EP0105152B1 - Hydraulic accumulator for supplying a pressure fluid - Google Patents

Hydraulic accumulator for supplying a pressure fluid Download PDF

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Publication number
EP0105152B1
EP0105152B1 EP83108104A EP83108104A EP0105152B1 EP 0105152 B1 EP0105152 B1 EP 0105152B1 EP 83108104 A EP83108104 A EP 83108104A EP 83108104 A EP83108104 A EP 83108104A EP 0105152 B1 EP0105152 B1 EP 0105152B1
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EP
European Patent Office
Prior art keywords
piston
hydraulic accumulator
pressure
cylinder
accumulator according
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
Application number
EP83108104A
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German (de)
French (fr)
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EP0105152A1 (en
Inventor
Gerhard Körner
Edelwald Lutz
Horst Ing. Grad. Plettner
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
BBC Brown Boveri AG Switzerland
BBC Brown Boveri AG Germany
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BBC Brown Boveri AG Switzerland
Brown Boveri und Cie AG Germany
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Publication of EP0105152A1 publication Critical patent/EP0105152A1/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
    • 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
    • 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

Definitions

  • the invention relates to a hydraulic accumulator for providing pressure fluid for a hydraulic system, in particular for actuating a medium or high voltage circuit breaker, with a cylinder in which a piston is movable, on one side of which the pressure fluid is located, the piston being replaced by one of several , spring arrangement formed on a circle of uniformly distributed tension or compression springs is applied to generate the pressure in the pressure fluid.
  • a hydraulic accumulator of the type mentioned is known from US-A-4 046 167.
  • this hydraulic accumulator there is a piston-cylinder arrangement within a housing, in which the cylinder is pressed against the piston by means of pressure springs distributed evenly around the circumference.
  • the high-pressure area with the high-pressure fluid is located between the piston crown located inside the cylinder and the inner surface of the cylinder.
  • the compression springs act directly on the cylinder and for this reason there is the problem that the energy stored in the compression springs exerts a different force on the cylinder depending on the tension state of the compression springs.
  • a first switch-off, a switch-on and a second switch-off can be carried out. At the first and the second switch-off, the pressure should be the same, so that the switching speed is approximately the same.
  • the object of the invention is therefore to provide a hydraulic accumulator of the type mentioned at the outset, in which the pressure within the pressure fluid can be kept approximately constant over a wide spring range.
  • tension or compression springs act on one end of a rocker arm which is mounted rotatably or pivotably approximately in its center, the other, inner end of which acts on the piston.
  • the particular advantages of the hydraulic accumulator according to the invention are that changes in the pressure in the pressure fluid, such as can occur in gas pressure accumulators due to leakage and because of the temperature dependence of the gas or in the hydraulic accumulator according to US Pat. No. 4,046,167 due to the spring characteristics, can be avoided .
  • the amount of pressurized fluid need not be greater than is necessary in order to have a sufficient amount of pressurized fluid with sufficient pressure available, for example in the case of a high-pressure circuit breaker, even when switched off for the second time.
  • a cylinder 74 which is tubular, is screwed onto a base plate 70 by means of screw connections 72. Inside the cylinder 74, a piston 76 is movable back and forth. In the base plate 70 there is an outlet opening 78 which is connected to the hydraulic system.
  • the high-pressure chamber 80 is located between the base plate 70, the cylinder 74 and the piston 76.
  • a piston rod 82 is fastened to the piston on the side of the piston 76 opposite the high-pressure chamber.
  • a container 84 is fastened on the end face of the cylinder opposite the base plate 70 by means of a screw connection 86 and has an outer wall 88 and an inner wall 90, the inner wall covering only approximately half of the outer wall 88.
  • the inner wall 90 is covered by a cover 92 with a through opening 94.
  • the outer wall 88 is closed at the top by means of an end cover 96.
  • calmed oil with low pressure whereas outside the cover 92, but still within the space formed by the outer wall 88 and the end cover 96, there is oil foamed with low pressure.
  • the piston rod 82 seals through the cover 96; at its upper end a support ring 98 is firmly attached, for example by means of a screw connection.
  • This support ring 98 has on its side opposite the piston rod a pin 100 which is guided in a bore 102 of a cross member 106 which is fixedly connected to the base plate 70 by means of bolts 104.
  • a radially extending support surface 108 is located on the support ring 98.
  • the base plate 70 has recesses 110 distributed around the circumference, which serve for the passage of a tube 112. Above the base plate, a support plate 120 is supported on two bearing bolts 122 on the base plate.
  • a support 124 At the upper end of the rod 112 there is a support 124, to which a tab 126 is attached, which is penetrated by a bolt 128 with which it is articulated on a double-arm lever 130.
  • a plate spring assembly consisting of a number of plate springs 132. From FIG. 2 it can be seen that a total of six such plate spring constructions and six double-arm levers 130 are arranged on the circumference.
  • the double arm lever 130 is articulated on an extension 134 on the cross member via an axis 136.
  • the inner end of the double arm lever has a spherical shape 138 which rests on the surface 108.
  • the plate 124 is slidable against the plate 120 so that the plate springs 132 can be tensioned (see left of the center line) or relaxed (see right of the center line of FIG. 1).
  • the plate spring assemblies 132 can be pivoted in the double arrow direction T due to their support in the bearing pin 122, as can be seen from the arrangement of the two plate springs to the left and right of the central axis.
  • the arrangement on the left side of the center line is in the cocked state, i.e. the piston is in the position in which the accumulator is completely filled with pressurized fluid.
  • pressure oil is drawn off or extracted through the opening or the passage 76, the piston moves downwards under the pressure of the springs 132, whereby the plate spring assemblies at their upper end with their axis 128 swivel outwards; due to the increased leverage, the reduction in spring force is compensated for upon further relaxation, so that the leverage of the double-arm lever 130 keeps the pressure in the fluid approximately constant.
  • coil springs can also be used.
  • a relief valve 140 is accommodated in the piston 76, which extends through the piston 76 with a valve rod 142 and projects beyond it on the side opposite the high-pressure chamber 80.
  • the valve rod 142 abuts against a boundary surface 144 on the low pressure container 84, 88, 90 and 96 and opens the relief valve 140, so that a passage from the high pressure chamber 80 to the low pressure chamber is released.

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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)
  • Actuator (AREA)
  • Driving Mechanisms And Operating Circuits Of Arc-Extinguishing High-Tension Switches (AREA)

Description

Die Erfindung betrifft einen Hydrospeicher zur Bereitstellung von Druckfluid für eine hydraulische Anlage, insbesondere zur Betätigung eines Mittel- oder Hochspannungsleistungsschalters, mit einem Zylinder, in dem ein Kolben bewegbar ist, auf dessen einer Seite sich das Druckfluid befindet, wobei der Kolben durch eine aus mehreren, auf einem Kreis gleichmäßig verteilten Zug- oder Druckfedern gebildete Federanordnung zur Erzeugung des Druckes im Druckfluid beaufschlagt ist.The invention relates to a hydraulic accumulator for providing pressure fluid for a hydraulic system, in particular for actuating a medium or high voltage circuit breaker, with a cylinder in which a piston is movable, on one side of which the pressure fluid is located, the piston being replaced by one of several , spring arrangement formed on a circle of uniformly distributed tension or compression springs is applied to generate the pressure in the pressure fluid.

Ein Hydrospeicher der eingangs genannten Art ist aus der US-A-4 046 167 bekannt geworden. Bei diesem Hydrospeicher befindet sich innerhalb eines Gehäuses eine Kolben-Zylinderanordnung, bei der der Zylinder mittels gleichmäßig am Umfang verteilter Druckfedern gegen den Kolben gedrückt wird. Zwischen dem im Inneren des Zylinders befindlichen Kolbenboden und der Zylinderinnenfläche befindet sich der Hochdruckbereich mit dem Hochdruckfluid.A hydraulic accumulator of the type mentioned is known from US-A-4 046 167. In this hydraulic accumulator there is a piston-cylinder arrangement within a housing, in which the cylinder is pressed against the piston by means of pressure springs distributed evenly around the circumference. The high-pressure area with the high-pressure fluid is located between the piston crown located inside the cylinder and the inner surface of the cylinder.

Bei der bekannten Einrichtung wirken die Druckfedern unmittelbar auf den Zylinder und aus diesem Grunde besteht das Problem, daß die in den Druckfedern gespeicherte Energie je nach Spannungszustand der Druckfedern eine unterschiedliche Kraft auf den Zylinder ausübt. Je weniger Druckfluid sich in dem Hochdruckraum befindet, je entspannter also die Druckfedern sind, desto geringer ist der Druck im Druckfluid, was bei bestimmten Anwendungsfällen, insbesondere bei Leistungsschaltern, bei denen bestimmte Schaltfolgen durchgeführt werden, nachteilig ist. Bei Hochspannungsleistungsschaltern beispielsweise muß innerhalb einer kurzen Zeit von ca. 300 msec. eine erste Ausschaltung, eine Einschaltung und eine zweite Ausschaltung durchgeführt werden können. Bei der ersten und der zweiten Ausschaltung sollte der Druck gleich groß sein, damit die Schaltgeschwindigkeit angenähert gleich ist. Bei der Hydraulikspeicheranordnung nach der US-A- 4 046 167 ist dies wegen der Federcharakteristiken der Druckfeder nicht ohne weiters zu erreichen, und aus diesem Grunde ist es erforderlich, den Druck im Inneren des Zylinders höher einzustellen, damit auch ein ausreichender Druck bei der zweiten Ausschaltung bereitgestellt wird.In the known device, the compression springs act directly on the cylinder and for this reason there is the problem that the energy stored in the compression springs exerts a different force on the cylinder depending on the tension state of the compression springs. The less pressure fluid there is in the high-pressure chamber, the more relaxed the pressure springs are, the lower the pressure in the pressure fluid, which is disadvantageous in certain applications, in particular in circuit breakers, in which certain switching sequences are carried out. In the case of high-voltage circuit breakers, for example, a short time of approx. 300 msec. a first switch-off, a switch-on and a second switch-off can be carried out. At the first and the second switch-off, the pressure should be the same, so that the switching speed is approximately the same. In the hydraulic accumulator arrangement according to US-A-4 046 167, this is not easily achieved because of the spring characteristics of the compression spring, and for this reason it is necessary to set the pressure inside the cylinder higher, so that a sufficient pressure in the second Deactivation is provided.

Aufgabe der Erfindung ist es daher, einen Hydrospeicher der eingangs genannten Art zu schaffen, bei dem der Druck innerhalb des Druckfluids über einen weiten Federbereich annähernd konstant gehalten werden kann.The object of the invention is therefore to provide a hydraulic accumulator of the type mentioned at the outset, in which the pressure within the pressure fluid can be kept approximately constant over a wide spring range.

Diese Aufgabe wird erfindungsgemäß dadurch gelöst, daß die Zug- bzw. Druckfedern an einem Ende eines annähernd in seiner Mitte dreh- bzw. schwenkbar gelagerten Kipphebel angreifen, dessen anderes, inneres Ende auf den Kolben einwirkt.This object is achieved in that the tension or compression springs act on one end of a rocker arm which is mounted rotatably or pivotably approximately in its center, the other, inner end of which acts on the piston.

Durch die mechanische Anordnung von Kipphebel zu den Federn und dem Kolben wird ein Drehmomentenausgleich erzielt, indem nämlich der wirksame Hebel der Kipphebel entsprechend der Stellung der Federn bzw. dem Spannungszustand der Federn durch Verschwenken der Kipphebel verkleinert oder vergrößert wird. Weitere vorteilhafte Ausgestaltungen der Erfindung sind den Unteransprüchen zu entnehmen. Gemäß kennzeichnenden Merkmalen des Anspruches 2 wird eine günstige Anordnung der Kipphebel erreicht und mit den kennzeichnenden Merkmalen des Anspruches 3 werden Gleit- bzw. Rutschvorgänge der Kipphebel auf dem Kolben vermieden.Due to the mechanical arrangement of the rocker arms to the springs and the piston, a torque compensation is achieved, namely that the effective lever of the rocker arms is reduced or enlarged in accordance with the position of the springs or the tension state of the springs by pivoting the rocker arms. Further advantageous embodiments of the invention can be found in the subclaims. According to the characterizing features of claim 2, a favorable arrangement of the rocker arms is achieved and with the characterizing features of claim 3 sliding or sliding operations of the rocker arms on the piston are avoided.

Es besteht dabei die Möglichkeit, auf die Kipphebel sowohl jeweils eine Druckfeder als auch eine Zugfeder einwirken zu lassen. Die Verwendung von Druckfedern ist bei der erfindungsgemäßen Ausgestaltung insoweit günstig, als die Baugröße des Hydrospeichers relativ klein gehalten werden kann, was bei Zugfedern nicht der Fall ist.It is possible to have both a compression spring and a tension spring act on the rocker arms. The use of compression springs is advantageous in the embodiment according to the invention insofar as the size of the hydraulic accumulator can be kept relatively small, which is not the case with tension springs.

Die besonderen Vorteile des erfindungsgemäßen Hydrospeichers bestehen darin, daß Anderungen des Druckes im Druckfluid, wie sie beispielsweise bei Gasdruckspeichern wegen Leckage und wegen der Temperaturabhängigkeit des Gases bzw. bei dem Hydrospeicher nach der US-A- 4046 167 wegen der Federcharakteristiken auftreten können, vermieden werden. Damit braucht die Druckfluidmenge nicht größer als notwenig zu sein, um - beispielsweise bei einem Hochdruckleistungsschalter - auch bei der zweiten Ausschaltung eine ausreichende Menge an Druckfluid mit ausreichendem Druck bereit zu haben.The particular advantages of the hydraulic accumulator according to the invention are that changes in the pressure in the pressure fluid, such as can occur in gas pressure accumulators due to leakage and because of the temperature dependence of the gas or in the hydraulic accumulator according to US Pat. No. 4,046,167 due to the spring characteristics, can be avoided . As a result, the amount of pressurized fluid need not be greater than is necessary in order to have a sufficient amount of pressurized fluid with sufficient pressure available, for example in the case of a high-pressure circuit breaker, even when switched off for the second time.

Anhand der Zeichnung, in der ein Ausführugsbeispiel der Erfindung dargestellt ist, soll die Erfindung näher erläutert und beschrieben werden.The invention will be explained and described in more detail with reference to the drawing, in which an exemplary embodiment of the invention is shown.

Es zeigt:

  • Figur 1: Eine Seitenansicht eines Hydrospeichers, und
  • Figur 2: eine Aufsicht von unten auf den Hydrospeicher gemäß Figur 1.
It shows:
  • Figure 1: A side view of a hydraulic accumulator, and
  • FIG. 2: a bottom view of the hydraulic accumulator according to FIG. 1.

Auf einer Grundplatte 70 ist mittels Schraubenverbindungen 72 ein Zylinder 74, der rohrförmig ausgebildet ist, aufgeschraubt. Im Inneren des Zylinders 74 ist ein Kolben 76 hin und her beweglich verschiebbar. In der Grundplatte 70 befindet sich eine Auslaßöffnung 78, die mit der hydraulischen Anlage verbunden ist. Zwischen der Grundplatte 70, dem Zylinder 74 und dem Kolben 76 befindet sich der Hochdruckraum 80. Auf der dem Hochdruckraum gegenüberliegenden Seite des Kolbens 76 ist an dem Kolben eine Kolbenstange 82 befestigt. Auf der der Grundplatte 70 gegenüberliegenden Stirnfläche des Zylinders ist ein Behälter 84 mittels einer Schraubverbindung 86 befestigt, der eine Außenwandung 88 und eine Innenwandung 90 besitzt, wobei die Innenwandung nur annähernd die Hälfte der Außenwandung 88 überdeckt. Am freien Ende, also im mittleren Bereich, ist die Innenwandung 90 mittels eines Deckels 92 mit einer Durchgangsöffnung 94 abgedeckt. Die Außenwandung 88 ist nach oben hin mittels eines Abschlußdeckels 96 abgeschlossen. In dem durch die Innenwandung 90 und die Außenwandung 88 gebildeten Raum befindet sich sogenanntes beruhigtes Öl mit Niederdruck, wogegen außerhalb des Deckels 92, aber noch innerhalb des durch die Außenwandung 88 und den Abschlußdeckel 96 gebildeten Raum aufgeschäumtes Öl mit Niederdruck vorhanden ist. Die Kolbenstange 82 durchgreift abgedichtet den Deckel 96; an ihrem oberen Ende ist ein Auflagering 98 beispielsweise mittels einer Schraubverbindung fest angebracht. Dieser Auflagering 98 besitzt auf seiner der Kolbenstange gegenüberliegenden Seite einen Zapfen 100, der in einer Bohrung 102 eines mit der Grundplatte 70 mittels Bolzen 104 fest verbundenen Traversenelementes 106 geführt ist. Am Auflagering 98 befindet sich eine radial verlaufende Auflagefläche 108.A cylinder 74, which is tubular, is screwed onto a base plate 70 by means of screw connections 72. Inside the cylinder 74, a piston 76 is movable back and forth. In the base plate 70 there is an outlet opening 78 which is connected to the hydraulic system. The high-pressure chamber 80 is located between the base plate 70, the cylinder 74 and the piston 76. A piston rod 82 is fastened to the piston on the side of the piston 76 opposite the high-pressure chamber. A container 84 is fastened on the end face of the cylinder opposite the base plate 70 by means of a screw connection 86 and has an outer wall 88 and an inner wall 90, the inner wall covering only approximately half of the outer wall 88. At the free end, in the middle Area, the inner wall 90 is covered by a cover 92 with a through opening 94. The outer wall 88 is closed at the top by means of an end cover 96. In the space formed by the inner wall 90 and the outer wall 88 there is so-called calmed oil with low pressure, whereas outside the cover 92, but still within the space formed by the outer wall 88 and the end cover 96, there is oil foamed with low pressure. The piston rod 82 seals through the cover 96; at its upper end a support ring 98 is firmly attached, for example by means of a screw connection. This support ring 98 has on its side opposite the piston rod a pin 100 which is guided in a bore 102 of a cross member 106 which is fixedly connected to the base plate 70 by means of bolts 104. A radially extending support surface 108 is located on the support ring 98.

Die Grundplatte 70 besitzt am Umfang verteilt Ausnehmungen 110, die zum Durchlaß eines Rohres 112 dienen. Oberhalb der Grundplatte stützt sich eine Auflageplatte 120 auf zwei Lagerbolzen 122 auf der Grundplatte ab.The base plate 70 has recesses 110 distributed around the circumference, which serve for the passage of a tube 112. Above the base plate, a support plate 120 is supported on two bearing bolts 122 on the base plate.

Am oberen Ende der Stange 112 befindet sich eine Auflage 124, an der eine Lasche 126 angebracht ist, die von einem Bolzen 128 durchgriffen ist, mit dem sie an einem Doppelarmhebel 130 angelenkt ist. Zwischen der Auflage 124 und der Platte 120 befindet sich ein Tellerfederpaket aus einer Anzahl von Tellerfedern 132. Aus der Figur 2 ist ersichtlich, daß am Umfang insgesamt sechs derartiger Tellerfederkonstruktionen und sechs Doppelarmhebel 130 angeordnet sind.At the upper end of the rod 112 there is a support 124, to which a tab 126 is attached, which is penetrated by a bolt 128 with which it is articulated on a double-arm lever 130. Between the support 124 and the plate 120 there is a plate spring assembly consisting of a number of plate springs 132. From FIG. 2 it can be seen that a total of six such plate spring constructions and six double-arm levers 130 are arranged on the circumference.

Der Doppelarmhebel 130 ist an einem Fortsatz 134 an dem Traversenelement über eine Achse 136 gelenkig aufgelagert. Das innere Ende des Doppelarmhebels besitzt eine ballige Ausformung 138, die auf der Fläche 108 aufliegt. Die Platte 124 ist gegen die Platte 120 verschiebbar, so daß die Tellerfedern 132 gespannt (siehe links von der Mittellinie) oder entspannt (siehe rechts von der Mittellinie der Fig. 1) sein können. Die Tellerfederpakete 132 sind aufgrund ihrer Auflagerung in dem Lagerbolzen 122 in Doppelpfeilrichtung T verschwenkbar, wie man aus der Anordnung der beiden Tellerfedern links und rechts der Mittelachse erkennen kann. In der Anordnung links ist der Abstand D1 + D2 klein und in der Anordnung rechts hat sich dieser Abstand vergrößert, wodurch das durch die Tellerfedern 132 bewirkte und erzeugte Drehmoment auf den Ring 98 vergrößert wird. Im völlig gespannten Zustand ist dieses Drehmoment annähernd so groß wie im entspannten Zustand, wodurch die auf dem Ring 98 ausgeübte Druckkraft auch bei kleiner werdender Federkraft annähernd konstant bleibt.The double arm lever 130 is articulated on an extension 134 on the cross member via an axis 136. The inner end of the double arm lever has a spherical shape 138 which rests on the surface 108. The plate 124 is slidable against the plate 120 so that the plate springs 132 can be tensioned (see left of the center line) or relaxed (see right of the center line of FIG. 1). The plate spring assemblies 132 can be pivoted in the double arrow direction T due to their support in the bearing pin 122, as can be seen from the arrangement of the two plate springs to the left and right of the central axis. In the arrangement on the left, the distance D1 + D2 is small, and in the arrangement on the right, this distance has increased, as a result of which the torque on the ring 98 caused and generated by the plate springs 132 is increased. In the fully tensioned state, this torque is approximately as great as in the relaxed state, as a result of which the compressive force exerted on the ring 98 remains approximately constant even when the spring force becomes smaller.

Wie gesagt, ist die Anordnung auf der linken Seite der Mittellinie im gespannten Zustand, d.h., daß sich der Kolben in der Stellung befindet, in der der Speicher vollständig mit Druckfluid gefüllt ist. Wenn nun bei einer Schalthandlung oder bei einer Steuerhandlung in der hydraulischen Steueranlage durch die Öffnung oder den Durchlaß 76 Drucköl abgezapft oder entnommen wird, bewegt sich der Kolben unter dem Druck der Federn 132 nach unten, wodurch die Tellerfederpakete an ihrem oberen Ende mit ihrer Achse 128 nach außen verschwenken; aufgrund der vergrößerten Hebelwirkung wird die Verringerung der Federkraft bei weiterer Entspannung ausgeglichen, so daß durch die Hebelwirkung der Doppelarmhebel 130 der Druck im Fluid annähernd konstant gehalten wird.As stated, the arrangement on the left side of the center line is in the cocked state, i.e. the piston is in the position in which the accumulator is completely filled with pressurized fluid. If, during a switching operation or during a control action in the hydraulic control system, pressure oil is drawn off or extracted through the opening or the passage 76, the piston moves downwards under the pressure of the springs 132, whereby the plate spring assemblies at their upper end with their axis 128 swivel outwards; due to the increased leverage, the reduction in spring force is compensated for upon further relaxation, so that the leverage of the double-arm lever 130 keeps the pressure in the fluid approximately constant.

Anstatt mehrerer Tellerfederpakete können auch Schraubenfedern verwendet werden.Instead of several disc spring sets, coil springs can also be used.

Im Kolben 76 ist ein Entlastungsventil 140 untergebracht, das mit einer Ventilstange 142 den Kolben 76 durchgreift und diesen auf der dem Hochdruckraum 80 entgegengesetzten Seite überragt. Wenn der Kolben 76 in die oberste Stellung vom Druckfluid z.B. aufgrund einer Überlastung im hydraulischen Steuersystem gedrückt wird, schlägt die Ventilstange 142 gegen eine Begrenzungsfläche 144 am Niederdruckbehälter 84, 88, 90 und 96 an und öffnet das Entlastungsventil 140, so daß ein Durchlaß vom Hochdruckraum 80 zum Niederdruckraum freigegeben wird.A relief valve 140 is accommodated in the piston 76, which extends through the piston 76 with a valve rod 142 and projects beyond it on the side opposite the high-pressure chamber 80. When the piston 76 is in the uppermost position from the pressurized fluid e.g. is pressed due to an overload in the hydraulic control system, the valve rod 142 abuts against a boundary surface 144 on the low pressure container 84, 88, 90 and 96 and opens the relief valve 140, so that a passage from the high pressure chamber 80 to the low pressure chamber is released.

Claims (6)

1. Hydraulic accumulator for providing pressure fluid for a hydraulic system, especially for actuating a medium-voltage or high-voltage circuit breaker, with a cylinder (74) in which a piston (76) is movable, the pressure fluid being located on one side (80) of the latter, the piston (76) being stressed by a spring arrangement, formed from several tension or compression springs (132) distributed uniformly in a circle, for generating the pressure in the pressure fluid, characterised in that the tension or compression springs (132) engage on one end of a rocker arm (130) which is mounted rotatably or pivotably at its centre and the other inner end of which acts on the piston (76).
2. Hydraulic accumulator according to Claim 1, characterised in that the rocker arms (130) are arranged, relative to the centre axis of the piston (76), approximately perpendicularly to this, the pivoting plane of the rocker arms extending through the centre axis of the piston.
3. Hydraulic accumulator according to one of Claims 1 or 2, characterised in that the rocker arms (130), at least at their end facing the piston (76), have, in the bearing region, an approximately semicircular curved surface (138) which rests against a supporting surface (108) connected to the piston.
4. Hydraulic accumulator according to Claim 3, characterised in that there is a base plate (70), on which the cylinder (74) in which the piston (76) moves is fastened, in that a crossmember element (106) is provided at a distance from the base plate by means of connecting bolts (104), the cylinder (74) and the piston rod (82) being accommodated between the base plate and the crossmember element, and in that the rocker arms (130) are mounted on the crossmember element (106) in an articulated manner.
5. Hydraulic accumulator according to one of the preceding claims, characterised in that the high-pressure space (80) on one side of the piston (76) and the low-pressure space of the hydraulic system constitute a unit with one another, and in that the piston rod (82) passes through the low-pressure unit and at its free end has a supporting ring (98) which forms the supporting surface (108) extending transversely relative to the centre axis of the piston rod.
6. Hydraulic accumulator according to Claim 5, characterised in that there is in the piston (76) a relief valve (140), which, when the piston comes up against a limiting surface (144) on the cylinder (74), is opened and connects the high-pressure space (80) on one side of the piston to the low-pressure space in the region of the piston rod (82).
EP83108104A 1982-08-28 1983-08-17 Hydraulic accumulator for supplying a pressure fluid Expired EP0105152B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19823232074 DE3232074A1 (en) 1982-08-28 1982-08-28 HYDRO STORAGE TO PROVIDE PRESSURE FLUID
DE3232074 1982-08-28

Publications (2)

Publication Number Publication Date
EP0105152A1 EP0105152A1 (en) 1984-04-11
EP0105152B1 true EP0105152B1 (en) 1986-11-26

Family

ID=6171942

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83108104A Expired EP0105152B1 (en) 1982-08-28 1983-08-17 Hydraulic accumulator for supplying a pressure fluid

Country Status (4)

Country Link
US (1) US4623134A (en)
EP (1) EP0105152B1 (en)
JP (1) JPS5958201A (en)
DE (2) DE3232074A1 (en)

Family Cites Families (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1365030A (en) * 1919-09-15 1921-01-11 Flentje Ernst Shock-absorber
US1512736A (en) * 1922-08-15 1924-10-21 Aldrich Roscoe Hilton Shock absorber for hydraulic systems
US1663647A (en) * 1927-02-07 1928-03-27 Alanson P Brush Energy-storage unit
US1861154A (en) * 1931-04-02 1932-05-31 Toledo Machine & Tool Company Fluid pressure accumulator
US2298512A (en) * 1936-10-15 1942-10-13 Edward A Rockwell Accumulator for supplying liquid under pressure
US2321093A (en) * 1940-12-20 1943-06-08 James A Lupfer Pressure equalizer
US2318065A (en) * 1941-05-07 1943-05-04 Mattia Peter De Hydraulic drive
AT204343B (en) * 1955-09-03 1959-07-10 Jean Louis Gratzmuller Hydraulic energy storage
US3064093A (en) * 1958-11-22 1962-11-13 Asea Ab Hydraulic means for stressing the springs of spring actuated electric switches
DE1290226B (en) * 1960-11-05 1969-03-06 Liebknecht Transformat Control arrangement for high-voltage pressure gas switch
US3495508A (en) * 1965-10-21 1970-02-17 Earle F Allen Hydraulic drive cylinder
US3581774A (en) * 1969-04-01 1971-06-01 Us Navy Constant pressure accumulator
DE2105640A1 (en) * 1971-02-06 1972-08-17 Knorr-Bremse GmbH, 8000 München Spring-loaded cylinder
DE2137108A1 (en) * 1971-07-24 1973-02-01 Fendt & Co Xaver ACCUMULATOR CHARGE VALVE
DE2419376C2 (en) * 1974-04-22 1985-03-14 Daimler-Benz Ag, 7000 Stuttgart Regenerative heat exchanger of a gas turbine,
GB1496796A (en) * 1975-01-30 1978-01-05 Dewandre Co Ltd C Spring brake actuators
US4046167A (en) * 1976-02-06 1977-09-06 Kawneer Company, Inc. Mechanical accumulator
US4077303A (en) * 1976-04-14 1978-03-07 Peder Ulrik Poulsen Apparatus for generating an impact force
DE2629565A1 (en) * 1976-07-01 1978-01-12 Wabco Westinghouse Gmbh SPRING STORAGE CYLINDER
GB1603420A (en) * 1978-05-30 1981-11-25 Woodhead Ltd Jonas Hydraulic shock absorbers

Also Published As

Publication number Publication date
JPS5958201A (en) 1984-04-03
DE3232074A1 (en) 1984-03-01
EP0105152A1 (en) 1984-04-11
US4623134A (en) 1986-11-18
DE3367963D1 (en) 1987-01-15

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