and the valve in the hydraulic connection is activated directly via the end plate of the metal bellows, so that due to the low fluid volume to be controlled in the metal bellows, in addition to the reduction in weight compared to known solutions, a particularly good response behavior is also ensured. Furthermore, overloading of the metal bellows is avoided with certainty.
If the pressure - equilibrium between the gas pre-filling pressure in the gas space and the hydraulic pressure in the oil space is established when the pressure accumulator according to the invention is in operation and the end plate of the metal bellows is between its predetermined end positions when the oil valve is open, then this operating state of the pressure compensation on the bellows remains in operation, regardless of how much the hydraulic pressure on the oil side may drop compared to the gas pre-filling pressure, because when the desired end position is reached the valve closes and the outflow from the oil chamber is interrupted, and also regardless of how much the hydraulic pressure increases relative to the gas pre-filling pressure likes, because when the relevant end position of the end plate is reached, the valve is closed again, so that an inflow to the oil space is no longer possible.

Nachstehend ist die Erfindung anhand von in der Zeichnung dargestellten Ausführungsbeispielen im einzelnen erläutert. Es zeigen:

Fig. 1
einen schematisch vereinfachten Längsschnitt eines Ausführungsbeispiels des Druckspeichers und
Fig. 2
einen der Fig. 1 ähnlichen Längsschnitt eines zweiten Ausführungsbeispieles.
The invention is explained in detail below on the basis of exemplary embodiments shown in the drawing. Show it:
Fig. 1
a schematically simplified longitudinal section of an embodiment of the pressure accumulator and
Fig. 2
a longitudinal section similar to FIG. 1 of a second embodiment.

Der in Fig. 1 gezeigte Druckspeicher weist ein als Ganzes mit 1 bezeichnetes Gehäuse mit einem im wesentlichen kreiszylinderförmigen Innenraum auf. Das Gehäuse 1 ist mit einem bodenseitigen Hydraulikanschluß 2 versehen und weist in seinem dem Hydraulikanschluß 2 entgegengesetzten Deckelteil 3 eine Gas-Füllöffnung auf, die durch einen Stopfen 5 verschlossen ist und es ermöglicht, durch Befüllen mit einem kompressiblen Gas im angrenzenden Gasraum 7 einen gewünschten Gas-Vorfülldruck herzustellen. Als Trennelement zwischen diesem Gasraum 7 und einem Ölraum 8, mit dem ein nicht gezeigtes Hydrauliksystem über den Hydraulikanschluß 2 in Verbindung ist, dient ein Metallbalg 9, der eine kreiszylindrische Form besitzt und am einen Ende durch eine Endplatte 11 abgeschlossen ist. Der Außendurchmesser des Balges 9 ist etwas geringer als der Innendurchmesser des Gehäuses 1. An seinem der Endplatte 11 entgegengesetzten, offenen Ende ist der Balg 9 mit dem Gehäuse 1 bei 13 dicht verschweißt, so daß der Balg 9 zusammen mit der Endplatte 11 ein dichtes Trennelement zwischen dem Ölraum 8 (das ist bei Fig. 1 der Innenraum des Balges 9) und dem Gasraum 7 bildet.The pressure accumulator shown in FIG. 1 has a one designated as a whole Housing with a substantially circular cylindrical interior on. The housing 1 is provided with a hydraulic connection 2 at the bottom and points in its opposite the hydraulic connection 2 Cover part 3 has a gas filling opening, which is closed by a plug 5 is and makes it possible, by filling with a compressible gas in the adjacent gas space 7 to produce a desired gas pre-filling pressure. As a separating element between this gas space 7 and an oil space 8, with which a hydraulic system, not shown, via the hydraulic connection 2 is in connection, a metal bellows 9, which has a circular cylindrical shape owns and is closed at one end by an end plate 11. The The outer diameter of the bellows 9 is slightly smaller than the inner diameter of the housing 1. At its open end opposite the end plate 11 End of the bellows 9 is tightly welded to the housing 1 at 13, so that the Bellows 9 together with the end plate 11 between a tight separator the oil space 8 (this is the interior of the bellows 9 in FIG. 1) and the gas space 7 forms.

Der Hydraulikanschluß 2 enthält ein doppeltwirkendes Ölventil 15 mit zwei Ventilsitzen 17 und 18, die jeweils durch Kegelflächen gebildet sind. Mit den Ventilsitzen 17, 18 wirken Sperrkörper in Form von Ventilkegeln 20 bzw. 21 zusammen, die an einem Ventilstößel 23 angebracht sind, der an der Innenseite der Endplatte 11 des Balges 9 befestigt und zusammen mit der Endplatte 11 bei deren Hubbewegungen in Richtung einer Längsachse 25 hin und her beweglich ist. Die auf die Längsachse 25 bezogenen axialen Abstände zwischen den Ventilsitzen 17 und 18 und den zugeordneten Ventilkegeln 20 bzw. 21 am Ventilstößel 23 sind so gewählt, daß bei einer vorgegebenen Hubweglänge, um die sich die Endplatte 11 in der Fig. 1 nach unten bewegt, wenn der Hydraulikdruck im Ölraum 8 geringer wird als der Gas-Vorfülldruck, der Ventilkegel 20 den Ventilsitz 17 erreicht, sobald die Endplatte 11 bei dieser Hubbewegung eine gewünschte Endstellung erreicht hat. Somit wird das Ölventil 15 gesperrt, so daß kein weiterer Ausstrom von Hydraulikflüssigkeit aus dem Ölraum 8 stattfindet, der Hydraulikdruck im Ölraum 8 somit konstant bleibt und sich bei dieser Endstellung der Endplatte 11 Druckgleichgewicht am Balg 9 einstellt.The hydraulic connection 2 contains a double-acting oil valve 15 two valve seats 17 and 18, which are each formed by conical surfaces. With the valve seats 17, 18 act blocking bodies in the form of valve cones 20 and 21 together, which are attached to a valve lifter 23, the attached to the inside of the end plate 11 of the bellows 9 and together with the end plate 11 during its lifting movements in the direction of a longitudinal axis 25 is movable back and forth. The related to the longitudinal axis 25 axial distances between the valve seats 17 and 18 and the associated Valve cones 20 and 21 on the valve lifter 23 are selected so that at a predetermined stroke length by which the end plate 11 in FIG. 1 moves down when the hydraulic pressure in the oil space 8 becomes lower as the gas pre-charge pressure, the valve plug 20 reaches the valve seat 17 as soon as the end plate 11 a desired end position during this stroke movement has reached. Thus, the oil valve 15 is blocked, so that no further Outflow of hydraulic fluid from the oil space 8 takes place, the hydraulic pressure in the oil chamber 8 thus remains constant and at this end position the end plate 11 adjusts the pressure balance on the bellows 9.

Bei durch Anstieg des Hydraulikdruckes bewirkter Hubbewegung in der entgegengesetzten Richtung (in Fig. 1 nach oben) kommt der Ventilkegel 21 zur Anlage am Ventilsitz 18, um bei Erreichen der diesbezüglichen Endstellung der Endplatte 11 das Ölventil 15 wiederum zu sperren, so daß der Zustrom von Hydraulikflüssigkeit zum Ölraum 8 unterbunden und somit wiederum Druckgleichgewicht am Balg 9 zwischen Ölraum 8 und Gasraum 7 hergestellt wird, um die entsprechende Endstellung der Endplatte 11 wiederum zu definieren.With lifting movement caused by an increase in hydraulic pressure in the in the opposite direction (upwards in FIG. 1) is the valve cone 21 to rest on the valve seat 18 to when the relevant end position is reached the end plate 11 to block the oil valve 15 again, so that the inflow prevented from hydraulic fluid to the oil chamber 8 and thus in turn Pressure equilibrium at bellows 9 between oil space 8 and gas space 7 is made to turn the corresponding end position of the end plate 11 define.

Bei dem Ausführungsbeispiel von Fig. 2 ist im Gegensatz zum Ausführungsbeispiel von Fig. 1 der Innenraum des Balges 9 dem Deckelteil 3 des Gehäuses 1 zugewandt, wo sich der Gasanschluß befindet. Somit bildet der Innenraum des Balges 9 den Gasraum 7, während die Außenseite des Balges 9 den Ölraum 8 begrenzt, in den der Hydraulikanschluß 2 mündet. Bei diesem Ausführungsbeispiel ist der Ventilstößel 23 des Ölventils 15 an der Außenseite der Endplatte 11 des Balges 9 befestigt. Die Funktionsweise ist die gleiche wie bei dem Beispiel von Fig. 1, d.h. bei Hubbewegungen der Endplatte 11 in beiden Richtungen entlang der Längsachse 25 kommen die Ventilkegel 20, 21 bei Erreichen der betreffenden Endstellung jeweils zur Anlage an den zugehörigen Ventilsitzen 17 bzw. 18, um die Zufuhr oder Abfuhr von Hydraulikflüssigkeit in den bzw. aus dem Ölraum 8 zu sperren und die entsprechenden Endstellungen der Endplatte 11 des Balges 9 zu definieren.In the embodiment of FIG. 2 is in contrast to the embodiment of Fig. 1, the interior of the bellows 9, the cover part 3 of the Housing 1 facing where the gas connection is located. Thus the Interior of the bellows 9, the gas space 7, while the outside of the bellows 9 limits the oil space 8 into which the hydraulic connection 2 opens. at In this embodiment, the valve lifter 23 of the oil valve 15 on the Outside of the end plate 11 of the bellows 9 attached. The way it works is the same as in the example of Fig. 1, i.e. when lifting the End plate 11 come in both directions along the longitudinal axis 25 Valve cone 20, 21 each when reaching the relevant end position System on the associated valve seats 17 and 18 to the supply or To block the discharge of hydraulic fluid into or from the oil space 8 and the corresponding end positions of the end plate 11 of the bellows 9 define.

Bei beiden Ausführungsbeispielen sind die Scheitel der Kegelflächen der Ventilkegel 20 und 21 einander zugekehrt, und die Ventilsitze 17 und 18 befinden sich axial zwischen den Ventilkegeln 20 und 21. In vorteilhafter Weise führt bei dieser Anordnung ein Druckgradient, wie er sich bei einem nicht vollkommenen Sperren des Ventils 15 am Balg 9 ergeben würde, zu einem entsprechenden Anstieg der Anpreßkraft zwischen Ventilkegeln 20 oder 21 an den zugehörigen Ventilsitzen 17 bzw. 18.In both embodiments, the apex of the conical surfaces are the Valve cones 20 and 21 facing each other, and valve seats 17 and 18 are located axially between the valve cones 20 and 21. Advantageously In this arrangement, a pressure gradient leads, as is the case with one would not result in complete locking of the valve 15 on the bellows 9, too a corresponding increase in the contact pressure between valve cones 20 or 21 on the associated valve seats 17 or 18.

In den Figuren sind die axialen Abstände der Ventilsitze 17, 18 des Ventiles 15 und der Ventilkegel 20 und 21 lediglich beispielhaft angegeben. Diese Abstände können nach Wunsch so gewählt werden, daß sich für die Endplatte 11 des Balges 9 im Betrieb eine gewünschte Arbeits-Hublänge zwischen den jeweils hydropneumatisch definierten Endstellungen ergibt.In the figures, the axial distances between the valve seats 17, 18 of the valve 15 and the valve cone 20 and 21 are only given as examples. This Distances can be chosen as desired so that there is enough space for the end plate 11 of the bellows 9 in operation a desired working stroke length between the hydropneumatically defined end positions.

Claims (4)

  1. Hydro-pneumatic pressure accumulator comprising a gas chamber (7) and oil chamber (8) surrounded by a housing (I) with a hydraulic connection (2) at the bottom and a metal bellows (9) with an end plate (11) separating these chambers, displaceable according to the volume changes in the gas chamber (7) and the oil chamber (8), provided with a valve (15) releasing or blocking the flow of hydraulic fluid from and to the oil chamber (8), and a valve tappet (23) controlling the valve, movable by the end plate (11) into a position locking the valve (15) during a motion of the end plate (11) which corresponds to an expansion of the volume of the gas chamber (7) exceeding a predetermined maximum value, whereby the valve tappet (23) is connected in a fixed manner with the end plate (11) of the metal bellows (9) and the valve (15) is blockable by the displacement of the valve tappet into two opposite blocking positions corresponding to the end positions of the end plate (11) of the metal bellows (9) at a predetermined maximum value or at a predetermined minimum volume of the gas chamber (7), whereby the valve (15) has two valve seats (17 and 18) offset in relation to each other in the axial direction corresponding to the direction of the displacement of the valve tappet (23), and the valve tappet (23) two blocking bodies (20, 21) which co-act in pairs to block the valve (15) as the valve tappet (23) moves into one or the other direction, and whereby the valve seats (17, 18) are designed as conical faces and the blocking bodies as valve cones (20, 21), characterised in that the hydraulic connection (2) contains the valve (15) with its two valve seats (17, 18), that the top of conical faces of the two valve seats (17, 18) and of the two valve cones (20, 21) are facing each other and that the valve seats (17, 18) are arranged axially between the valve cones (20, 21).
  2. Hydro-pneumatic pressure accumulator according to Claim 1, characterised in that the valve (15) controlling the flow of hydraulic fluid is arranged at the open end of the metal bellows (9) opposite to the end plate (11) so that the space within the metal bellows forms the oil chamber (8) through which the valve tappet (23) extends up to its point of attachment on the inside of the end plate (11).
  3. Hydro-pneumatic pressure accumulator according to Claim 1, characterised in that the metal bellows (9) with its end plate (11) faces the valve (15) controlling the flow of the hydraulic fluid so that the inside of the metal bellows (9) forms the gas chamber (7) and the oil chamber (8) is on the outside of the metal bellows (9) and its end plate (11) to which the valve tappet (23) is attached on the outside.
  4. Hydro-pneumatic pressure accumulator according to one of the Claims 1 to 3, characterised in that the axial spacing between the valve seats (17, 18) and between the blocking bodies (20, 21) provided on the valve tappet (23) is such that the end plate (11) connected to the valve tappet (23) can be displaced by the required stroke between its end positions with the valve (15) open, corresponding to the predetermined maximum value and the predetermined minimum value of the volume of the gas chamber (7).
EP00912582A 1999-05-29 2000-03-10 Hydropneumatic pressure accumulator Expired - Lifetime EP1181457B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19924807 1999-05-29
DE19924807A DE19924807A1 (en) 1999-05-29 1999-05-29 Hydropneumatic pressure accumulator
PCT/EP2000/002083 WO2000073663A1 (en) 1999-05-29 2000-03-10 Hydropneumatic pressure accumulator

Publications (2)

Publication Number Publication Date
EP1181457A1 EP1181457A1 (en) 2002-02-27
EP1181457B1 true EP1181457B1 (en) 2003-06-25

Family

ID=7909702

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00912582A Expired - Lifetime EP1181457B1 (en) 1999-05-29 2000-03-10 Hydropneumatic pressure accumulator

Country Status (6)

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US (1) US6527012B1 (en)
EP (1) EP1181457B1 (en)
JP (1) JP2003500614A (en)
AT (1) ATE243813T1 (en)
DE (2) DE19924807A1 (en)
WO (1) WO2000073663A1 (en)

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DE10233481A1 (en) * 2002-07-24 2004-02-12 Hydraulik-Ring Gmbh Storage for a liquid medium
DE10304288A1 (en) * 2002-10-24 2004-05-13 Continental Teves Ag & Co. Ohg Pressure medium accumulator has two shut-off components as toroidal seals in piston stem, whereby diameters of sealing lines of first and second shut-off components are the same
DE10249750B4 (en) * 2002-10-25 2014-11-06 Cummins Ltd. Compensation device for absorbing the volume expansion of media, in particular a urea-water solution, during freezing
DE10304999A1 (en) * 2003-02-07 2004-08-19 Carl Freudenberg Kg Metal bellows compression storage for motor vehicle hydraulic braking systems has a compression container with one chamber for compressed gas and another chamber for hydraulic fluid
US7108016B2 (en) * 2004-03-08 2006-09-19 The United States Of America As Represented By The Administrator Of The Environmental Protection Agency Lightweight low permeation piston-in-sleeve accumulator
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DE102008016354A1 (en) * 2007-08-28 2009-05-28 Continental Teves Ag & Co. Ohg Pressure reservoir for use in brake system of motor vehicle, has metal bellow cooperating with protection valve that is formed to prevent supply of fluid by closing supply opening during reaching preset deformation
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Also Published As

Publication number Publication date
JP2003500614A (en) 2003-01-07
ATE243813T1 (en) 2003-07-15
US6527012B1 (en) 2003-03-04
DE19924807A1 (en) 2000-12-07
EP1181457A1 (en) 2002-02-27
DE50002656D1 (en) 2003-07-31
WO2000073663A1 (en) 2000-12-07

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