EP1987254B1 - Pressure accumulator, in particular pulsation damper - Google Patents

Pressure accumulator, in particular pulsation damper Download PDF

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Publication number
EP1987254B1
EP1987254B1 EP06818509A EP06818509A EP1987254B1 EP 1987254 B1 EP1987254 B1 EP 1987254B1 EP 06818509 A EP06818509 A EP 06818509A EP 06818509 A EP06818509 A EP 06818509A EP 1987254 B1 EP1987254 B1 EP 1987254B1
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EP
European Patent Office
Prior art keywords
pressure accumulator
separating element
fluid
piston part
accumulator according
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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.)
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EP06818509A
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German (de)
French (fr)
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EP1987254A1 (en
Inventor
Markus Lehnert
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Hydac Technology GmbH
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Hydac Technology GmbH
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Publication of EP1987254A1 publication Critical patent/EP1987254A1/en
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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
    • 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
    • F15B1/021—Installations or systems with accumulators used for damping
    • 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
    • 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
    • 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

Definitions

  • Pressure accumulators are known, cf. DE 10 2004 004 341 A1 , Such accumulators are primarily used for damping pressure fluctuations in hydraulic systems in order to protect measuring and control devices, filters and other components integrated in the system from harmful pulsations.
  • a preferred field of use is the use as a pulsation damper in the injection system of internal combustion engines, especially large diesel engines on ships or in combined heat and power plants.
  • pressure fluctuations occur in both the fuel supply system and in the fuel return system, the frequency and severity of the pulsations being determined by the sequence of injection processes, the removal of fuel from the system, the compression, the injection by means of high-pressure injection pumps and the reopening connect to the system.
  • the invention has for its object to provide a pressure accumulator, which is characterized despite a compact design by a particularly good damping effect.
  • the choice of the depth of the "pot” allows an adjustment of the volume ratio of gas space to fluid space according to the respective working conditions.
  • the length of the metal bellows can be chosen to be sufficiently long, even in the case of a desirably small volume of the gas space, so that it has a multiplicity of folds. This ensures that the bellows is in the range of tolerable material stresses in the execution of alternating movements, so that he can perform the largest possible stroke with the largest possible number of repetitions, without the operational safety would be compromised.
  • the stopper may also be constituted by a structure whose structural elements are selected with a view to minimizing the restriction of the flow path caused by them.
  • a further retaining ring fixed on the inner wall of the tubular body and at least one further fastening rod spanning the interior of the retaining ring can be provided.
  • the two storage lids 11 have only one opening, namely inflow opening 15 and outflow opening 17, a large opening cross-section can be provided, so that large flow rates can be achieved.
  • the inner diameter of the tubular body 1 and the outer diameter of the metal bellows 21 are selected such that a sufficiently large annular space 51 is available as part of the flow path belonging to the fluid space 33.
  • the components of the support structure for the cover 27 are chosen so that no significant impediment to the flow path is given, d. H.
  • Both the retaining ring 35 and the mounting rod 39 are, as can be seen from the figures, slim, so that the outer edge of the lid 27 can be flowed around relatively unhindered.
  • the storage housing is formed by a simple tubular body 1 and the housing closure by means of the same trained storage lid 11, results in a particularly simple and inexpensive production.
  • the damper unit 19 can be prefabricated as a unit that can be used as a whole in the tubular body 1 and fixed by means of snap rings 37, 47, there is also a particularly simple installation.
  • the prefabricated as a unit damper unit exists in particular from the actual metal bellows 21, as well as the piston member 31 and the retaining ring 35th

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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)

Description

Die Erfindung betrifft einen Druckspeicher mit einem Speichergehäuse, das eine Längsachse definiert und eine Einströmöffnung und eine Ausströmöffnung für ein Fluid aufweist, wobei zwei Arbeitsräume, nämlich ein Gasraum für ein Arbeitsgas und ein Fluidraum, innerhalb des Speichergehäuses fluiddicht durch ein balgartiges Trennglied voneinander getrennt sind, wobei das Trennglied an seinem einen Ende mit einem einen gehäusefesten Abschluss des Gasraumes bildenden Deckel und an seinem anderen Ende mit einem im Speichergehäuse axial bewegbaren Kolbenteil verbunden ist, das einen beweglichen Abschluss des Gasraumes bildet, so dass Arbeitsbewegungen des Kolbenteiles Volumenänderungen der an das Trennglied angrenzenden Arbeitsräume bewirken, wobei Einströmöffnung und Ausströmöffnung jeweils an dem einen bzw. dem anderen der in Axialrichtung entgegengesetzten Enden des Speichergehäuses vorgesehen sind, wobei das Speichergehäuse ein kreiszylindrischer Rohrkörper ist, in dem das Trennglied konzentrisch unter Bildung eines Ringraums zwischen Innenwand des Rohrkörpers und Außenseite des Trennglieds aufgenommen ist.The invention relates to a pressure accumulator having a storage housing which defines a longitudinal axis and has an inflow opening and an outflow opening for a fluid, wherein two working spaces, namely a gas space for a working gas and a fluid space within the storage housing fluid-tightly separated by a bellows-type partition member, wherein the separating member is connected at its one end with a housing-tight completion of the gas space forming lid and at its other end with an axially movable piston housing in the storage housing, which forms a movable closure of the gas space, so that working movements of the piston part volume changes adjacent to the partition member Work spaces cause, wherein the inflow opening and outflow opening are respectively provided at the one and the other of the axially opposite ends of the storage housing, wherein the storage housing is a circular cylindrical tubular body, in which the partition member is concentrically received to form an annular space between the inner wall of the tubular body and the outer side of the partition member.

Ein derartiger Druckspeicher ist aus WO 2005/073564 A1 und JP02225802 bekannt. Bei dem bekannten Druckspeicher weist eine ringförmige Verlängerung des Deckelteils, das insoweit als Bestandteil des Speichergehäuses anzusehen ist, auf seiner Innenseite eine zylindrische Führungsfläche auf, innerhalb der das obere Ende des Kolbenteils längs verfahrbar unter Beibehalten eines Radialabstands in der Art eines Ringspalts geführt ist. Über den Ringspalt ist es möglich, dass die partielle Fluidfüllung im Arbeitsraum zwischen die gebildeten Hohlräume zwischen den Einzelfalten und dem Außenumfang des Kolbenteils tritt, um dergestalt bei den Bewegungen der Einzelfalten diese entsprechend abzustützen.Such an accumulator is off WO 2005/073564 A1 and JP02225802 known. In the known pressure accumulator, an annular extension of the cover part, which is to be regarded in this respect as part of the storage housing, on its inside a cylindrical guide surface, within the the upper end of the piston member is guided longitudinally movable while maintaining a radial distance in the manner of an annular gap. About the annular gap, it is possible that the partial fluid filling occurs in the working space between the cavities formed between the individual folds and the outer circumference of the piston member so as to support them in the movements of the individual folds.

Druckspeicher sind bekannt, vgl. DE 10 2004 004 341 A1 . Vorrangig werden derartige Druckspeicher zur Dämpfung von Druckschwankungen in Hydrauliksystemen eingesetzt, um Mess- und Regeleinrichtungen, Filter und andere im System integrierten Komponenten vor schädlichen Pulsationen zu schützen. Ein bevorzugtes Einsatzgebiet ist die Verwendung als Pulsationsdämpfer im Einspritzsystem von Verbrennungsmotoren, insbesondere großer Dieselmotoren auf Schiffen oder in Blockheizkraftwerken. Hierbei treten Druckschwankungen sowohl im Kraftstoff-Zulaufsystem als auch im Kraftstoff-Rücklaufsystem auf, wobei Frequenz und Ausprägung der Pulsationen durch die Folge von Einspritzvorgängen bestimmt ist, die das Entnehmen von Kraftstoff aus dem System, das Verdichten, das Einspritzen mittels Hochdruckeinspritzpumpen und das erneute Öffnen der Verbindung zum System umfassen. Bei einem 8-Zylinder Viertaktmotor beträgt diese Frequenz beispielsweise 40 Hz bei einer Drehzahl von 600 Umdrehungen/Minute. Je nach Eigenschaften des Systems, den vorgegeben Kraftstoffförderdrücken und der Funktionsweise der Hochdruckpumpen können Druckspitzen von mehr als 50 Bar auftreten.Pressure accumulators are known, cf. DE 10 2004 004 341 A1 , Such accumulators are primarily used for damping pressure fluctuations in hydraulic systems in order to protect measuring and control devices, filters and other components integrated in the system from harmful pulsations. A preferred field of use is the use as a pulsation damper in the injection system of internal combustion engines, especially large diesel engines on ships or in combined heat and power plants. In this case, pressure fluctuations occur in both the fuel supply system and in the fuel return system, the frequency and severity of the pulsations being determined by the sequence of injection processes, the removal of fuel from the system, the compression, the injection by means of high-pressure injection pumps and the reopening connect to the system. In an 8-cylinder four-stroke engine, this frequency is for example 40 Hz at a speed of 600 revolutions / minute. Depending on the characteristics of the system, the given fuel delivery pressures and the operation of the high-pressure pumps, pressure peaks of more than 50 bar may occur.

Da in derartigen Kraftstoffsystemen üblicher Weise Messeinrichtungen wie Viskosimeter, Temperaturmesser und dergleichen integriert sind, die für Druckschwankungen empfindlich sind, ist es wichtig, die Druckschwankungen zu beseitigen oder zumindest zu reduzieren.Since in such fuel systems conventionally measuring devices such as viscometers, thermometers and the like are integrated, which are sensitive to pressure fluctuations, it is important to eliminate or at least reduce the pressure fluctuations.

Im Hinblick hierauf liegt der Erfindung die Aufgabe zugrunde, einen Druckspeicher zu schaffen, der sich trotz kompakter Bauweise durch eine besonders gute Dämpferwirkung auszeichnet.In view of this, the invention has for its object to provide a pressure accumulator, which is characterized despite a compact design by a particularly good damping effect.

Erfindungsgemäß ist diese Aufgabe durch einen Druckspeicher gelöst, der die Merkmale des Patentanspruches 1 in seiner Gesamtheit aufweist. Gemäß dem kennzeichnenden Teil des Anspruches 1 besteht eine wesentliche erfinderische Besonderheit gegenüber dem Stande der Technik darin, dass das Speichergehäuse in seiner Längsachse und in der Richtung der Arbeitsbewegung des Kolbenteils vom Fluid durchströmbar ist, dass der Ringraum Teil eines Strömungsweges des Fluids zwischen Einströmöffnung und Ausströmöffnung bildet, dass der Deckel des Trennglieds an der Innenwand des Rohrkörpers über eine Tragstruktur fixiert ist, deren Strukturelemente im Hinblick auf eine Minimierung einer Drosselung am Strömungsweg zwischen Ringraum und benachbarter Ausströmöffnung ausgelegt sind, und dass die Tragstruktur einen an der Innenwand des Rohrkörpers fixierten Haltering aufweist, mit dem der Deckel des Trennglieds über sich vom Seitenrand des Deckels zum Haltering hin erstreckende Befestigungsstangen verbunden ist. Vorteilhafte Ausgestaltungen des erfindungsgemäßen Druckspeichers sind Gegenstände der Unteransprüche.According to the invention this object is achieved by a pressure accumulator having the features of claim 1 in its entirety. According to the characterizing part of claim 1, an essential inventive feature over the prior art is that the storage housing in its longitudinal axis and in the direction of the working movement of the piston member can be flowed through by the fluid, that the annular space is part of a flow path of the fluid between inflow and outflow forms that the lid of the partition member is fixed to the inner wall of the tubular body via a support structure, the structural elements are designed with a view to minimizing throttling at the flow path between annulus and adjacent outflow, and that the support structure has a fixed to the inner wall of the tubular body retaining ring with which the cover of the separating member is connected to fixing rods extending from the side edge of the lid to the retaining ring. Advantageous embodiments of the pressure accumulator according to the invention are subject matters of the subclaims.

Hieraus ergibt sich der Vorteil einer besonders einfachen und kostengünstigen Bauweise. Bei entsprechend schlanker Gestaltung von Haltering und Befestigungsstangen ergibt sich lediglich ein geringer Strömungswiderstand.This results in the advantage of a particularly simple and inexpensive construction. With correspondingly slim design of retaining ring and mounting rods only results in a low flow resistance.

Es ist eine In-Line-Bauweise verwirklicht ist, bei der beide Fluidanschlüsse, die Einströmöffnung und die Ausströmöffnung, auf einer Achse liegen. Gegenüber bekannten Lösungen, bei denen an einem Ende des Speichergehäuses ein Strömungsumlenkblock vorgesehen ist, an dem beide Fluidanschlüsse angeordnet sind und in dem innere Umlenkflächen einen Strömungsweg für einströmendes Fluid und ausströmendes Fluid vorgeben, ergibt sich eine geringere Baulänge und eine kompakte Bauweise. Die In-Line-Bauweise ermöglicht auch einen einfacheren und platzsparenderen Einbau. Wenn das Speichergehäuse beispielsweise eine zylindrische Form besitzt, erscheint der Druckspeicher nach dem Einbau wie ein Leitungszwischenstück, das sich lediglich im Durchmesser von der Basisleitung unterscheidet. Da bei In-Line-Einbau keine Biege-/Torsionsmomente vom Druckspeicher auf die Leitung ausgeübt werden, läßt sich möglicherweise die Anzahl von Befestigungselementen verringern.It is an in-line construction is realized, in which both fluid ports, the inlet opening and the outflow, lie on one axis. Across from known solutions in which at one end of the storage housing a Strömungsumlenkblock is provided, on which both fluid ports are arranged and specify in the inner deflection surfaces a flow path for incoming fluid and outflowing fluid, resulting in a smaller overall length and a compact design. The in-line design also allows easier and space-saving installation. For example, if the storage enclosure has a cylindrical shape, after installation, the accumulator will appear like a conduit interface that only differs in diameter from the base conduit. Since no bending / torsion moments are exerted by the pressure accumulator on the line during in-line installation, it may be possible to reduce the number of fastening elements.

Da an jedem Gehäuseende lediglich eine Öffnung vorhanden ist, sind besonders groß dimensionierte Fluidanschlüsse möglich, so dass wesentlich größere Durchflussmengen als beim Stand der Technik realisiert werden können. Diese führt, in Verbindung mit der Durchströmung des Speichergehäuses in dessen Längsrichtung zu der erstrebten Verbesserung der Dämpfungswirkung.Since only one opening is present at each end of the housing, particularly large-sized fluid connections are possible, so that substantially larger flow rates than in the prior art can be realized. This leads, in conjunction with the flow through the storage housing in its longitudinal direction to the desired improvement in the damping effect.

Vorzugsweise ist als Trennglied ein Metallbalg mit einer Vielzahl von übereinander angeordneten Falten oder Membranpaaren vorgesehen, der in seinem Innenraum den Gasraum zwischen Deckel und Kolbenteil begrenzt. Bei Verwendung eines derartigen Metallbalges treten praktisch keine Gasverluste auf. Bei Verwendung geeigneter Metalle, beispielsweise nicht rostendem Stahl, ergeben sich keinerlei Probleme durch aggressive Fluide wie Dieselöl, Schweröl oder biologische Kraftstoffe. Auch sind erhöhte Kraftstofftemperaturen nicht störend, da entsprechende metallische Werkstoffe für Temperaturen weit über 200° Celsius beständig sind. Da am Metallbalg Schweißverbindungen vorgesehen sind, ergibt sich ein gasdichter Abschluss ohne zusätzliche Dichtungen.Preferably, a metal bellows with a plurality of superimposed folds or membrane pairs is provided as the separating member, which limits the gas space between the lid and the piston part in its interior. When using such a metal bellows occur virtually no gas losses. When using suitable metals, such as stainless steel, there are no problems with aggressive fluids such as diesel oil, heavy oil or biofuels. Also, increased fuel temperatures are not annoying, since corresponding metallic materials are resistant to temperatures well above 200 ° Celsius. As the metal bellows Welded connections are provided, resulting in a gas-tight seal without additional seals.

Bei vorteilhaften Ausführungsbeispielen weist das Kolbenteil an seiner an den Fluidraum angrenzenden Seite einen das Volumen des Fluidraumes vergrößernden Hohlraum auf. Wenn hierbei die Anordnung so getroffen ist, dass das Kolbenteil topfförmig mit kreiszylinderförmiger Seitenwand ausgebildet ist, die sich in den kreiszylindrischen Innenraum des Metallbalges entlang der Innenseite von dessen Falten mit entsprechend der Arbeitsbewegungen des Kolbenteiles unterschiedlich großer Eintauchtiefe hinein erstreckt, geht die Vergrößerung des Volumens des Fluidraumes gleichzeitig mit einer Verringerung des Volumens des Gasraumes einher.In advantageous exemplary embodiments, the piston part has, on its side adjoining the fluid space, a cavity which increases the volume of the fluid space. If in this case the arrangement is such that the piston part is cup-shaped with a circular cylindrical side wall extending into the circular cylindrical interior of the metal bellows along the inside of its folds with correspondingly the working movements of the piston part of different sized immersion depth, the increase in the volume of the Fluid space simultaneously with a reduction in the volume of the gas space.

Hieraus ergeben sich mehrere Vorteile. Zum einen ermöglicht die Wahl der Tiefe des "Topfes" eine Anpassung des Volumenverhältnisses von Gasraum zu Fluidraum entsprechend den jeweiligen Arbeitsbedingungen. Zum anderen ergibt sich der besondere Vorteil, dass die Länge des Metallbalges auch bei wünschenswert kleinem Volumen des Gasraumes ausreichend lang gewählt sein kann, so dass er eine Vielzahl von Falten aufweist. Dadurch ist sichergestellt, dass sich der Balg bei der Ausführung alternierender Bewegungen im Bereich erträglicher Materialspannungen befindet, so dass er einen möglichst großen Hub mit einer möglichst großen Anzahl von Wiederholungen ausführen kann, ohne dass die Betriebssicherheit gefährdet wäre.This results in several advantages. On the one hand, the choice of the depth of the "pot" allows an adjustment of the volume ratio of gas space to fluid space according to the respective working conditions. On the other hand, there is the particular advantage that the length of the metal bellows can be chosen to be sufficiently long, even in the case of a desirably small volume of the gas space, so that it has a multiplicity of folds. This ensures that the bellows is in the range of tolerable material stresses in the execution of alternating movements, so that he can perform the largest possible stroke with the largest possible number of repetitions, without the operational safety would be compromised.

Schließlich ist dadurch, dass das Kolbenteil sich topfartig in den Innenraum des Metallbalges erstreckt, der Metallbalg von innen geführt und gestützt, so dass die Möglichkeiten einer angularen oder lateralen Auslenkung begrenzt sind, was den Metallbalg vor ungünstigen Betriebszuständen schützt und einen optimalen Bewegungsablauf gewährleistet.Finally, the fact that the piston part extends pot-like into the interior of the metal bellows, the metal bellows is guided and supported from the inside, so that limits the possibilities of an angular or lateral deflection are what protects the metal bellows from unfavorable operating conditions and ensures optimal movement.

Wenn hierbei der Innendurchmesser des Rohrkörpers in solchem Maße größer gewählt ist als der Außendurchmesser des Metallbalges dass der lichte Querschnitt des durch den Ringraum gebildeten Strömungsweges gleich oder größer als der lichte Querschnitt von Einströmöffnung und Ausströmöffnung ist, dann lassen sich möglichst große Fluid-Durchflußmengen ohne ins Gewicht fallende Drosselung realisieren.If in this case the inner diameter of the tubular body is chosen to be larger than the outer diameter of the metal bellows that the clear cross section of the flow path formed by the annulus equal to or greater than the clear cross section of inflow and outflow, then the largest possible fluid flow rates without ins Implement weight-reducing throttling.

Um die den Metallbalg ausziehende Arbeitsbewegung des Kolbenteiles zu begrenzen, wenn beispielsweise kein Fluid-Systemdruck vorhanden ist und der Gasraum mit dem Arbeitsgas vorgefüllt ist, ist eine Anschlageinrichtung für die Zusammenwirkung mit dem Kolbenteil vorhanden.In order to limit the metal bellows extracting working movement of the piston member, for example, if no fluid system pressure is present and the gas space is pre-filled with the working gas, a stop device for cooperation with the piston member is present.

In ähnlicher Weise wie bei der den Deckel des Trennglieds fixierenden Tragstruktur kann auch die Anschlageinrichtung durch eine Struktur gebildet sein, deren Strukturelemente im Hinblick auf die Minimierung der durch sie bewirkten Drosselung des Strömungsweges ausgewählt sind. Auch hierfür kann ein an der Innenwand des Rohrkörpers fixierter weiteren Haltering und zumindest eine den Innenraum des Halteringes überspannende weitere Befestigungsstange vorgesehen sein.In a manner similar to the support structure fixing the lid of the separator, the stopper may also be constituted by a structure whose structural elements are selected with a view to minimizing the restriction of the flow path caused by them. For this purpose, a further retaining ring fixed on the inner wall of the tubular body and at least one further fastening rod spanning the interior of the retaining ring can be provided.

Als Arbeitsgas, mit dem der Arbeitsraum vorgefüllt wird, kommt beispielsweise Stickstoffgas (N2) in Frage. Zusätzlich kann der Gasraum mit einer Zusatzmenge eines Alkohols, vorzugsweise Ethylenglykol, befüllt sein. Dadurch läßt sich das Volumen des Gasraumes zusätzlich zum Zweck einer Feineinstellung reduzieren. Bei entsprechend ausreichender Zusatzmenge des Alkohols ergibt sich eine Schutzfunktion für den Metallbalg, d.h. bevor das Kolbenteil, beispielsweise bei Überdruck im Fluidsystem, am Deckel des Metallbalges anschlägt, bildet sich zwischen Kolbenteil und Deckel ein schützendes Flüssigkeitspolster.As a working gas, with which the working space is pre-filled, for example nitrogen gas (N 2 ) comes into question. In addition, the gas space may be filled with an additional amount of an alcohol, preferably ethylene glycol. As a result, the volume of the gas space can be reduced in addition to the purpose of a fine adjustment. If the amount of alcohol added is sufficiently high, a protective function for the metal bellows results, ie before the piston part, for example, in case of overpressure in the fluid system, strikes the lid of the metal bellows, forms a protective fluid cushion between the piston part and the lid.

Nachstehend ist die Erfindung anhand eines in der Zeichnung dargestellten Ausführungsbeispieles im Einzelnen erläutert. Es zeigen:

  • Fig. 1 einen Längsschnitt eines Ausführungsbeispieles des erfindungsgemäßen Druckspeichers;
  • Fig. 2 eine perspektivische Schrägansicht lediglich der im Inneren des Speichergehäuses des Ausführungsbeispieles von Fig. 1 vorgesehenen Dämpfereinheit, gesehen im wesentlichen in der in Fig. 1 mit Pfeil II angegebenen Blickrichtung, und
  • Fig. 3 eine der Fig. 2 entsprechende, perspektivische Schrägansicht der Dämpfereinheit, jedoch gesehen im wesentlichen in der in Fig. 1 mit Pfeil III angegebenen Blickrichtung.
The invention with reference to an embodiment shown in the drawing will be explained in detail. Show it:
  • Fig. 1 a longitudinal section of an embodiment of the pressure accumulator according to the invention;
  • Fig. 2 an oblique perspective view only of the inside of the storage enclosure of the embodiment of Fig. 1 provided damper unit, seen substantially in the Fig. 1 indicated by arrow II, and
  • Fig. 3 one of the Fig. 2 corresponding perspective oblique view of the damper unit, but seen substantially in the in Fig. 1 with arrow III indicated direction.

Das in der Zeichnung dargestellte Ausführungsbeispiel des erfindungsgemäßen Druckspeichers, das als Pulsationsdämpfer einsetzbar ist, weist als Speichergehäuse einen kreiszylindrischen Rohrkörper 1 mit einer Längsachse 3 auf. Der Rohrkörper 1 weist an seiner Innenwand 5 schmale Ringnuten 7 als Sitz für unten zu beschreibende Sprengringe auf sowie je ein Innengewinde 9 an beiden Endbereichen. Mit diesen Innengewinden 9 ist an beiden Enden ein Speicherdeckel 11 verschraubt, die beide gleich ausgebildet und über jeweils ein Dichtelement 13 am Rohrkörper 1 abgedichtet sind. Der in der Figur links gelegene Speicherdeckel 11 weist eine zentrale Einströmöffnung 15 auf, während der in den Figur rechts gelegene Speicherdeckel 11 eine entsprechende Ausströmöffnung 17 für das Fluid aufweist, dessen Druckschwankungen gedämpft werden sollen.The illustrated in the drawing embodiment of the pressure accumulator according to the invention, which is used as a pulsation damper, has as a storage housing a circular cylindrical tubular body 1 with a longitudinal axis 3. The tubular body 1 has on its inner wall 5 narrow annular grooves 7 as a seat for below to be described snap rings and each an internal thread 9 at both end regions. With these internal threads 9, a storage lid 11 is screwed at both ends, both of which are of the same design and sealed by a respective sealing element 13 on the tubular body 1. The left in the figure memory cover 11 has a central inflow opening 15, while the right in the figure memory cover 11 has a corresponding outflow opening 17 for the fluid whose pressure fluctuations are to be damped.

In konzentrisch zur Längsachse 3 gelegener Anordnung befindet sich im Innenraum des Rohrkörpers 1 die in den Fig. 2 und 3 gesondert dargestellte Dämpfereinheit, die in den letzt genannten Figuren als Ganzes mit 19 bezeichnet ist. Wesentlicher Bestandteil der Dämpfereinheit ist als Trennglied ein Metallbalg 21 in Form eines Faltenbalges kreiszylindrischer Gestalt, der in Fig. 1 in voll ausgezogenem Zustand dargestellt ist, der dem größten Volumen des im Inneren des Metallbalges 21 befindlichen Gasraumes 23 entspricht. Anstelle eines Faltenbalges könnte auch ein nicht näher dargestellter Membranbalg zum Einsatz kommen, der anstelle von übereinander angeordneten Falten über dahingehend angeordnete Membranpaare verfügt. Zur Bildung eines gehäusefesten Abschlusses des Gasraumes 23 ist ein Ende 25 des Metallbalges 21 mit einem Deckel 27 verschweißt. An seinem anderen Ende 29 ist der Metallbalg 21 mit einem Kolbenteil 31 verschweißt, das einen beweglichen Abschluss des Gasraumes 23 bildet und im Speichergehäuse eine axiale Arbeitsbewegung ausführen kann, die zu Volumenänderungen des Gasraumes 23 und des die Dämpfereinheit 19 umgebenden Fluidraumes 33 führt.In concentric with the longitudinal axis 3 located arrangement is located in the interior of the tubular body 1 in the FIGS. 2 and 3 damper unit shown separately, which is designated in the last-mentioned figures as a whole by 19. An essential part of the damper unit is a metal bellows 21 in the form of a bellows circular-cylindrical shape as a separating member in Fig. 1 is shown in the fully extended state, which corresponds to the largest volume of the inside of the metal bellows 21 located gas space 23. Instead of a bellows, it would also be possible to use a membrane bellows, not shown in more detail, which has membrane pairs arranged in juxtaposition instead of folds arranged one above the other. To form a at the housing-tight completion of the gas space 23, one end 25 of the metal bellows 21 is welded to a cover 27. At its other end 29 of the metal bellows 21 is welded to a piston member 31 which forms a movable closure of the gas space 23 and can perform an axial working movement in the storage housing, which leads to volume changes of the gas space 23 and the damper unit 19 surrounding fluid space 33.

Der Deckel 27 ist über eine Tragstruktur an der Innenwand 5 des Rohrkörpers 1 fixiert. Diese Tragstruktur weist einen Haltering 35 auf, der mittels eines Sprengringes 37, der in der bereits erwähnten Ringnut 7 sitzt, gesichert ist. Der Haltering 35 wiederum ist über Befestigungsstangen 39 mit dem Seitenrand des Deckels 27 verbunden.The cover 27 is fixed to the inner wall 5 of the tubular body 1 via a support structure. This support structure has a retaining ring 35, which is secured by means of a snap ring 37 which sits in the already mentioned annular groove 7. The retaining ring 35 in turn is connected via attachment rods 39 to the side edge of the lid 27.

Wie aus Fig. 1 deutlich zu ersehen ist, hat das Kolbenteil 31 die Form eines Topfes, dessen kreiszylindrische Seitenwand 41 sich in den Innenraum des Metallbalges 21 hinein erstreckt, wobei die Eintauchtiefe in den Innenraum von der Kolbenstellung bei der Arbeitsbewegung des Kolbenteiles 31 abhängig ist. Wie erwähnt, hat das Kolbenteil 31 bei der Darstellung von Fig. 1 die dem größten Volumen des Gasraumes 23 entsprechende Endstellung, wobei das Kolbenteil 31 mit seinem offenen Topfrand an Stangen 43 anliegt, die Teil einer Anschlageinrichtung bilden. Diese Anschlageinrichtung ist durch eine ähnliche Struktur gebildet, wie sie auch als Tragstruktur für den Deckel 27 Verwendung findet, d. h. es ist ein Haltering 45 mittels eines Sprengringes 47 in der Ringnut 7 gesichert, wobei die Stangen 43 sich in ähnlicher Weise wie die Befestigungsstangen 39 am Haltering 35, sich vom Innenrand des Halteringes 45 erstrecken.How out Fig. 1 can be clearly seen, the piston member 31 has the shape of a pot, the circular cylindrical side wall 41 extends into the interior of the metal bellows 21, wherein the immersion depth in the interior of the piston position in the working movement of the piston member 31 is dependent. As mentioned, the piston member 31 in the illustration of Fig. 1 the largest volume of the gas space 23 corresponding end position, the piston member 31 rests with its open pot edge of rods 43, which form part of a stop device. This stop device is formed by a similar structure, as it is also used as a support structure for the cover 27, ie a retaining ring 45 is secured by means of a snap ring 47 in the annular groove 7, wherein the rods 43 in a similar manner as the mounting rods 39 on Retaining ring 35, extending from the inner edge of the retaining ring 45.

Der Deckel 27 weist einen zentralen Füllanschluss 49 auf, über den der Gasraum 23 mit einer Vorfüllung versehen werden kann, die aus dem Arbeitsgas, namentlich N2, sowie einer Zusatzmenge aus einem Alkohol, vorzugsweise Ethylenglykol, besteht.The lid 27 has a central filling port 49, via which the gas space 23 can be provided with a pre-filling, which consists of the working gas, namely N 2 , and an additional amount of an alcohol, preferably ethylene glycol.

Da die beiden Speicherdeckel 11 lediglich eine Öffnung aufweisen, nämlich Einströmöffnung 15 bzw. Ausströmöffnung 17, kann ein großer Öffnungsquerschnitt vorgesehen sein, so dass große Durchflussmengen erreicht werden können. Damit ein großer Volumenstrom ohne merkliche Drosselung das Speichergehäuse durchströmen kann, sind der Innendurchmesser des Rohrkörpers 1 und der Außendurchmesser des Metallbalges 21 so gewählt, dass ein ausreichend großer Ringraum 51 als Teil des zum Fluidraum 33 gehörenden Strömungsweges zur Verfügung steht. Im Hinblick hierauf sind auch die Bauelemente der Tragstruktur für den Deckel 27 so gewählt, dass keine wesentliche Behinderung des Strömungsweges gegeben ist, d. h. sowohl der Haltering 35 als auch die Befestigungsstange 39 sind, wie aus den Figuren entnehmbar, schlank ausgebildet, so dass der äußere Rand des Deckels 27 verhältnismäßig ungehindert umströmt werden kann. Entsprechendes gilt für die Gestaltung der Anschlageinrichtung für das Kolbenteil 31, die mit schlank ausgebildetem Haltering 45 und schlanken Stangen 43 keinen beachtlichen Strömungswiderstand bildet.Since the two storage lids 11 have only one opening, namely inflow opening 15 and outflow opening 17, a large opening cross-section can be provided, so that large flow rates can be achieved. In order for a large volume flow to flow through the accumulator housing without appreciable throttling, the inner diameter of the tubular body 1 and the outer diameter of the metal bellows 21 are selected such that a sufficiently large annular space 51 is available as part of the flow path belonging to the fluid space 33. In view of this, the components of the support structure for the cover 27 are chosen so that no significant impediment to the flow path is given, d. H. Both the retaining ring 35 and the mounting rod 39 are, as can be seen from the figures, slim, so that the outer edge of the lid 27 can be flowed around relatively unhindered. The same applies to the design of the stopper for the piston member 31, which forms a slender trained retaining ring 45 and slender rods 43 is not a considerable flow resistance.

Dadurch, dass das Speichergehäuse durch einen einfachen Rohrkörper 1 gebildet ist und der Gehäuseabschluss mittels gleich ausgebildeter Speicherdeckel 11 erfolgt, ergibt sich eine besonders einfache und kostengünstige Herstellung. Da die Dämpfereinheit 19 als Baueinheit vorgefertigt werden kann, die als Ganzes in den Rohrkörper 1 eingesetzt und mittels Sprengringen 37, 47 fixiert werden kann, ergibt sich auch eine besonders einfache Montage. Die als Baueinheit vorgefertigte Dämpfereinheit besteht dabei insbesondere aus dem eigentlichen Metallbalg 21, sowie dem Kolbenteil 31 und dem Haltering 35.The fact that the storage housing is formed by a simple tubular body 1 and the housing closure by means of the same trained storage lid 11, results in a particularly simple and inexpensive production. Since the damper unit 19 can be prefabricated as a unit that can be used as a whole in the tubular body 1 and fixed by means of snap rings 37, 47, there is also a particularly simple installation. The prefabricated as a unit damper unit exists in particular from the actual metal bellows 21, as well as the piston member 31 and the retaining ring 35th

Bei entsprechender Vorfüllmenge besteht eine Schutzfunktion für den Metallbalg 21, d.h. bevor das Kolbenteil 31 mit seiner freien Stirnseite an der zugewandten Fläche des Deckels 27 des Halteringes 35 anstößt, bildet sich zwischen den genannten Teilen eine Flüssigkeitsschicht. Hierdurch ist ausgeschlossen, dass auch ein weiterhin ansteigender Druck den Metallbalg 21 radial zusammendrücken könnte.With a corresponding pre-charge amount, there is a protective function for the metal bellows 21, i. before the piston member 31 abuts with its free end face on the facing surface of the lid 27 of the retaining ring 35, a liquid layer is formed between said parts. This excludes that even a further increasing pressure could compress the metal bellows 21 radially.

Im mit Gas vorgefüllten Zustand stützt sich das Kolbenteil 31 auf der Anschlageinrichtung 43 mit ihren Befestigungsstäben ab und der Metallbalg 21 befindet sich insoweit dann in seiner maximalen Streckung. In diesem Zustand ist er so ausgelegt, dass er dem inneren Gasvorfülldruck auf jedenfall Stand halten kann. In allen weiteren Betriebszuständen befindet sich der Metallbalg 21 in einem weitestgehend druckausgeglichenen Zustand. Er wird sich in Abhängigkeit des Systemdruckes und der in ihm herrschenden Gastemperatur zwischen dem unteren und oberen Extrempunkt befinden fähig alle Druckschwankungen für die er ausgelegt ist durch Flüssigkeitsaufnahme und -abgabe zu dämpfen bzw. zu eliminieren. Das dahingehende Arbeitsprinzip entspricht dann dem eines klassischen hydropneumatischen Druckspeichers im Dämpfereinsatz.In the pre-filled with gas state, the piston member 31 is supported on the stopper 43 with its mounting rods and the metal bellows 21 is so far in its maximum extension. In this condition, it is designed to withstand the internal gas pre-charge pressure in any case. In all other operating conditions, the metal bellows 21 is in a largely pressure-balanced state. Depending on the system pressure and the prevailing gas temperature between the lower and upper extreme point, it will be able to damp or eliminate any pressure fluctuations for which it is designed to absorb or dispense liquid. The working principle then corresponds to that of a classic hydropneumatic pressure accumulator in the damper insert.

Die Anschlageinrichtung 43 mit ihren Befestigungsstäben dient dem Abstützen des Kolbenteils 31 soweit der Systemdruck unter den Vorfülldruck im Inneren der Metallbalg-Baugruppe, gebildet aus den Komponenten Metallbalg 21, Kolbenteil 31, Haltering 35 sowie (Gas-)Füllanschluß fällt, was beispielsweise beim Vorfüllen des Metallbalgspeichers 21 mit Stickstoff geschehen kann. Das Abstützen der freien Stirnseite des Kolbenteils 31 ermöglicht einen freien Durchfluß der Speichereinrichtung, auch wenn der Systemdruck kleiner sein sollte als der Vorfülldruck; das Kolbenteil 31 kann dabei jedenfalls nicht die Fluidöffnung 15 im Deckel 11 versperren.The stop device 43 with its mounting rods serves to support the piston member 31 as far as the system pressure below the Vorfülldruck inside the metal bellows assembly formed from the components metal bellows 21, piston member 31, retaining ring 35 and (gas) Füllanschluß falls, which for example during the pre-filling of Metal bellows memory 21 can be done with nitrogen. The support of the free end face of the piston member 31 allows a free flow of the storage device, even if the system pressure should be less than the pre-charge pressure; In any case, the piston part 31 can not obstruct the fluid opening 15 in the cover 11.

Claims (12)

  1. A pressure accumulator
    - comprising an accumulator housing (1) that defines a longitudinal axis (3) and has an inflow opening (15) and an outflow opening (17) for a fluid,
    - two working chambers, namely a gas chamber (23) for a working gas and a fluid chamber (33), within the accumulator housing (1) are separated fluid-tight from one another by a bellows-like separating element (21),
    - the separating element (21) being connected on its one end (25) to a cover (27) forming a housing-mounted termination of the gas chamber (23), and on its other end (29) to a piston part (31) which is axially moveable in the accumulator housing (1) and which forms a moveable termination of the gas chamber (23) so that working movements of the piston part (31) cause volume changes of the working chambers which border the separating element (21),
    - the inflow opening (15) and the outflow opening (17) respectively being provided on ends of the accumulator housing (1) opposite the one or the other of the ends in the axial direction,
    - the accumulator housing being a circular cylindrical tubular body (1) in which the separating element (21) is accommodated concentrically such as to form an annular space (51) between the inside wall (5) of the tubular body (1) and the outer side of the separating element (21),
    - characterised in that fluid can flow through the accumulator housing (1) in its longitudinal direction and in the direction of the working movement of the piston part (31),
    - that the annular space (51) forms part of a flow path of the fluid between the inflow opening (15) and the outflow opening (17),
    - that the cover (27) of the separating element (21) is fixed on the inside wall (5) of the tubular body (1) by a support structure (35, 39), the structure elements of which are designed in view of minimising throttling on the flow path between the annular space (51) and the adjacent outflow opening (17), and
    - that the support structure has a retaining ring (35) fixed on the inside wall of the tubular body (35) and to which the cover (27) of the separating element (21) is connected by means of fastening rods (39) extending from the side edge of the cover (27) to the retaining ring (35).
  2. The pressure accumulator according to Claim 1, characterised in that the separating element is a metal bellows (21) with a plurality of folds or membrane pairs located over one another and which in its interior borders the gas chamber between the cover (27) and the piston part (31).
  3. The pressure accumulator according to Claim 2, characterised in that the piston part (31) on its side bordering the fluid chamber (33) has a cavity which enlarges the volume of the fluid chamber.
  4. The pressure accumulator according to Claim 3, characterised in that the piston part (31) is made cup-shaped with a circular cylindrical side wall (41) which extends into the circularly cylindrical interior of the metal bellows (21) along the inside of its folds with an immersion depth of varied magnitude according to the working movements of the piston part (31).
  5. The pressure accumulator according to any of the preceding claims, characterised in that the inside diameter of the tubular body (1) is selected to be larger than the outside diameter of the separating element (21) to such a degree that the clear cross-section of the flow path formed by the annular space (51) is equal to or greater than the clear cross-section of the inflow opening (15) and the outflow opening (17).
  6. The pressure accumulator according to any of the preceding claims, characterised in that there is a stop means (43, 45) for limiting the working movement of the piston part (31) which enlarges the volume of the gas chamber (23).
  7. The pressure accumulator according to Claim 6, characterised in that the stop means (43, 35) is formed by a structure the structural elements of which are chosen in view of minimising the throttling of the flow path between the inflow opening (15) and the annular space (51).
  8. The pressure accumulator according to Claim 6 or 7, characterised in that the stop means is formed by a further retaining ring (45) which is fixed on the inside wall (5) of the tubular body (1) and by at least one further fastening rod (43) which extends between regions of the retaining ring (45) which are essentially opposite one another.
  9. The pressure accumulator according to any of the preceding claims, characterised in that the gas chamber (23) is filled with an alcohol in addition to being filled with working gas.
  10. The pressure accumulator according to Claim 9, characterised in that the alcohol is ethylene glycol.
  11. The pressure accumulator according to any of the preceding claims, characterised in that the gas chamber (23) and the fluid chamber (33) are separated from one another gas-tight by the separating element (21).
  12. The pressure accumulator according to any of the preceding claims, characterised in that the pressure accumulator is a pulsation damper.
EP06818509A 2006-02-22 2006-11-14 Pressure accumulator, in particular pulsation damper Not-in-force EP1987254B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006008175A DE102006008175A1 (en) 2006-02-22 2006-02-22 Flow pulsation damper for e.g. vehicle fuel injection systems, comprises cylindrical casing passing flow from one end to the other, around gas-filled bellows
PCT/EP2006/010885 WO2007098795A1 (en) 2006-02-22 2006-11-14 Pressure accumulator, in particular pulsation damper

Publications (2)

Publication Number Publication Date
EP1987254A1 EP1987254A1 (en) 2008-11-05
EP1987254B1 true EP1987254B1 (en) 2012-09-12

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EP06818509A Not-in-force EP1987254B1 (en) 2006-02-22 2006-11-14 Pressure accumulator, in particular pulsation damper

Country Status (8)

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US (1) US8176940B2 (en)
EP (1) EP1987254B1 (en)
JP (1) JP5074426B2 (en)
KR (1) KR101304186B1 (en)
CN (1) CN101384824B (en)
DE (1) DE102006008175A1 (en)
DK (1) DK1987254T3 (en)
WO (1) WO2007098795A1 (en)

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CN104265700A (en) * 2014-09-15 2015-01-07 邢宇 Novel technology for replacing liner pressure accumulator and piston pressure accumulator by metal bellows pressure accumulator
EP3306109B1 (en) * 2015-05-29 2022-04-27 Eagle Industry Co., Ltd. Metal bellows-type accumulator
DE102016003153A1 (en) * 2016-03-15 2017-09-21 Hydac Technology Gmbh Storage device and hydropneumatic suspension
FR3060533A1 (en) * 2016-12-19 2018-06-22 Safran Aircraft Engines ACCUMULATOR ON AN AIRCRAFT FUEL LINE
CN107939834A (en) * 2017-11-16 2018-04-20 中国航空工业集团公司北京航空精密机械研究所 A kind of ultra-precision machine tool hydraulic system of surge suppressing
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Publication number Publication date
CN101384824B (en) 2011-01-12
EP1987254A1 (en) 2008-11-05
US8176940B2 (en) 2012-05-15
JP2009527706A (en) 2009-07-30
WO2007098795A1 (en) 2007-09-07
DK1987254T3 (en) 2012-10-01
CN101384824A (en) 2009-03-11
KR101304186B1 (en) 2013-09-06
JP5074426B2 (en) 2012-11-14
US20100307146A1 (en) 2010-12-09
DE102006008175A1 (en) 2007-08-23
KR20090035464A (en) 2009-04-09

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