EP0158054B1 - Hydraulic drive - Google Patents

Hydraulic drive Download PDF

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Publication number
EP0158054B1
EP0158054B1 EP85101751A EP85101751A EP0158054B1 EP 0158054 B1 EP0158054 B1 EP 0158054B1 EP 85101751 A EP85101751 A EP 85101751A EP 85101751 A EP85101751 A EP 85101751A EP 0158054 B1 EP0158054 B1 EP 0158054B1
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EP
European Patent Office
Prior art keywords
piston
storage
pressure
hydraulic drive
working
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
EP85101751A
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German (de)
French (fr)
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EP0158054A1 (en
Inventor
Gerhard Körner
Horst Plettner
Edelwald Lutz
Egon Orth
Rudi Weingärtner
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BBC Brown Boveri AG Switzerland
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BBC Brown Boveri AG Switzerland
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Publication of EP0158054A1 publication Critical patent/EP0158054A1/en
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Expired legal-status Critical Current

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    • HELECTRICITY
    • H01ELECTRIC ELEMENTS
    • H01HELECTRIC SWITCHES; RELAYS; SELECTORS; EMERGENCY PROTECTIVE DEVICES
    • H01H33/00High-tension or heavy-current switches with arc-extinguishing or arc-preventing means
    • H01H33/02Details
    • H01H33/28Power arrangements internal to the switch for operating the driving mechanism
    • H01H33/30Power arrangements internal to the switch for operating the driving mechanism using fluid actuator
    • H01H33/34Power arrangements internal to the switch for operating the driving mechanism using fluid actuator hydraulic

Definitions

  • the invention relates to a hydraulic drive, in particular for high-voltage circuit breakers, with a working piston designed as a differential piston and provided with a piston rod penetrating the pressure housing in the center, which is guided in a one-sided axial recess in a pressure housing and on the one hand constantly under the force of an energy store stands and the other side can either be pressurized or relieved of pressure.
  • Such a drive is known from DE-A-2828 958, in which a differential piston is acted upon by hydraulic fluid from a separately arranged energy store.
  • a spatial separation inevitably leads to the laying of pressure lines which are susceptible to interference from external influences, which, depending on their length, have an adverse effect on the efficiency of the system, and which have to be laid taking fire safety into account, which overall requires a considerable amount of installation work caused.
  • the recess is made as a step-shaped cylinder bore, the working piston being guided in the bore with a smaller diameter and the storage piston in the bore with a larger diameter.
  • the recess in the pressure housing is expediently closed with a housing cover, this having a cup-shaped bulge which accommodates the collecting space for the hydraulic fluid.
  • the spring arrangement or spring accumulator, to serve as an energy store concentrically around the pressure housing, the storage piston using transmission rods, which are arranged symmetrically to its central axis and slide out of the pressure housing in a pressure-tight manner, via a thrust piece with the spring accumulator is rigidly coupled.
  • the spring accumulator is supported against a molded-in shoulder on the almost cylindrical pressure housing.
  • the end of the pressure housing facing away from the housing recess has a cylindrical outer contour which serves as a sliding guide for the circular pressure piece.
  • the spring accumulator is expediently formed from disk spring assemblies. This measure offers the known advantage that with an appropriate choice of dimensions and preload an almost constant force curve can be set over the spring travel, so that the hydraulic accumulator has an almost constant pressure over its entire operating range.
  • the housing cover has an integrally formed switch flange in the extension of the pressure housing, to which a high-voltage circuit breaker can be attached.
  • a mechanical position indicator which actuates a limit switch attached to the housing cover in the extension of one of the transmission rods, serves to control the respective memory content of the hydraulic accumulator.
  • a mechanical and electrical position indicator is provided, which is connected to a coupling via a lever with a slide for converting the translational movement of the working piston into a rotational movement, which coupling is firmly connected to the piston rod.
  • a high-pressure pump and a hydraulic control unit are integrated diametrically opposite one another in the pressure housing in the area of the storage space, the control slide belonging to the hydraulic control unit being located in a bore running parallel to the central axis of the storage piston.
  • Another advantage that results from this design is that all hydraulic connections between the pressure chambers and the high-pressure pump and the hydraulic control unit are designed in the form of fluid channels embedded in the pressure housing, so that externally installed pressure lines are not required.
  • the fluid channels are designed so that hydraulic fluid is conveyed from the collecting space into the storage space and from there via the three-way control unit can get from the storage space into a working space for the working piston and from the working space into the collecting space.
  • the work space is located on the side of the working piston facing away from the storage space.
  • a spring-loaded locking pin inserted in the pressure housing engages in an annular groove provided for this purpose on the working piston jacket when the working piston is in its working position.
  • the spring force of the compression spring is to be set so that the locking pin slides back into its bore at operating pressure in the hydraulic fluid storage space as a result of the force acting on its excellent end face.
  • the hydraulic drive according to the invention is designed in such a way that it meets the standards, regulations or legal regulations (e.g. ANSI, ICE / VDE) and reliably maintains the switching times or switching intervals required there.
  • standards, regulations or legal regulations e.g. ANSI, ICE / VDE
  • one or more additional, externally arranged hydraulic accumulators that are independent of external energy supply and have the same structure, i.e. Units without work, pump and control unit can be provided, which are connected to the hydraulic drive via corresponding hydraulic lines and valves.
  • the drive capacity can be increased practically as desired and adapted to the application requirements, the additional space requirement being small due to the compact design.
  • the connecting lines can be rigid, i.e. firm or flexible, e.g. be laid as an armored hose.
  • the valves are designed according to the invention as a multi-way valve and expediently arranged on the hydraulic drive in order to prevent the pressure drop in the storage space in the case of damaged connections.
  • the location of the or the additional storage can be determined according to the respective local conditions.
  • FIG. 1 shows the schematic structure of the arrangement formed from the storage unit and hydraulic actuator.
  • a storage piston 16 which delimits a collecting space 34, which is subjected to low pressure and in which the storage piston 16 is supported against the pressure housing via a spring arrangement symmetrical with respect to its central axis, against a storage space 30 which acts on high pressure is also a working piston 18, which has a piston rod 28 which axially penetrates axially the storage piston 16 and the pressure housing 10 for the purpose of actuating an electrical switch 100, and which separates the storage space 30 from a working space 38, which can be selected by means of a control unit 22 optionally via fluid channels 54, 56 connected to the storage space 30 can be pressurized, or connected to the collecting space 34 via fluid channels 54, 58 can be relieved of the pressure.
  • a high-pressure pump 20 delivers pressure fluid from the collecting space 34 into the storage space 30 via fluid channels 50, 52.
  • the hydraulic drive shown in FIGS. 2 to 4 has a pressure housing 10 with an almost cylindrical stepped outer contour, into which a step-shaped cylinder bore is formed starting from an end face in the axial direction.
  • This bore has a first area with a large diameter, which serves as storage cylinder 12, and a second area with a smaller diameter, which serves as working cylinder 14, at a depth of approximately 1/3.
  • the pressure housing 10 is closed off from the outside with a flanged housing cover 32.
  • a high-pressure pump 20 is fitted outside in a pressure-tight manner by means of a circumferential seal into a housing opening arranged radially to the cylinder axis.
  • a hydraulic control unit 22 is also positively integrated diametrically opposite in the pressure housing 10.
  • the storage cylinder 12 serves to receive a storage piston 16, which separates the storage space 30, which is under high pressure, from the collecting space 34, which is acted upon by low pressure and is arranged in the cup-shaped, arched housing cover 32. If the operating pressure in the storage space 30 is exceeded, it is connected to the collecting space 34 via a bore 86 which extends axially eccentrically in the storage piston 16 and leads to a pressure relief valve 84 located in the storage piston 16.
  • the storage piston 16 On the side facing the collecting space 34, the storage piston 16 has a collar 90, through which a fluid channel 58, which is formed in the pressure housing 10 and is extended by means of a pressed-in piece of pipe, is eccentrically guided in a bore 92 with sufficient play and ends in the collecting space 34. Further bores are arranged symmetrically to the central axis, each receiving a transmission rod 60.
  • the storage piston 16 On the end of the storage piston 16 opposite the collar 90 there is a sliding seal embedded in the outer surface of the storage piston 16 102, which seals the storage space 30 against the wall of the storage cylinder 12. In its center, the storage piston 16 is penetrated by a piston rod 28 in an axially extending guide bore 82. At least one sliding seal 104 inserted into the guide bore 82 is provided to seal the storage space 30. Two slide rings 106 serve for the exact guidance of the piston rod 28 in the guide bore 82.
  • the free access for the hydraulic fluid from the storage space 30 to a work space 36 is limited to a defined cross section by a fitted insert and an inserted impact bushing 110.
  • the piston rod 28 is non-detachably connected to a working piston 18, which, designed as a differential piston, has annularly tapering shoulders 88 on both piston surfaces, which act as impact dampers and which merge into the piston rod 28 on one side.
  • the working piston 18 On the end opposite the piston rod 28, the working piston 18 carries a piston ring, a sliding seal 42 is also embedded in the piston jacket at an approximately medium piston height.
  • an annular groove 44 is provided in the jacket of the working piston 18, the contour of which is adapted to a spring-loaded locking pin 46.
  • a fluid channel 54 opens into the bottom 48 of the working cylinder 14 and establishes the connection to the hydraulic control unit 22 running axially parallel to the working cylinder 14.
  • the hydraulic control unit is connected to the storage space 30 via a fluid duct 56, and to the collecting space 34 via a fluid duct 58.
  • the high-pressure pump 20 is connected to the collecting space 34 via a fluid channel 50 and to the storage space 30 via a fluid channel 52.
  • the spring-loaded locking pin 46 is arranged in the radial direction in the working cylinder 14 as a pressure-controlled locking device, which is aligned with the provided annular groove 44 when the working piston 18 is in the working position.
  • the transmission rods 60 are led out of the pressure housing 10 in a bushing with a sliding seal and connect the accumulator piston 16 to a spring arrangement 26 by means of a pressure piece 62.
  • the stepped and threaded ends of the transmission rod 60 are each bores in the collar 90 of the thread which are adapted to the thread diameter Storage piston 16 and holes in the pressure piece 62 inserted so that the collar and the pressure piece 62 are supported on the transmission rod 60 and are each fixed non-positively.
  • the pressure piece 62 is guided by the cylindrical end of the pressure housing 10 so that it slides on the slide guide 74 with its inner bore 70, which has a slide piece 72 for reducing friction.
  • the spring arrangement 26 is layered in alternating directions and arranged and preloaded in accordance with its geometry in such a way that an almost constant force curve results over the entire working path.
  • the spring assemblies 26 are supported on the one hand against the pressure piece 62 and on the other hand against an abutment 78 incorporated on the circumference of the pressure housing 10.
  • the housing cover 32 is penetrated by the piston rod 28 in a central bore 108 with an inserted sliding seal.
  • Eccentrically arranged in the extension of a transmission rod 60 is a mechanical control indicator 120 for the accumulator piston which penetrates the housing cover in a slide-tight bore 109 and leads out of the pressure housing 10 and which actuates a limit switch 122 fastened to the housing cover 32.
  • the further configuration of the housing cover 32 provides that an electrical switch 100 to be actuated via the piston rod 28 can be flanged to the switch flange 124 in the extension of the pressure housing 10.
  • the housing cover 32 is guided radially outwards so that it serves as a hood base 116 for receiving a cover 114, which is detachably connected to the hood base 116 with a closure.
  • An optical reading device can be attached to the hood base at the level of the mechanical setting indicator 120.
  • an electrical setting indicator 128 is provided for the working piston, which is connected to a coupling 132 via a lever with a sliding piece 130. The coupling serves to connect the piston rod 28 to the electrical switch 100 to be actuated.
  • hydraulic fluid passes from the storage space 30 to the bottom 48 of the working cylinder 14, so that the same pressure is present on both piston surfaces.
  • the working piston 18 is moved into the working position.
  • the piston rod 28 moves in the direction of the switch flange 124, as a result of which the flanged electrical switch 100 is actuated.
  • the fluid channels 54 and 58 are connected to one another in the hydraulic control unit 22.
  • the hydraulic fluid located in the working space A 38 reaches the collecting space 34 via the fluid channels 54 and 58.
  • the working piston 18 is displaced into its rest position at high speed by the storage pressure prevailing in the working space R 36.
  • the piston rod 28 moves back and actuates the electrical switch 100 and, via the lever with the slider 130, the electrical setting indicator.
  • a volume unit of hydraulic fluid corresponding to the volume of the working space 38 is consumed from the storage space 30.
  • the required number of switching operations to be made possible without the supply of external energy determines the size of the storage volume which, as explained at the beginning, is stored under almost constant force corresponding to almost constant pressure.
  • the respective available storage volume in the storage space 30 can be read on the mechanical control display 120.
  • the actuation of the high-pressure pump 20 can be controlled with the aid of the limit switch 122 provided.
  • the impact dampers 88 mentioned at the outset are provided.
  • FIG. 5 is shown schematically how an external hydraulic accumulator 10 ', 16', 26 'connects via a connecting line either as a rigid pipe 40 or as a flexible hose 40' to a multi-way valve 24, which is located on the hydraulic drive, the high pressure pump 20 either with the Storage space 34 or connects to the external hydraulic accumulator.
  • This hydraulic accumulator consists of a pressure housing 10 ', which is designed in the same way as the pressure housing 10 of the hydraulic drive.
  • the cylindrical interior is divided by a storage piston 16 'into a storage space 30' and into a second area, which receives the spring arrangement 26 'provided as a storage element.
  • the supply of pressurized fluid via the connecting line (40, 40 ') through the high-pressure pump 20 is provided, the intermediate multi-way valve securing the storage space 30 against a drop in pressure.

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  • Actuator (AREA)
  • Driving Mechanisms And Operating Circuits Of Arc-Extinguishing High-Tension Switches (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)

Description

Die Erfindung betrifft einen hydraulischen Antrieb, insbesondere für Hochspannungsleistungsschalter, mit einem als Differentialkolben ausgebildeten und mit einer des Druckgehäuse mittig durchdringenden Kolbenstange versehenen Arbeitskolben, der in einer in einem Druckgehäuse befindlichen einseitigen axialen Ausnehmung geführt ist und auf der einen Seite ständig unter der Kraft eines Energiespeichers steht und dessen andere Seite wahlweise mit Druck beaufschlagbar oder vom Druck entlastbar ist.The invention relates to a hydraulic drive, in particular for high-voltage circuit breakers, with a working piston designed as a differential piston and provided with a piston rod penetrating the pressure housing in the center, which is guided in a one-sided axial recess in a pressure housing and on the one hand constantly under the force of an energy store stands and the other side can either be pressurized or relieved of pressure.

Ein derartiger Antrieb ist aus der DE-A- 2828 958 bekannt, bei dem ein Differentialkolben von einem separat angeordneten Energiespeicher mit Hydraulikfluid beaufschlagt wird. Eine solche räumliche Trennung führt zwangslaufig zur Verlegung von Druckleitungen, die anfallig gegen Störungen durch Einwirkungen von außen sind, die sich abhängig von ihrer Länge nachteilig auf den Wirkungsgrad der Anlage auswirken, und die unter Beachtung der Brandsicherheit zu verlegen sind, was insgesamt einen erheblichen Montageaufwand verursacht.Such a drive is known from DE-A-2828 958, in which a differential piston is acted upon by hydraulic fluid from a separately arranged energy store. Such a spatial separation inevitably leads to the laying of pressure lines which are susceptible to interference from external influences, which, depending on their length, have an adverse effect on the efficiency of the system, and which have to be laid taking fire safety into account, which overall requires a considerable amount of installation work caused.

Aufgabe der Erfindung ist es daher, eine Vorrichtung zu schaffen, in der sowohl der hydraulische Antrieb als auch der erforderliche Energiespeicher einschließlich der zugehörigen Aggregate untergebracht sind ohne aufwendige Verlegung von Druckleitungen und geschützt gegen Einwirkungen von außen.It is therefore an object of the invention to provide a device in which both the hydraulic drive and the required energy store, including the associated units, are accommodated without complex laying of pressure lines and protected against external influences.

Diese Aufgabe wird erfindungsgemäß durch die kennzeichnender Merkmale des Anspruches 1 gelöst.This object is achieved by the characterizing features of claim 1.

Durch Anwendung der Erfindung ergibt sich die Möglichkeit, jederzeit, d.h. auch bei Störung oder Unterbrechung der Energiezufuhr, den hydraulischen Antrieb bestimmungsgemäß zu betätigen, da Antrieb und Energiespeicher eine Baueinheit bilden.By using the invention there is the possibility at any time, i.e. even in the event of a malfunction or interruption of the energy supply, to operate the hydraulic drive as intended, since the drive and energy storage form a structural unit.

In einer vorteilhaften Ausgestaltung der Erfindung wird die Ausnehmung als stufenförmige Zylinderbohrung eingebracht, wobei der Arbeitskolben in der Bohrung mit kleinerem Durchmesser, der Speicherkolben in der Bohrung mit größerem Durchmesser geführt werden. Diese Anordnung führt zu einer sehr kompakten Bauweise, da das mögliche Speichervolumen im Speicherraum ein Vielfaches des erforderlichen Stellvolumens für den Arbeitskolben beträgt. Ein weiterer Vorteil ist die mit dieser Anordnung erreichbare hohe Stellkraft für den Arbeitskolben.In an advantageous embodiment of the invention, the recess is made as a step-shaped cylinder bore, the working piston being guided in the bore with a smaller diameter and the storage piston in the bore with a larger diameter. This arrangement leads to a very compact design, since the possible storage volume in the storage space is a multiple of the required actuating volume for the working piston. Another advantage is the high positioning force for the working piston that can be achieved with this arrangement.

Zweckmäßigerweise wird die Ausnehmung im Druckgehäuse mit einem Gehausedeckel verschlossen, wobei dieser eine topfförmige Auswölbung aufweist, die den Sammelraum für das Hydraulikfluid aufnimmt.The recess in the pressure housing is expediently closed with a housing cover, this having a cup-shaped bulge which accommodates the collecting space for the hydraulic fluid.

Zur Verringerung der Baulänge des hydraulischen Antriebs ist es vorteilhaft, die als Energiespeicher dienende Federanordnung, kurz Federspeicher genannt, außerhalb konzentrisch um das Druckgehäuse anzuordnen, wobei der Speicherkolben mittels symmetrisch zu seiner Mittelachse angeordneter druckdicht gleitend aus dem Druckgehäuse herausgeführter Übertragungsstangen über ein Druckstück mit dem Federspeicher starr gekoppelt ist.In order to reduce the overall length of the hydraulic drive, it is advantageous to arrange the spring arrangement, or spring accumulator, to serve as an energy store concentrically around the pressure housing, the storage piston using transmission rods, which are arranged symmetrically to its central axis and slide out of the pressure housing in a pressure-tight manner, via a thrust piece with the spring accumulator is rigidly coupled.

Zur Vermeidung zusätzlicher Haltevorrichtungen und damit Montageaufwand sowie zur Erhaltung der kompakten Bauweise stützt sich der Federspeicher gegen einen an dem nahezu zylindrischen Druckgehäuse eingeformten Absatz ab. Das der Gehäuseausnehmung abgewandte Ende des Druckgehäuses weist eine zylindrische Außenkontur auf, die als Gleitführung des kreisrunden Druckstücks dient.In order to avoid additional holding devices and thus assembly effort and to maintain the compact design, the spring accumulator is supported against a molded-in shoulder on the almost cylindrical pressure housing. The end of the pressure housing facing away from the housing recess has a cylindrical outer contour which serves as a sliding guide for the circular pressure piece.

Zweckmäßigerweise wird der Federspeicher aus-Tellerfederpaketen gebildet. Diese Maßnahme bietet den bekannten Vorteil, daß bei entsprechender Wahl von Abmessung und Vorspannkraft ein nahezu konstanter Kraftverlauf über den Federweg einstellbar ist, so daß der Hydraulikspeicher über seinen gesamten Betriebsbereich nahezu konstanten Druck aufweist.The spring accumulator is expediently formed from disk spring assemblies. This measure offers the known advantage that with an appropriate choice of dimensions and preload an almost constant force curve can be set over the spring travel, so that the hydraulic accumulator has an almost constant pressure over its entire operating range.

In weiterer vorteilhafter Ausgestaltung der Erfindung weist der Gehäusedeckel in Verlängerung des Druckgehäuses einen angeformten Schalterflansch auf, an den ein Hochspannungsleistungsschalter befestigt werden kann.In a further advantageous embodiment of the invention, the housing cover has an integrally formed switch flange in the extension of the pressure housing, to which a high-voltage circuit breaker can be attached.

Zur Kontrolle des jeweiligen Speicherinhaltes des Hydraulikspeichers dient eine mechanische Stellungsanzeige, die in Verlängerung einer der Übertragungsstangen einen am Gehäusedeckel befestigten Endschalter betätigt.A mechanical position indicator, which actuates a limit switch attached to the housing cover in the extension of one of the transmission rods, serves to control the respective memory content of the hydraulic accumulator.

Zur Kontrolle der Stellung des Arbeitskolbens sind eine mechanische und elektrische Stellungsanzeige vorgesehen, die über einen Hebel mit Gleitstück zur Umsetzung der Translationsbewegung des Arbeitskolbens in eine Rotationsbewegung an eine Kupplung anschließen, die fest mit der Kolbenstange verbunden ist.To control the position of the working piston, a mechanical and electrical position indicator is provided, which is connected to a coupling via a lever with a slide for converting the translational movement of the working piston into a rotational movement, which coupling is firmly connected to the piston rod.

Im Sinne einer kompakten Bauweise sind im Bereich des Speicherraumes sich diametral gegenüberliegend eine Hochdruckpumpe und eine hydraulische Steuereinheit in das Druckgehäuse integriert, wobei der zur hydraulischen Steuereinheit gehörende Steuerschieber in einer parallel zur Mittelachse des Speicherkolbens verlaufenden Bohrung liegt.In terms of a compact design, a high-pressure pump and a hydraulic control unit are integrated diametrically opposite one another in the pressure housing in the area of the storage space, the control slide belonging to the hydraulic control unit being located in a bore running parallel to the central axis of the storage piston.

Ein weiterer Vorteil, der sich aus dieser Gestaltung ergibt, beruht darauf, daß sämtliche hydraulischen Verbindungen zwiscben den Druckräumen und der Hochdruckpumpe sowie der hydraulischen Steuereinheit in Form von in das Druckgehäuse eingelassenen Fluidkanälen ausgebildet sind, so daß extern verlegte Druckleitungen entfallen. Die Fluidkanäle sind so ausgeführt, daß Hydraulikfluid vom Sammelraum in den Speicherraum gefördert wird und von dort über die dreiwegige Steuereinheit vom Speicherraum in einen Arbeitsraum für den Arbeitskolben sowie vom Arbeitsraum in den Sammelraum gelangen kann. Der Arbeitsraum befindet sich auf der dem Speicherraum abgewandten Seite des Arbeitskolbens.Another advantage that results from this design is that all hydraulic connections between the pressure chambers and the high-pressure pump and the hydraulic control unit are designed in the form of fluid channels embedded in the pressure housing, so that externally installed pressure lines are not required. The fluid channels are designed so that hydraulic fluid is conveyed from the collecting space into the storage space and from there via the three-way control unit can get from the storage space into a working space for the working piston and from the working space into the collecting space. The work space is located on the side of the working piston facing away from the storage space.

Um im Falle eines störungsbedingten Druckabfalls im Speicherraum unbeabsichtigte Schaltvorgänge des Antriebs auszuschließen greift ein im Druckgehäuse eingelassener federbelasteter Verriegelungsstift bei in seiner Arbeitsstellung befindlichem Arbeitskolben in eine hierfür auf dem Arbeitskolbenmantel vorgesehene Ringnut ein. Die Federkraft der Druckfeder ist so einzustellen, daß der Verriegelungsstift bei Betriebsdruck im Speicherraum des Hydraulikfluids infolge der auf seine hervorragende Stirnfläche wirkenden Kraft in seine Bohrung zurückgleitet.In order to rule out accidental switching operations of the drive in the event of a pressure drop in the storage space due to a fault, a spring-loaded locking pin inserted in the pressure housing engages in an annular groove provided for this purpose on the working piston jacket when the working piston is in its working position. The spring force of the compression spring is to be set so that the locking pin slides back into its bore at operating pressure in the hydraulic fluid storage space as a result of the force acting on its excellent end face.

Der erfindungsgemäße hydraulische Antrieb ist hinsichtlich seiner Schaltleistung so ausgelegt, daß er die Normen, Vorschriften oder gesetzlichen Regelungen (z.B. ANSI, ICE/VDE) erfüllt und dort geforderte Schaltzeiten bzw. Schaltinterwalle sicher einhält.With regard to its switching capacity, the hydraulic drive according to the invention is designed in such a way that it meets the standards, regulations or legal regulations (e.g. ANSI, ICE / VDE) and reliably maintains the switching times or switching intervals required there.

Zur Erhöhung der Speicherkapazität können ein oder mehrere zusätzliche, extern angeordnete und von Fremdenergiezufuhr unabhängige, gleichartig aufgebaute Hydraulikspeicher, d.h. Aggregate ohne Arbeits-, Pumpen- und Steuereinheit vorgesehen sein, die über entsprechende Hydraulikleitungen und -ventile mit dem hydraulischen Antrieb verbunden sind. Hiermit läßt sich die Antriebskapazität praktisch beliebig erhöhen und den Einsatzerfordernissen anpassen, wobei der zusätzliche Raumbedarf aufgrund der kompakten Gestaltung gering ist.To increase the storage capacity, one or more additional, externally arranged hydraulic accumulators that are independent of external energy supply and have the same structure, i.e. Units without work, pump and control unit can be provided, which are connected to the hydraulic drive via corresponding hydraulic lines and valves. With this, the drive capacity can be increased practically as desired and adapted to the application requirements, the additional space requirement being small due to the compact design.

Die Verbindungsleitungen können starr, d.h. fest, oder flexibel, z.B. als Panzerschlauch verlegt sein. Die Ventile sind erfindungsgemäß als Mehrwegeventil ausgestaltet und zweckmäßigerweise am hydraulischen Antrieb angeordnet, um den Druckabfall im Speicherraum bei beschädigten Verbindungen zu verhindern. Dabei kann der Ort der oder des Zusatzspeichers den jeweiligen örtlichen Gegebenheiten entsprechend festgelegt werden.The connecting lines can be rigid, i.e. firm or flexible, e.g. be laid as an armored hose. The valves are designed according to the invention as a multi-way valve and expediently arranged on the hydraulic drive in order to prevent the pressure drop in the storage space in the case of damaged connections. The location of the or the additional storage can be determined according to the respective local conditions.

Anhand einer Schemaskizze und eines Ausführungsbeispiel soll in den Figuren und Figurenbeschreibung der Erfindungsgedanke und seine Ausgestaltungsmöglichkeiten noch einmal erläutert und konkreter veranschaulicht werden.On the basis of a schematic sketch and an exemplary embodiment, the idea of the invention and its design possibilities are to be explained again and illustrated more specifically in the figures and description of the figures.

Es zeigen:

  • Fig. 1 Prinzipskizze der Anordnung,
  • Fig. 2 Schnitt durch einen hydraulischen Antrieb mit Hydraulikspeicher in Ruhestellung (z.B. Schalter geöffnet),
  • Fig. 3 Schnitt durch einen hydraulischen Antrieb mit Hydraulikspeicher in Arbeitsstellung (z.B. Schalter geschlossen),
  • Fig. 4 Seitenansicht der Anschlußseite (Schalterseite),
  • Fig. 5 Prinzipskizze der Anordnung mit einem externen Hydraulikspeicher.
Show it:
  • 1 is a schematic diagram of the arrangement,
  • 2 section through a hydraulic drive with hydraulic accumulator in the rest position (eg switch open),
  • 3 section through a hydraulic drive with hydraulic accumulator in the working position (eg switch closed),
  • 4 side view of the connection side (switch side),
  • Fig. 5 schematic diagram of the arrangement with an external hydraulic accumulator.

Figur 1 zeigt den schematischen Aufbau der aus Speichereinheit und hydraulischem Stellglied gebildeten Anordnung. Innerhalb eines gemeinsamen Druckgehäuses 10 sind befindlich ein Speicherkolben 16, der einen Sammelraum 34, der mit Niederdruck beaufschlagt ist und in dem sich der Speicherkolben 16 über eine zu seiner Mittelachse symmetrischen Federanordnung gegen das Druckgehäuse abstützt, gegen einen Speicherraum 30 abgrenzt, der mit Hochdruck beaufschlagt ist, ferner ein Arbeitskolben 18, der eine Kolbenstange 28 aufweist, die mittig axial den Speicherkolben 16 und das Druckgehäuse 10 durchdringt zwecks Betätigung eines elektrischen Schalters 100, und der den Speicherraum 30 von einem Arbeitsraum 38 trennt, der mittels einer Steuereinheit 22 wahlweise über Fluidkanäle 54,56 mit dem Speicherraum 30 verbunden mit Druck beaufschlagbar ist, oder über Fluidkanäle 54, 58 mit dem SammeIraum 34 verbunden vom Druck entlastbar ist. Eine Hochdruckpumpe 20 fördert über Fluidkanäle 50, 52 vom Sammelraum 34 Druckfluid in den Speicherraum 30.Figure 1 shows the schematic structure of the arrangement formed from the storage unit and hydraulic actuator. Within a common pressure housing 10 there is a storage piston 16, which delimits a collecting space 34, which is subjected to low pressure and in which the storage piston 16 is supported against the pressure housing via a spring arrangement symmetrical with respect to its central axis, against a storage space 30 which acts on high pressure is also a working piston 18, which has a piston rod 28 which axially penetrates axially the storage piston 16 and the pressure housing 10 for the purpose of actuating an electrical switch 100, and which separates the storage space 30 from a working space 38, which can be selected by means of a control unit 22 optionally via fluid channels 54, 56 connected to the storage space 30 can be pressurized, or connected to the collecting space 34 via fluid channels 54, 58 can be relieved of the pressure. A high-pressure pump 20 delivers pressure fluid from the collecting space 34 into the storage space 30 via fluid channels 50, 52.

Der in Fig. 2 bis 4 abgebildete hydraulische Antrieb besitzt ein Druckgehäuse 10 mit nahezu zylindrischer abgesetzter Außenkontur, in das ausgehend von einer Stirnfläche in axialer Richtung eine stufenförmige Zylinderbohrung eingeformt ist. Diese Bohrung weist auf ca. 1/3 Tiefe einen ersten Bereich mit großem Durchmesser, der als Speicherzylinder 12 dient, und einen zweiten Bereich mit kleinerem Durchmesser auf, der als Arbeitszylinder 14 dient. Nach außen abgeschlossen wird das Druckgehäuse 10 mit einem angeflanschten Gehausedeckel 32.The hydraulic drive shown in FIGS. 2 to 4 has a pressure housing 10 with an almost cylindrical stepped outer contour, into which a step-shaped cylinder bore is formed starting from an end face in the axial direction. This bore has a first area with a large diameter, which serves as storage cylinder 12, and a second area with a smaller diameter, which serves as working cylinder 14, at a depth of approximately 1/3. The pressure housing 10 is closed off from the outside with a flanged housing cover 32.

Im Bereich des Speicherzylinders 12 ist außen eine Hochdruckpumpe 20 mittels einer umlaufenden Dichtung druckdicht in eine radial zur Zylinderachse angeordnete Gehäuseöffnung eingepaßt. Diametral gegenüberliegend ist ebenfalls formschlüssig eine hydraulische Steuereinheit 22 in das Druckgehäuse 10 integriert.In the area of the storage cylinder 12, a high-pressure pump 20 is fitted outside in a pressure-tight manner by means of a circumferential seal into a housing opening arranged radially to the cylinder axis. A hydraulic control unit 22 is also positively integrated diametrically opposite in the pressure housing 10.

Der Speicherzylinder 12 dient zur Aufnahme eines Speicherkolbens 16, der den unter Hochdruck stehenden Speicherraum 30 von dem mit Niederdruck beaufschlagten im topfförmig ausgewölbten Gehäusedeckel 32 angeordneten Sammelraum 34 trennt. Bei Überschreitung des Betriebsdrucks im Speicherraum 30 wird dieser über eine Bohrung 86, die axial exzentrisch im Speicherkolben 16 verläuft und zu einem im Speicherkolben 16 befindlichen Überdruckventil 84 führt, mit dem Sammelraum 34 verbunden. Auf der dem Sammelraum 34 zugewandten Seite weist der Speicherkolben 16 einen Kragen 90 auf, durch den exzentrisch in axialer Richtung ein in das Druckgehäuse 10 eingeformter mittels einem eingepreßten Rohrstück verlängerter Fluidkanal 58 in einer Bohrung 92 mit ausreichendem Spiel durchgeführt ist und im Sammelraum 34 endet. Symmetrisch zur Mittelachse sind weitere Bohrungen angeordnet, die je eine Übertragungsstange 60 aufnehmen.The storage cylinder 12 serves to receive a storage piston 16, which separates the storage space 30, which is under high pressure, from the collecting space 34, which is acted upon by low pressure and is arranged in the cup-shaped, arched housing cover 32. If the operating pressure in the storage space 30 is exceeded, it is connected to the collecting space 34 via a bore 86 which extends axially eccentrically in the storage piston 16 and leads to a pressure relief valve 84 located in the storage piston 16. On the side facing the collecting space 34, the storage piston 16 has a collar 90, through which a fluid channel 58, which is formed in the pressure housing 10 and is extended by means of a pressed-in piece of pipe, is eccentrically guided in a bore 92 with sufficient play and ends in the collecting space 34. Further bores are arranged symmetrically to the central axis, each receiving a transmission rod 60.

Auf dem dem Kragen 90 entgegengesetzt liegenden Ende des Speicherkolbens 16 befindet sich eine in die Mantelfläche des Speicherkolbens 16 eingelassene Gleitdichtung 102, die den Speicherraum 30 gegen die Wand des Speicherzylinders 12 abdichtet. In seinem Zentrum wird der Speicherkolben 16 in einer axial verlaufenden Führungsbohrung 82 von einer Kolbenstange 28 durchdrungen. Zur Abdichtung des Speicherraums 30 ist wenigstens eine in die Führungsbohrung 82 eingesetzte Gleitdichtung 104 vorgesehen. Zwei Gleitringe 106 dienen zur exakten Führung der Kolbenstange 28 in der Führungsbohrung 82.On the end of the storage piston 16 opposite the collar 90 there is a sliding seal embedded in the outer surface of the storage piston 16 102, which seals the storage space 30 against the wall of the storage cylinder 12. In its center, the storage piston 16 is penetrated by a piston rod 28 in an axially extending guide bore 82. At least one sliding seal 104 inserted into the guide bore 82 is provided to seal the storage space 30. Two slide rings 106 serve for the exact guidance of the piston rod 28 in the guide bore 82.

Der freie Zugang für das Hydraulikfluid vom Speicherraum 30 zu einem Arbeitsraum 36 wird durch ein eingepaßtes Einsatzstück und eine eingesetzte Prallbüchse 110 auf einen definierten Querschnitt begrenzt. Die Kolbenstange 28 ist unlösbar mit einem Arbeitskolben 18 verbunden, der, als Differentialkolben ausgebildet, auf beiden Kolbenflachen ringförmig sich verjüngende Absatze 88 aufweist, die als Aufpralldämpfer wirken, und die auf einer Seite in die Kolbenstange 28 übergehen. Auf dem der Kolbenstange 28 entgegengesetzten Ende trägt der Arbeitskolben 18 einen Kolbenring, daneben auf etwa mittlerer Kolbenhöhe ist eine Gleitdichtung 42 in den Kolbenmantel eingelassen. Auf der der Kolbenstange zugewandten Seite ist im Mantel des Arbeitskolbens 18, eine Ringnut 44 vorgesehen, deren Kontur einen federbelasteten Verriegelungsstift 46 angepaßt ist. In den Boden 48 des Arbeitszylinders 14 mündet ein Fluidkanal 54, der axial parallel verlaufend zum Arbeitszylinder 14 die Verbindung zur hydraulischen Steuereinheit 22 herstellt. Über einen Fluidkanal 56 ist die hydraulische Steuereinheit mit dem Speicherraum 30 verbunden, über einen Fluidkanal 58 mit dem Sammelraum 34.The free access for the hydraulic fluid from the storage space 30 to a work space 36 is limited to a defined cross section by a fitted insert and an inserted impact bushing 110. The piston rod 28 is non-detachably connected to a working piston 18, which, designed as a differential piston, has annularly tapering shoulders 88 on both piston surfaces, which act as impact dampers and which merge into the piston rod 28 on one side. On the end opposite the piston rod 28, the working piston 18 carries a piston ring, a sliding seal 42 is also embedded in the piston jacket at an approximately medium piston height. On the side facing the piston rod, an annular groove 44 is provided in the jacket of the working piston 18, the contour of which is adapted to a spring-loaded locking pin 46. A fluid channel 54 opens into the bottom 48 of the working cylinder 14 and establishes the connection to the hydraulic control unit 22 running axially parallel to the working cylinder 14. The hydraulic control unit is connected to the storage space 30 via a fluid duct 56, and to the collecting space 34 via a fluid duct 58.

Die Hochdruckpumpe 20 ist über einen Fluidkanal 50 mit dem Sammelraum 34 verbunden und über einen Fluidkanal 52 mit dem Speicherraum 30.The high-pressure pump 20 is connected to the collecting space 34 via a fluid channel 50 and to the storage space 30 via a fluid channel 52.

Unmittelbar neben der Prallbüchse 110 ist in radialer Richtung in den Arbeitszylinder 14 der federbelastete Verriegelungsstift 46 als druckgesteuerte Verriegelung angeordnet, der bei in Arbeitsstellung befindlichem Arbeitskolben 18 mit der vorgesehenen Ringnut 44 fluchtet.Immediately next to the impact sleeve 110, the spring-loaded locking pin 46 is arranged in the radial direction in the working cylinder 14 as a pressure-controlled locking device, which is aligned with the provided annular groove 44 when the working piston 18 is in the working position.

Die Übertragungsstangen 60 sind in einer Durchführung mit Gleitdichtung aus dem Druckgehäuse 10 herausgeführt und verbinden den Speicherkolben 16 über ein Druckstück 62 mit einer Federanordnung 26. Dabei sind die abgesetzten und mit Gewinde versehenen Enden der Übertragungsstange 60 jeweils durch dem Gewindedurchmesser angepaßte Bohrungen im Kragen 90 des Speicherkolbens 16 sowie Bohrungen im Druckstück 62 durchgesteckt, so daß sich der Kragen und das Druckstück 62 auf die Übertragungsstange 60 abstützen und jeweils kraftschlüssig fixiert sind.The transmission rods 60 are led out of the pressure housing 10 in a bushing with a sliding seal and connect the accumulator piston 16 to a spring arrangement 26 by means of a pressure piece 62. The stepped and threaded ends of the transmission rod 60 are each bores in the collar 90 of the thread which are adapted to the thread diameter Storage piston 16 and holes in the pressure piece 62 inserted so that the collar and the pressure piece 62 are supported on the transmission rod 60 and are each fixed non-positively.

Das Druckstück 62 wird von dem zylindrischen Ende des Druckgehäuses 10 so geführt, daß es mit seiner ein Gleitstück 72 zur Minderung auftretender Reibung aufweisenden Innenbohrung 70 auf der Gleitführung 74, gleitet.The pressure piece 62 is guided by the cylindrical end of the pressure housing 10 so that it slides on the slide guide 74 with its inner bore 70, which has a slide piece 72 for reducing friction.

Die Federanordnung 26 ist wechselsinnig geschichtet und entsprechend ihrer Geometrie so angeordnet und vorgespannt, daß ein nahezu konstanter Kraftverlauf über den gesamten Arbeitsweg resultiert. Die Federpakete 26 stützen sich hierbei einerseits gegen das Druckstück 62 andererseits gegen ein am Umfang des Druckgehäuses 10 eingearbeitetes Widerlager 78 ab.The spring arrangement 26 is layered in alternating directions and arranged and preloaded in accordance with its geometry in such a way that an almost constant force curve results over the entire working path. The spring assemblies 26 are supported on the one hand against the pressure piece 62 and on the other hand against an abutment 78 incorporated on the circumference of the pressure housing 10.

Der Gehäusedeckel 32 wird in einer zentralen Bohrung 108 mit eingelegter Gleitdichtung von der Kolbenstange 28 durchdrungen. Exzentrisch angeordnet ist in Verlängerung einer Übertragungsstange 60 eine in einer gleitdichten Bohrung 109 den Gehäusedeckel durchdringende mechanische Stellanzeige 120 für den Speicherkolben aus dem Druckgehäuse 10 herausgeführt, die einen am Gehäusedeckel 32 befestigten Endschalter 122 betätigt. Die weitere Ausgestaltung des Gehäusedeckels 32 sieht vor, daß in Verlängerung des Druckgehäuses 10 an einem Schalterflansch 124 ein über die Kolbenstange 28 zu betätigender elektrischer Schalter 100 angeflanscht werden kann. Ferner ist der Gehäusedeckel 32 so radial nach außen geführt, daß er als Haubensockel 116 zur Aufnahme einer Abdeckhaube 114 dient, die mit einem Verschluß lösbar mit dem Haubensockel 116 verbunden ist. In Höhe der mechanischen Stellanzeige 120 ist an den Haubensockel eine optische Ableseeinrichtung befestigbar. Desweiteren ist eine elektrische Stellanzeige 128 für den Arbeitskolben vorgesehen, die über einen Hebel mit Gleitstück 130 mit einer Kupplung 132 verbunden ist. Die Kupplung dient zur Verbindung der Kolbenstange 28 mit dem zu betätigenden elektrischen Schalter 100. Auf der dem Schalterflansch abgewandten Seite befindet sich im Druckgehäuse 10 eine Gewindebohrung 134, die eine Zylinderschraube 136 zur Fixierung einer Haltevorrichtung 138 aufnimmt.The housing cover 32 is penetrated by the piston rod 28 in a central bore 108 with an inserted sliding seal. Eccentrically arranged in the extension of a transmission rod 60 is a mechanical control indicator 120 for the accumulator piston which penetrates the housing cover in a slide-tight bore 109 and leads out of the pressure housing 10 and which actuates a limit switch 122 fastened to the housing cover 32. The further configuration of the housing cover 32 provides that an electrical switch 100 to be actuated via the piston rod 28 can be flanged to the switch flange 124 in the extension of the pressure housing 10. Furthermore, the housing cover 32 is guided radially outwards so that it serves as a hood base 116 for receiving a cover 114, which is detachably connected to the hood base 116 with a closure. An optical reading device can be attached to the hood base at the level of the mechanical setting indicator 120. Furthermore, an electrical setting indicator 128 is provided for the working piston, which is connected to a coupling 132 via a lever with a sliding piece 130. The coupling serves to connect the piston rod 28 to the electrical switch 100 to be actuated. On the side facing away from the switch flange there is a threaded bore 134 in the pressure housing 10 which receives a cylinder screw 136 for fixing a holding device 138.

Bei Einschalten der Hochdruckpumpe 20 wird über den Fluidkanal 50 Hydraulikfluid aus dem Sammelraum 34 über den Fluidkanal 52 in den Speicherraum 30 gefördert. Infolge des bei weiterer Förderung ansteigenden Drucks im Speicherraum 30 bewegt sich der Speicherkolben 16 gegen die mittels der Übertragungsstangen 60 übertragenen aus dem Zusammendrücken der Federanordnung 26 resultierenden Kraft in Richtung Gehäusedeckel 32, bis er seine vorgegebene Endstellung erreicht hat. Bei weiterem Druckanstieg öffnet sich das Überdruckventil 84, und Hydraulikfluid gelangt durch die Bohrung 86 vom Speicherraum 30 in den Sammelraum 34.When the high-pressure pump 20 is switched on, hydraulic fluid is conveyed from the collecting space 34 via the fluid channel 52 into the storage space 30 via the fluid channel 50. As a result of the increasing pressure in the storage space 30 during further conveyance, the storage piston 16 moves in the direction of the housing cover 32 against the force transmitted by the compression rods 60 resulting from the compression of the spring arrangement 26 until it has reached its predetermined end position. When the pressure rises further, the pressure relief valve 84 opens and hydraulic fluid passes through the bore 86 from the storage space 30 into the collecting space 34.

Werden in der hydraulischen Steuereinheit 22 die Fluid kanäle 54 und 56 miteinander verbunden, so gelangt Hydraulikfluid aus dem Speicherraum 30 an den Boden 48 des Arbeitszylinders 14, so daß auf beiden Kolbenflächen der gleiche Druck ansteht. Da jedoch die dem Arbeitsraum A 38 zugewandte Kolbenfläche des Arbeitskolbens 18 um den Querschnitt der Kolbenstange 28 größer ist als die gegenüberliegende Kolbenfläche wird der Arbeitskolben 18 in Arbeitsstellung bewegt. Entsprechend diesem Kolbenhub bewegt sich die Kolbenstange 28 in Richtung Schalterflansch 124, wodurch die Betätigung des angeflanschten elektrischen Schalters 100 erfolgt. Um den Arbeitskolben 18 aus der Arbeitsstellung in seine Ruhestellung zu bringen, werden in der hydraulischen Steuereinheit 22 die Fluidkanäle 54 und 58 miteinander verbunden. Auf diese Weise gelangt das im Arbeitsraum A 38 befindliche Hydraulikfluid über die Fluidkanäle 54 und 58 in den Sammelraum 34. Infolge der Druckentlastung im Arbeitsraum A 38 wird der Arbeitskolben 18 durch den im Arbeitsraum R 36 vorherrschenden Speicherdruck mit hoher Geschwindigkeit in seine Ruhestellung verschoben. Entsprechend bewegt sich die Kolbenstange 28 zurück und betätigt den elektrischen Schalter 100 und über den Hebel mit Gleitstück 130 die elektrische Stellanzeige.If the fluid channels 54 and 56 are connected to one another in the hydraulic control unit 22, hydraulic fluid passes from the storage space 30 to the bottom 48 of the working cylinder 14, so that the same pressure is present on both piston surfaces. However, since the one facing the work area A 38 Piston area of the working piston 18 is larger by the cross section of the piston rod 28 than the opposite piston area, the working piston 18 is moved into the working position. In accordance with this piston stroke, the piston rod 28 moves in the direction of the switch flange 124, as a result of which the flanged electrical switch 100 is actuated. In order to bring the working piston 18 out of the working position into its rest position, the fluid channels 54 and 58 are connected to one another in the hydraulic control unit 22. In this way, the hydraulic fluid located in the working space A 38 reaches the collecting space 34 via the fluid channels 54 and 58. As a result of the pressure relief in the working space A 38, the working piston 18 is displaced into its rest position at high speed by the storage pressure prevailing in the working space R 36. Correspondingly, the piston rod 28 moves back and actuates the electrical switch 100 and, via the lever with the slider 130, the electrical setting indicator.

Mit jedem Schaltvorgang Ein/Aus wird ein dem Volumen des Arbeitsraums 38 entsprechende Volumeneinheit an Hydraulikfluid aus dem Speicherraum 30 verbraucht. Die geforderte Anzahl der ohne Fremdenergiezufuhr zu ermöglichenden Schaltvorgange bestimmt die Größe des Speichervolumens, das wie eingangs erläutert unter nahezu konstanter Kraft entsprechend nahezu konstantem Druck gespeichert wird. Das jeweils vorhandene Speichervolumen im Speicherraum 30 kann an der mechanischen Stellanzeige 120 abgelesen werden. Mit Hilfe des vorgesehenen Endschalters 122 kann die Betätigung der Hochdruckpumpe 20 gesteuert werden.With each switching operation on / off, a volume unit of hydraulic fluid corresponding to the volume of the working space 38 is consumed from the storage space 30. The required number of switching operations to be made possible without the supply of external energy determines the size of the storage volume which, as explained at the beginning, is stored under almost constant force corresponding to almost constant pressure. The respective available storage volume in the storage space 30 can be read on the mechanical control display 120. The actuation of the high-pressure pump 20 can be controlled with the aid of the limit switch 122 provided.

Zur Vermeidung mechanischer Beschädigungen des Arbeitskolbens 18 infolge seiner raschen Bewegung von Ruhestellung in Arbeitsstellung und umgekehrt sind die eingangs erwähnten Aufpralldämpfer 88 vorgesehen.To avoid mechanical damage to the working piston 18 as a result of its rapid movement from the rest position into the working position and vice versa, the impact dampers 88 mentioned at the outset are provided.

Ihre Wirkung beruht darauf, daß der Ablaufquerschnitt für das Druckfluid aus dem Arbeitszylinder 14 abhängig von der jeweiligen Stellung des Arbeitskolbens 18 sich verringert. Dies hat zur Folge, daß das Druckfluid langsamer abläuft, so daß der Arbeitskolben 18 in seiner Bewegung abgebremst wird.Their effect is based on the fact that the discharge cross-section for the pressure fluid from the working cylinder 14 is reduced depending on the respective position of the working piston 18. This has the consequence that the pressure fluid runs more slowly, so that the working piston 18 is braked in its movement.

In Figur 5 ist schematisch gezeigt, wie ein externer Hydraulikspeicher 10', 16', 26' über eine Verbindungsleitung wahlweise als starre Rohrleitung 40 oder als flexible Schlauchleitung 40' an ein Mehrwegeventil 24 anschließt, das am hydraulischen Antrieb befindlich die Hochdruckpumpe 20 entweder mit dem Speicherraum 34 oder mit dem externen Hydraulikspeicher verbindet. Dieser Hydraulikspeicher besteht aus einem Druckgehäuse 10', das gleichartig gestaltet ist wie das Druckgehäuse 10 des hydraulischen Antriebs.In Figure 5 is shown schematically how an external hydraulic accumulator 10 ', 16', 26 'connects via a connecting line either as a rigid pipe 40 or as a flexible hose 40' to a multi-way valve 24, which is located on the hydraulic drive, the high pressure pump 20 either with the Storage space 34 or connects to the external hydraulic accumulator. This hydraulic accumulator consists of a pressure housing 10 ', which is designed in the same way as the pressure housing 10 of the hydraulic drive.

Der zylindrische Innenraum wird von einem Speicherkolben 16' unterteilt in einen Speicherraum 30' und in einen zweiten Bereich, der die als Speicherelement vorgesehene Federanordnung 26' aufnimmt.The cylindrical interior is divided by a storage piston 16 'into a storage space 30' and into a second area, which receives the spring arrangement 26 'provided as a storage element.

Im Beispiel ist die Versorgung mit Druckfluid über die Verbindungsleitung (40,40') durch die Hochdruckpumpe 20 vorgesehen, wobei das zwischengeschaltete Mehrwegeventil den Speicherraum 30 gegen Druckabfall sichert.In the example, the supply of pressurized fluid via the connecting line (40, 40 ') through the high-pressure pump 20 is provided, the intermediate multi-way valve securing the storage space 30 against a drop in pressure.

Schaltungstechnisch ist vorgesehen, daß bei Bedarf das im externen Hydraulikspeicher befindliche Druckfluid in den Speicherraum 30 fließt infolge der von der Federanordnung 26' ausgehenden gespeicherten Kraft, so daß eine zusätzliche Zahl von Schaltvorgängen gewährleistet ist.In terms of circuitry, it is provided that, if necessary, the pressure fluid in the external hydraulic accumulator flows into the storage space 30 due to the stored force emanating from the spring arrangement 26 ', so that an additional number of switching operations is ensured.

Claims (14)

1. Hydraulic drive, in particular for power circuit-breakers, having a working piston (18) designed as a differential piston and provided with a piston rod (28) passing centrally through the pressure housing (10), which working piston is guided in a one-sided axial recess (12, 14) located in a pressure housing (10) and on one side (30, 36) is constantly under the force of an energy store (26) and whose other side (38) can be optionally pressurized or depressurized, characterized in that the recess (12, 14) receiving the working piston (18) has inserted in it a storage piston (16), which bears against the energy store formed by springs (26) arranged symmetrical to its centre axis, in that the piston rod (28) passes centrally through the storage piston (16), in that storage piston (16) with the piston rod (28), the wall of the recess (12) and the working piston (18) delimit a storage space (30) which, as a hydraulic store, provides pressure energy for supplying the hydraulic drive without any further feeding of outside energy, in that the consumed hydraulic fluid can be fed to a collecting space (34) which is under low pressure and is delimited by the side of the storage piston (16) facing away from the storage space (30), the wall and the bottom (32) of the recess and the piston rod (28), and in that the storage space (30) is separated from the collecting space (34) by the storage piston (16).
2. Hydraulic drive according to Claim 1, characterized in that the recess (12, 14) in the pressure housing (10) is a cylinder bore (12, 14) tapering in offset stages, the working piston (18) being guided in the bore having the smaller diameter, serving as working cylinder (14), and the storage piston is guided in the bore having the larger diameter, serving as storage cylinder (12), and said recess is closed tightly by means of a housing cover (32).
3. Hydraulic drive according to Claim 2, characterized in that the working cylinder (14) has at its end facing the storage cylinder (12) an interlocking device (46) which fixes the working piston (18) in working position, i.e. in its end position of the working piston (18) closest to the storage piston (16).
4. Hydraulic drive according to at least one of the preceding claims, characterized in that a high-pressure pump (20) for filling the storage space (30) and a hydraulic control unit (22) for controlling the movement of the working piston (18) are positively integrated in the pressure housing (10).
5. Hydraulic drive according to Claim 4, characterized in that fluid channels (50, 52, 54, 56, 58) are made in the pressure housing (10) for connecting the high-pressure pump (20) to the storage space (30) and to the collecting space (34) and also for connecting the storage space (30) to the control unit (22) and for connecting the control unit (22) to the working space (A 38) and the collecting space (34).
6. Hydraulic drive according to at least one of the preceding claims, characterized in that the storage piston (16) and the energy store as spring arrangement (26) are rigidly coupled to each other.
7. Hydraulic drive according to at least one of the preceding claims, characterized in that the energy store designed as spring arrangement (26) bears on the one hand against a thrust piece (60), which adjoins the storage piston (16) by means of transmission rods (62) and is guided by the end of the pressure housing (10) facing away from the cylindrically shaped recess (12, 14), and on the other hand bears against the pressure housing (10) on the side facing away from the recess (12, 14).
8. Hydraulic drive according to at least one of the preceding claims, characterized in that the energy store (26) is arranged concentric to the centre axis of the storage piston (16) and is preferably formed from laminated cup springs (80).
9. Hydraulic drive according to at least one of Claims 2 - 8, characterized in that a switch flange (124) is formed on the housing cover (32), on the side facing away from the pressure housing (10), which switch flange can be flanged to an electrical power circuit-breaker (100).
10- Hydraulic drive according to at least one of the preceding claims, characterized in that a mechanical adjustment indicator (120) of the storage piston (16) is provided, corresponding to the available remaining quantity of pressure fluid in the storage space (30).
11. Hydraulic drive according to at least one of Claims 2 -10, characterized in that an electrical adjustment indicator (128) for the working piston (18) is fastened on the housing cover (32), which adjustment indicator is connected to a coupling (132) via a lever with slide piece (130) for conversion of the translatory movement of the working piston (18) into a rotational movement, which coupling is rigidly connected to the working piston (18) and simultaneously actuates an optical adjustment indicator (126).
12. Hydraulic drive according to at least one of the preceding claims, characterized in that at least one external hydraulic store (10', 16', 26'), for the additional provision of pressure fluid, is connected to the storage space (30) via a pipeline (40) or a hoseline (40').
13. Hydraulic drive according to Claim 12, characterized in that the connecting line (40,40') is connected to a valve (24) arranged at the storage space (30), so that it is protected against a pressure drop.
14. Hydraulic drive according to one of Claims 12 or 13, characterized in that the external hydraulic store (10', 16', 26') can be fed with pressure fluid via the connecting line (40,40') by the high-pressure pump (20) of the hydraulic drive.
EP85101751A 1984-03-10 1985-02-16 Hydraulic drive Expired EP0158054B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3408909 1984-03-10
DE19843408909 DE3408909A1 (en) 1984-03-10 1984-03-10 HYDRAULIC DRIVE

Publications (2)

Publication Number Publication Date
EP0158054A1 EP0158054A1 (en) 1985-10-16
EP0158054B1 true EP0158054B1 (en) 1987-01-14

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US (1) US4716812A (en)
EP (1) EP0158054B1 (en)
JP (1) JPH076531B2 (en)
DE (2) DE3408909A1 (en)

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DE3611497A1 (en) * 1986-04-05 1987-10-08 Bbc Brown Boveri & Cie Drive device for sulphur hexafluoride high-voltage power circuit breakers
DE3611501A1 (en) * 1986-04-05 1987-10-08 Bbc Brown Boveri & Cie DRIVE FOR GENERATING A LINEAR MOVEMENT FOR A CONSUMER
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Also Published As

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DE3408909A1 (en) 1985-09-12
JPS60208613A (en) 1985-10-21
EP0158054A1 (en) 1985-10-16
US4716812A (en) 1988-01-05
JPH076531B2 (en) 1995-01-30
DE3560057D1 (en) 1987-02-19

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