EP0715580A1 - Device for changing points - Google Patents

Device for changing points

Info

Publication number
EP0715580A1
EP0715580A1 EP95921646A EP95921646A EP0715580A1 EP 0715580 A1 EP0715580 A1 EP 0715580A1 EP 95921646 A EP95921646 A EP 95921646A EP 95921646 A EP95921646 A EP 95921646A EP 0715580 A1 EP0715580 A1 EP 0715580A1
Authority
EP
European Patent Office
Prior art keywords
piston
cylinder
hydraulic
spaces
valves
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.)
Granted
Application number
EP95921646A
Other languages
German (de)
French (fr)
Other versions
EP0715580B1 (en
Inventor
Gerald Durchschlag
Herbert Achleitner
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.)
Voestalpine Railway Systems GmbH
Original Assignee
Voestalpine VAE GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Voestalpine VAE GmbH filed Critical Voestalpine VAE GmbH
Priority to SI9530154T priority Critical patent/SI0715580T1/en
Publication of EP0715580A1 publication Critical patent/EP0715580A1/en
Application granted granted Critical
Publication of EP0715580B1 publication Critical patent/EP0715580B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B61—RAILWAYS
    • B61L—GUIDING RAILWAY TRAFFIC; ENSURING THE SAFETY OF RAILWAY TRAFFIC
    • B61L5/00—Local operating mechanisms for points or track-mounted scotch-blocks; Visible or audible signals; Local operating mechanisms for visible or audible signals
    • B61L5/04—Fluid-pressure devices for operating points or scotch-blocks
    • B61L5/045—Fluid-pressure devices for operating points or scotch-blocks using electrically controlled fluid-pressure operated driving means

Definitions

  • the invention relates to a device for switching switches, in which a plurality of hydraulic actuating devices coupled to one another are arranged offset in the longitudinal direction of the rails.
  • a mechanical linkage In such devices for switching points, it is known to carry out the connection of the individual closures with a mechanical linkage.
  • a mechanical connection of a plurality of actuating devices or closures requires a relatively large amount of space and a large number of individual parts which are different from one another.
  • the pluggability of the tongue device is impaired with such a mechanical connection and, moreover, an unfavorable one-sided mass distribution is effected on a switch.
  • a hydraulic actuating device is already known from EP-A2 480 303, in which a plurality of individual adjusting cylinders are controlled via a hydraulic station.
  • Different circuit arrangements for the series connection or the parallel connection of a plurality of such hydraulic actuating devices are known from DE-B2 1952823.
  • the known hydraulic actuating devices each require a separate hydraulic drive unit, which overall gives a relatively complex construction.
  • the invention now aims to provide a device of the type mentioned at the outset, which can be easily retrofitted into existing switch devices and in which the effort for an additional drive unit and a correspondingly complex control system can be eliminated.
  • the invention aims at ensuring a high degree of reliability and susceptibility to malfunctions despite a simple construction requiring only a few different components.
  • the device according to the invention is intended to be a simple replacement for mechanical devices of known design can be used to improve the packability of the tongue device and to avoid the one-sided mass distribution on the switch.
  • the task according to the invention essentially consists in that at least one hydraulic cylinder piston unit is connected to a first mechanical actuating device, the cylinder chambers of which, as pump chambers, are connected to the work chambers of adjacent actuating devices formed by hydraulic cylinder piston units are connected in the same direction.
  • a first cylinder piston unit is used as a pump element means that complex drive units can be dispensed with.
  • the pump assembly displaces fluid from the respective work area into work areas of identically constructed cylinder piston assemblies, whereby the coupling with adjacent cylinder piston assemblies can be achieved directly.
  • such a device can be constructed with an identically constructed cylinder-piston assembly of particularly simple construction, only corresponding hydraulic lines being provided for the connection between adjacent cylinder-piston assemblies.
  • the interconnection takes place in such a way that adjacent cylinder piston assemblies are adjusted in the same direction when medium is pressed out of the first passive cylinder piston unit driven by the mechanical actuating device.
  • the design according to the invention is developed in such a way that the pump element and the hydraulic actuating devices each contain a floating piston or plunger guided between two work spaces in a cylinder, the end faces or ring surfaces of the plunger respectively immersing in the opposite work spaces Pistons or plungers have identical cross-sectional area.
  • a floating piston or plunger represents a structurally particularly simple, reliable and compact structural unit, which takes up the desired space in a small space Place can be arranged.
  • a plurality of identical cylinder-piston assemblies of this type can be provided, the main advantage being that pressure is applied to identical cross-sectional areas, which results in a synchronous movement.
  • the corresponding cross-sectional correction can be carried out in a simple manner by means of sealing elements or packings in such a configuration in order to ensure the respectively required adjustment path with a constant, displaced volume.
  • Such a hydraulic actuating device with floating pistons or plungers thus, in addition to its compact design, also easily adapts to the respectively required requirements.
  • the design can advantageously be such that the piston or plunger of the pump element has a bearing, in particular a sliding block with an annular groove or a bearing eye between it has free ends and that the bearing is protruding from an opening in the cylinder or between two fixed cylinders.
  • a particularly simple and reliable compact design is possible, which is also suitable for subsequent installation in a simple manner.
  • the annular surface of a piston can, as already mentioned above, ensure the required identical working cross section in both directions of displacement.
  • a particularly simple construction is achieved in this case in that the piston is rigidly connected to a continuous piston rod which penetrates the cylinder and that the piston rod or the cylinder is fixed in place.
  • the entire system is advantageously set at a predetermined excess pressure in relation to the atmospheric pressure. In this way, temperature fluctuations, which could lead to a change in pressure, can be buffered, for which purpose the design is advantageously made such that the working spaces of the cylinder-piston units are connected to a pressure accumulator via pressure relief valves.
  • the overpressure valves are designed as controllable check valves, such controllable check valves resulting in a high degree of operational reliability. At high operating temperatures, medium is pressed out into the pressure accumulator by opening the check valves, whereas if the pressure drops, the pressure can be made available to the system again via the check valves.
  • the design can be made in a particularly simple manner in such a way that a pressure-controlled directional control valve is connected to each of the pump work spaces which, when falling below a predetermined pressure, comes into the closed position, which ensures that in this case all adjusting devices are blocked. Blocking of the actuating devices would be signaled by the mechanical actuator and the corresponding control devices for the mechanical actuator at the corresponding point, so that the damage can be remedied immediately.
  • An alternative to changing the cross-section to control a different adjustment position along the rail path is an embodiment which is preferably arranged such that blow-open valves are arranged in a line connecting the two working spaces of a cylinder piston unit, for example in the form of a bore . Depending on the piston or plunging position, this connection is interrupted or it there is flow, whereby the target position can be reached exactly.
  • FIG. 1 shows a plan view of a partial area of a rail switch
  • FIG. 2 shows a detail of the connection of a cylinder-piston unit with a mechanical slide rod
  • FIG. 3 shows a schematic partial view of the illustration according to FIG. 2
  • FIG. 4 shows an enlarged illustration of the Fig. 5 shows a top view of the representation according to Fig. 4
  • Fig. 6 shows a schematic representation of the hydraulic connection of the individual cylinder piston assemblies
  • Fig. 7 shows a modified design of the hydraulic connection
  • Fig. 8 shows an alternative arrangement of hydraulic cylinder piston units in the course of the track
  • FIGS. 9, 10 and 11 further alternative designs of cylinder piston units for the device according to the invention.
  • Fig.l rails 1 are schematically indicated, which are connected to sleepers 2.
  • tongue rails 3 are provided in addition to the control rails 1, which can be brought into their respective positions via an actuator, which is schematically designated by 4.
  • Actuator 4 acts on slide rails 5 via slide rods 5.
  • Slide rods 5 are coupled to a hydraulic cylinder piston unit 7 via a central tap 6. Additional hydraulic cylinder-piston units 7 in the course of the rail can also be seen, each of which is coupled to slide rods and locking devices, which in turn are denoted schematically by 5.
  • FIG. 2 the type of mechanical connection of the hydraulic cylinder piston assemblies 7 to the slide rods 5 can be seen more clearly.
  • the cylinder-piston units 7 have a sliding block 8, in which a bolt 9 of the slide rod 5 engages. When the slide rod 5 is actuated, the sliding block and thus the piston of the hydraulic cylinder piston units shifted, whereby medium is pressed out of the respective work space.
  • the type of fixing of the hydraulic cylinder piston units 7 on the threshold 2 is illustrated in FIG. The determination is made via a stop plate 10, which is fixed on the threshold 2.
  • the hydraulic. Cylinder piston units 7 require relatively little space so that the plugging of the substructure is not impaired.
  • FIGS. 4 and 5 show a hydraulic cylinder piston unit 7 having a plunger 11.
  • the plungers 11 plunge into the respective work spaces 13 of the hydraulic cylinder piston units via seals 12, and when the plunger 11 is displaced in one of the directions of the double arrow 14, medium is pressed out of the corresponding work space 13.
  • the hydraulic connections lead to the external openings 15 in the respective work space 13.
  • the link block is again designated 8, via which the mechanical coupling takes place.
  • a rubber sleeve 16 is also provided.
  • FIG. 5 shows the device according to FIG. 4 in a top view.
  • identical cross sections are effective on both sides.
  • the cylinders of the hydraulic cylinder-piston unit are fixed via bolts 17 on the angle plate 10.
  • the working spaces 13 of the first hydraulic cylinder piston unit 7, which acts as a pump element, are connected via hydraulic lines 18 to corresponding working spaces 13 of adjacent hydraulic cylinder piston units 7, the connection being such that when the first hydraulic cylinder piston unit, as the pump element, is displaced all other hydraulic cylinder piston units 7 at the same meaningful shift are coupled.
  • the cross section must be influenced accordingly, for which purpose a corresponding sealing element can be arranged inside the cylinder to reduce the cross section.
  • the hydraulic lines 18 now contain a series of valves in order to keep the pressure constant under operating conditions and to be able to reliably detect impermissible situations.
  • a spring-loaded valve 19 is provided, which is acted upon by the hydraulic pressure in the lines 18. If the pressure in the hydraulic lines 18 drops below a limit value, the force of the spring of the spring-loaded valve 19 will move the spring-loaded valve 19 into the closed position, so that a further displacement of the hydraulic cylinder piston unit 7, which acts as a pump element, is prevented. In this case, the point machine is blocked and a corresponding fault message is issued.
  • a pressure accumulator 20 is also provided, which is connected to the respective hydraulic lines 18 via overflow valves or check valves 21.
  • the overflow valves or non-return valves are switched in such a way that when the pressure rises due to thermal expansion, fluid is pressed into the reservoir 20 and conversely, when the pressure drops slightly, fluid is pressed out of the hydraulic accumulator 20 into the lines 18.
  • the spring-loaded safety valves 19 only become effective in the event of a leak and a corresponding pressure drop in the accumulator 20.
  • FIG. 7 shows a simplified design of the hydraulic linkage.
  • the reference numerals from FIG. 6 have been retained in FIG.
  • a pressure accumulator 20 is connected to the entire hydraulic circuit, so that hydraulic fluid is returned to the accumulator 20 when a pressure relief valve 21 responds.
  • the preload valves or safety valves 19 are acted upon by the accumulator pressure of the piston accumulator. Overpressure can occur, especially if the temperature increases due to sunshine.
  • the piston chambers are in turn connected to one another in series, the pump element in turn being provided with the preload valves or safety valves 19. Both connecting lines are protected separately with pressure relief valves.
  • modified hydraulic cylinder piston units 7 are provided, each of which engages at the ends of the slide rods 5.
  • the modified cylinder-piston units 7 serve the same purpose as the design according to FIG. 1, but the functions for displacements to the left or to the right are separated from one another and no common plunger or piston is used for both working spaces finds.
  • FIG. 9 again shows a modified design of the hydraulic cylinder piston units.
  • the design is such that the same cross sections of a piston come into effect in the two work spaces 13.
  • the piston 22 is connected to a piston rod 23 and in the present case the ring surface is effective or acted upon.
  • the same components as in the embodiment according to FIG. 6 or 7 are used in this embodiment, and the same reference numerals have been used here again.
  • a blockage in the event of a drop in pressure of any cylinder-piston unit is brought about directly and all work spaces 13 are equipped with corresponding safety valves.
  • the individual adjustment paths of these closures can be roughly specified by determining the diameter ratios, and the poppet valves can be used to fine-tune the details by adjusting the path of the plunger by adjusting the cylinder base to the poppet valve.
  • the reference circuit of the push-open valves makes a new adjustment. A displacement of the piston due to leaks is thus remedied by re-adjustment after the changeover process has taken place.

Landscapes

  • Mechanical Engineering (AREA)
  • Engineering & Computer Science (AREA)
  • Actuator (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Selective Calling Equipment (AREA)
  • Vehicle Body Suspensions (AREA)
  • Measuring Pulse, Heart Rate, Blood Pressure Or Blood Flow (AREA)
  • Massaging Devices (AREA)
  • Investigation Of Foundation Soil And Reinforcement Of Foundation Soil By Compacting Or Drainage (AREA)
  • Structure Of Transmissions (AREA)
  • Confectionery (AREA)
  • Keying Circuit Devices (AREA)
  • Reciprocating Pumps (AREA)
  • Power Steering Mechanism (AREA)
  • Accommodation For Nursing Or Treatment Tables (AREA)
  • Machines For Laying And Maintaining Railways (AREA)
  • Transmitters (AREA)
  • Supplying Of Containers To The Packaging Station (AREA)
  • Pens And Brushes (AREA)
  • Motor Or Generator Current Collectors (AREA)
  • Train Traffic Observation, Control, And Security (AREA)
  • Electric Propulsion And Braking For Vehicles (AREA)

Abstract

The points-changing device described has a multiplicity of interlinked hydraulic control devices (7) spaced at intervals along the line. A mechanical control device is connected to the first hydraulic cylinder/piston unit (7) which is designed to act as a pump, the swept space (13) in this unit (7) being connected up to the swept spaces (13) of subsequent hydraulic cylinder/piston units (7) such that all pump in the same direction.

Description

Einrichtung zum Umstellen von Weichen Device for switching switches

Die Erfindung bezieht sich auf eine Einrichtung zum Umstellen von Weichen, bei welcher eine Mehrzahl von miteinander gekuppel- ten hydraulischen Stelleinrichtungen in Schienenlängsrichtung versetzt angeordnet ist. Bei derartigen Einrichtungen zum Umstellen von Weichen ist es bekannt, die Verbindung der einzel¬ nen Verschlüsse mit einem mechanischen Gestänge durchzuführen. Eine derartige mechanische Verbindung einer Mehrzahl von Stell- einrichtungen bzw. Verschlüssen erfordert aber relativ viel Platz sowie eine große Anzahl von voneinander verschiedenen Einzelteilen. Zusätzlich zu dem erhöhten Platzbedarf wird bei einer derartigen mechanischen Verbindung die Stopfbarkeit der Zungenvorrichtung beeinträchtigt und es wird darüberhinaus eine ungünstige einseitige Massenverteilung an einer Weiche bewirkt.The invention relates to a device for switching switches, in which a plurality of hydraulic actuating devices coupled to one another are arranged offset in the longitudinal direction of the rails. In such devices for switching points, it is known to carry out the connection of the individual closures with a mechanical linkage. However, such a mechanical connection of a plurality of actuating devices or closures requires a relatively large amount of space and a large number of individual parts which are different from one another. In addition to the increased space requirement, the pluggability of the tongue device is impaired with such a mechanical connection and, moreover, an unfavorable one-sided mass distribution is effected on a switch.

Aus der EP-A2 480 303 ist bereits eine hydraulische Stellein¬ richtung bekannt, bei welcher über eine Hydraulikstation eine Mehrzahl von einzelnen Verstellzylindern angesteuert wird. Aus der DE-B2 1952823 sind unterschiedliche Schaltungsanordnungen für die Reihenschaltung oder die Parallelschaltung einer Mehr¬ zahl derartiger hydraulischer Stelleinrichtungen bekannt.A hydraulic actuating device is already known from EP-A2 480 303, in which a plurality of individual adjusting cylinders are controlled via a hydraulic station. Different circuit arrangements for the series connection or the parallel connection of a plurality of such hydraulic actuating devices are known from DE-B2 1952823.

Die bekannten hydraulischen Stelleinrichtungen erfordern jeweils ein separates hydraulisches Antriebsaggregat, wodurch insgesamt eine relativ aufwendige Konstruktion gegeben ist.The known hydraulic actuating devices each require a separate hydraulic drive unit, which overall gives a relatively complex construction.

Die Erfindung zielt nun darauf ab, eine Einrichtung der eingangs genannten Art zu schaffen, welche in einfacher Weise nachträg- lieh in bestehende Umstellvorrichtungen von Weichen eingebaut werden kann und bei welcher der Aufwand für ein zusätzliches Antriebsaggregat und eine entsprechend aufwendige Steuerung ent¬ fallen kann. Insbesondere zielt die Erfindung hiebei darauf ab, trotz einer nur geringe verschiedene Bauteile erfordernden ein- fachen Bauweise ein hohes Maß an Zuverlässigkeit und Störungs- unanfälligkeit zu gewährleisten. Schließlich soll die erfin¬ dungsgemäße Einrichtung in einfacher Weise als Austausch für mechanische Einrichtungen bekannter Bauweise Verwendung finden können, um die Stopfbarkeit der Zungenvorrichtung zu verbessern und die einseitige Massenverteilung an der Weiche zu vermeiden.The invention now aims to provide a device of the type mentioned at the outset, which can be easily retrofitted into existing switch devices and in which the effort for an additional drive unit and a correspondingly complex control system can be eliminated. In particular, the invention aims at ensuring a high degree of reliability and susceptibility to malfunctions despite a simple construction requiring only a few different components. Finally, the device according to the invention is intended to be a simple replacement for mechanical devices of known design can be used to improve the packability of the tongue device and to avoid the one-sided mass distribution on the switch.

Zur Lösung dieser Aufgabe besteht die erfindungsgemäße Aufgabe im wesentlichen darin, daß mit einer ersten mechanischen Stell¬ einrichtung wenigstens ein hydraulisches Zylinderkolbenaggregat verbunden ist, dessen bzw. deren Zylinderräume als Pumpen¬ arbeitsräume mit den Arbeitsräumen von benachbarten, von hydrau- lischen Zylinderkolbenaggregaten gebildeten Stelleinrichtungen zu gleichsinnigem Antrieb verbunden sind. Dadurch, daß ein erstes Zylinderkolbenaggregat als Pumpelement Verwendung findet, kann auf aufwendige Antriebsaggregate verzichtet werden. Das Pumpenaggregat verdrängt bei einem Umstellvorgang Fluid aus dem jeweiligen Arbeitsraum in Arbeitsräume von identisch aufgebauten Zylinderkolbenaggregaten, wodurch unmittelbar die Kopplung mit benachbarten Zylinderkolbenaggregaten erzielt werden kann. Ins¬ gesamt kann eine derartige Einrichtung mit identisch bauenden Zylinderkolbenaggregaten besonders einfacher Bauweise aufgebaut werden, wobei zur Verbindung zwischen benachbarten Zylinderkol¬ benaggregaten lediglich entsprechende Hydraulikleitungen vorzu¬ sehen sind. Die Zusammenschaltung erfolgt jeweils so, daß eine gleichsinnige Verstellung benachbarter Zylinderkolbenaggregate bewirkt wird, wenn Medium aus dem ersten passiven und durch die mechanische Stelleinrichtung angetriebenen Zylinderkolbenaggre¬ gat ausgepreßt wird.To achieve this object, the task according to the invention essentially consists in that at least one hydraulic cylinder piston unit is connected to a first mechanical actuating device, the cylinder chambers of which, as pump chambers, are connected to the work chambers of adjacent actuating devices formed by hydraulic cylinder piston units are connected in the same direction. The fact that a first cylinder piston unit is used as a pump element means that complex drive units can be dispensed with. During a changeover process, the pump assembly displaces fluid from the respective work area into work areas of identically constructed cylinder piston assemblies, whereby the coupling with adjacent cylinder piston assemblies can be achieved directly. Overall, such a device can be constructed with an identically constructed cylinder-piston assembly of particularly simple construction, only corresponding hydraulic lines being provided for the connection between adjacent cylinder-piston assemblies. The interconnection takes place in such a way that adjacent cylinder piston assemblies are adjusted in the same direction when medium is pressed out of the first passive cylinder piston unit driven by the mechanical actuating device.

In besonders einfacher Weise ist die erfindungsgemäße Ausbildung so weitergebildet, daß das Pumpelement und die hydraulischen Stelleinrichtungen je einen schwimmenden Kolben bzw. Plunger zwischen zwei Arbeitsräumen geführt in einem Zylinder enthalten, wobei die jeweils in die einander gegenüberliegenden Arbeits¬ räume eintauchenden Stirn- oder Ringflächen des Kolbens bzw. Plungers identische Querεchnittsflache aufweisen. Ein derartiger schwimmender Kolben bzw. Plunger stellt eine konstruktiv beson¬ ders einfache, betriebssichere und kompakte Baueinheit dar, welche mit geringem Platzbedarf jeweils an der gewünschten Stelle angeordnet werden kann. Es kann eine Mehrzahl von identi¬ schen derartigen Zylinderkolbenaggregaten vorgesehen sein, wobei der wesentliche Vorteil darin liegt, daß jeweils identische Querschnittsflächen mit Druckmittel beaufschlagt werden, wodurch sich eine synchrone Bewegung ergibt.In a particularly simple manner, the design according to the invention is developed in such a way that the pump element and the hydraulic actuating devices each contain a floating piston or plunger guided between two work spaces in a cylinder, the end faces or ring surfaces of the plunger respectively immersing in the opposite work spaces Pistons or plungers have identical cross-sectional area. Such a floating piston or plunger represents a structurally particularly simple, reliable and compact structural unit, which takes up the desired space in a small space Place can be arranged. A plurality of identical cylinder-piston assemblies of this type can be provided, the main advantage being that pressure is applied to identical cross-sectional areas, which results in a synchronous movement.

Wenn eine nicht lineare Verstellung gewünscht wird, kann bei einer derartigen Ausbildung in einfacher Weise durch Dichtungs¬ elemente bzw. Packungen die entsprechende QuerSchnittskorrektur vorgenommen, um bei jeweils gleichbleibendem, verdrängtem Volu¬ men den jeweils geforderten Verstellweg sicherzustellen. Eine derartige hydraulische Stelleinrichtung mit schwimmenden Kolben bzw. Plungern bildet somit neben seiner kompakten Bauweise auch in einfacher Weise die Anpassung an die jeweils gewünschten Erfordernisse.If a non-linear adjustment is desired, the corresponding cross-sectional correction can be carried out in a simple manner by means of sealing elements or packings in such a configuration in order to ensure the respectively required adjustment path with a constant, displaced volume. Such a hydraulic actuating device with floating pistons or plungers thus, in addition to its compact design, also easily adapts to the respectively required requirements.

Zur Kopplung der hydraulischen Stellvorrichtungen bzw. des Pump¬ zylinders mit den mechanischen Stelleinrichtungen kann die Aus¬ bildung mit Vorteil so getroffen sein, daß der Kolben bzw. Plun- ger des Pumpelementes ein Lager, inbesondere einen Kulissenstein mit einer Ringnut oder ein Lagerauge zwischen seinen freien Enden aufweist und daß das Lager aus einer Durchbrechung des Zylinders vorragend oder zwischen zwei ortsfest festgelegten Zylindern angeordnet ist. Auch hier ist wiederum eine besonders einfache und betriebssichere kompakte Ausbildung möglich, welche sich auch für den nachträglichen Einbau in einfacher Weise eig¬ net.To couple the hydraulic actuators or the pump cylinder to the mechanical actuators, the design can advantageously be such that the piston or plunger of the pump element has a bearing, in particular a sliding block with an annular groove or a bearing eye between it has free ends and that the bearing is protruding from an opening in the cylinder or between two fixed cylinders. Here again, a particularly simple and reliable compact design is possible, which is also suitable for subsequent installation in a simple manner.

Anstelle der eingangs erwähnten Plunger bzw. schwimmenden Kolben kann, wie bereits oben erwähnt, jeweils die Ringfläche eines Kolbens den geforderten identischen Arbeitsquerschnitt in beide Verschieberichtungen gewährleisten. Eine besonders einfache Kon¬ struktion wird in diesem Falle dadurch erreicht, daß der Kolben mit einer durchgehenden und die Zylinder dichtend durchsetzenden Kolbenstange starr verbunden ist und daß die Kolbenstange oder der Zylinder ortsfest festgelegt ist. Um ein hohes Maß an Betriebssicherheit zu gewährleisten, ist mit Vorteil das Gesamtsystem unter einem vorbestimmten Überdruck gegenüber dem atmosphärischen Druck eingestellt. Auf diese Weise können Temperaturschwankungen, welche zu einer Druckänderung führen könnten, gepuffert werden, wofür mit Vorteil die Ausbil¬ dung so getroffen ist, daß die Arbeitsräume der Zylinderkolben¬ aggregate über Überdruckventile mit einem Druckspeicher verbun¬ den sind. In besonders einfacher Weise sind hiebei die Über¬ druckventile als aufsteuerbare Rückschlagventile ausgebildet, wobei derartige aufsteuerbare Rückschlagventile ein hohes Maß an Betriebssicherheit ergeben. Bei hohen Betriebstemperaturen wird Medium durch Aufsteuerung der Rückschlagventile in den Druck¬ speicher hinausgepreßt, wohingegen bei einem Absinken des Druckes der Druck über die Rückschlagventile in das System wie- deru zur Verfügung gestellt werden kann. Um bei einer derarti¬ gen Ausbildung sicherzustellen, daß dann, wenn im Leitungssystem ein Leck auftritt, die Betriebssicherheit durch rechtzeitige Warnung weiterhin gewährleistet ist, kann die Ausbildung in besonders einfacher Weise so getroffen sein, daß an die Pumpen- arbeitsräume je ein druckgesteuertes Wegeventil angeschlossen ist, welches bei Unterschreiten eines vorgegebenen Druckes in Schließstellung gelangt, wodurch sichergestellt ist, daß in diesem Fall sämtliche Stelleinrichtungen blockiert werden. Ein Blockieren der Stelleinrichtungen würde vom mechanischen Stell- antrieb und den entsprechenden Kontrollvorrichtungen für den mechanischen Stellantrieb an der entsprechenden Stelle signali¬ siert werden, sodaß die Behebung des Schadens unmittelbar veran¬ laßt werden kann.Instead of the plungers or floating pistons mentioned at the outset, the annular surface of a piston can, as already mentioned above, ensure the required identical working cross section in both directions of displacement. A particularly simple construction is achieved in this case in that the piston is rigidly connected to a continuous piston rod which penetrates the cylinder and that the piston rod or the cylinder is fixed in place. In order to ensure a high degree of operational safety, the entire system is advantageously set at a predetermined excess pressure in relation to the atmospheric pressure. In this way, temperature fluctuations, which could lead to a change in pressure, can be buffered, for which purpose the design is advantageously made such that the working spaces of the cylinder-piston units are connected to a pressure accumulator via pressure relief valves. In a particularly simple manner, the overpressure valves are designed as controllable check valves, such controllable check valves resulting in a high degree of operational reliability. At high operating temperatures, medium is pressed out into the pressure accumulator by opening the check valves, whereas if the pressure drops, the pressure can be made available to the system again via the check valves. In order to ensure, in the case of such a design, that if a leak occurs in the line system, operational safety is still ensured by timely warning, the design can be made in a particularly simple manner in such a way that a pressure-controlled directional control valve is connected to each of the pump work spaces which, when falling below a predetermined pressure, comes into the closed position, which ensures that in this case all adjusting devices are blocked. Blocking of the actuating devices would be signaled by the mechanical actuator and the corresponding control devices for the mechanical actuator at the corresponding point, so that the damage can be remedied immediately.

Eine zur Querschnittsänderung alternative Methode zur Ansteue- rung einer längs des Schienenweges unterschiedlichen Verstell¬ position stellt eine Ausbildung dar, die bevorzugt so getroffen wird, daß in einer die beiden Arbeitsräume eines Zylinderkolben¬ aggregates verbindenden Leitung, z.B. in Form einer Bohrung, Aufstoßventile angeordnet sind. Abhängig von der Kolben- bzw. Plungenstellung wird diese Verbindung unterbrochen oder es herrscht Durchfluß, wobei die Sollposition genau erreicht werden kann.An alternative to changing the cross-section to control a different adjustment position along the rail path is an embodiment which is preferably arranged such that blow-open valves are arranged in a line connecting the two working spaces of a cylinder piston unit, for example in the form of a bore . Depending on the piston or plunging position, this connection is interrupted or it there is flow, whereby the target position can be reached exactly.

Die Erfindung wird nachfolgend anhand von in der Zeichnung sche- matisch dargestellten Ausführungsbeispielen näher erläutert. In dieser zeigen Fig.l eine Draufsicht auf einen Teilbereich einer Schienenweiche, Fig.2 ein Detail der Verbindung eines Zylinder¬ kolbenaggregates mit einer mechanischen Schieberstange, Fig.3 eine schematische Teilansicht der Darstellung nach Fig.2, Fig.4 eine vergrößerte Darstellung des hydraulischen Zylinderkolben¬ aggregates teilweise im Schnitt, Fig.5 eine Draufsicht auf die Darstellung nach Fig.4, Fig.6 eine schematische Darstellung der hydraulischen Verbindung der einzelnen Zylinderkolbenaggregate, Fig.7 eine abgewandelte Ausbildung der hydraulischen Verbindung, Fig.8 eine alternative Anordnung von hydraulischen Zylinderkol¬ benaggregaten im Gleisverlauf und Fig.9, Fig.10 und Fig.11 weitere alternative Ausbildungen von Zylinderkolbenaggregaten für die erfindungsgemäße Einrichtung.The invention is explained in more detail below on the basis of exemplary embodiments schematically illustrated in the drawing. 1 shows a plan view of a partial area of a rail switch, FIG. 2 shows a detail of the connection of a cylinder-piston unit with a mechanical slide rod, FIG. 3 shows a schematic partial view of the illustration according to FIG. 2, and FIG. 4 shows an enlarged illustration of the Fig. 5 shows a top view of the representation according to Fig. 4, Fig. 6 shows a schematic representation of the hydraulic connection of the individual cylinder piston assemblies, Fig. 7 shows a modified design of the hydraulic connection, Fig. 8 shows an alternative arrangement of hydraulic cylinder piston units in the course of the track and FIGS. 9, 10 and 11 further alternative designs of cylinder piston units for the device according to the invention.

In Fig.l sind schematisch Schienen 1 angedeutet, welche mit Schwellen 2 verbunden sind. Im Bereich einer Weiche sind zusätz¬ lich zu den Regelschienen 1 Zungenschienen 3 vorgesehen, welche über einen Stellantrieb, welcher schematisch mit 4 bezeichnet ist, in ihre jeweilige Position gebracht werden können. Der Stellantrieb 4 wirkt hiebei über SchieberStangen 5 auf die Zun¬ genschienen 3. Die Schieberstangen 5 sind über einen mittigen Abgriff 6 mit einem hydraulischen Zylinderkolbenaggregat 7 ge¬ koppelt. Es sind weiters zusätzliche hydraulische Zylinderkol¬ benaggregate 7 im Schienenverlauf ersichtlich, welche jeweils mit Schieberstangen und Verschlußeinrichtungen, welche wiederum schematisch mit 5 bezeichnet werden, gekoppelt sind. Bei der Darstellung in Fig.2 ist die Art der mechanischen Verbindung der hydraulischen Zylinderkolbenaggreate 7 mit den Schieberstangen 5 deutlicher ersichtlich. Die Zylinderkolbenaggregate 7 weisen ei- nen Kulissenstein 8 auf, in welchen ein Bolzen 9 der Schieber¬ stange 5 eingreift. Bei Betätigung der Schieberstange 5 wird der Kulissenstein und damit der Kolben der hydraulischen Zylinder- kolbenaggregate verschoben, wodurch aus dem jeweiligen Arbeits¬ raum Medium ausgepreßt wird. In Fig.3 ist die Art der Festlegung der hydraulischen Zylinderkolbenaggregate 7 an der Schwelle 2 verdeutlicht. Die Festlegung erfolgt über ein Anschlagblech 10, welches an der Schwelle 2 festgelegt ist. Die hydraulischer. Zy¬ linderkolbenaggregate 7 benötigen hiebei relativ geringen Platz, sodaß das Stopfen des Unterbaues nicht beeinträchtigt wird.In Fig.l rails 1 are schematically indicated, which are connected to sleepers 2. In the area of a switch, tongue rails 3 are provided in addition to the control rails 1, which can be brought into their respective positions via an actuator, which is schematically designated by 4. Actuator 4 acts on slide rails 5 via slide rods 5. Slide rods 5 are coupled to a hydraulic cylinder piston unit 7 via a central tap 6. Additional hydraulic cylinder-piston units 7 in the course of the rail can also be seen, each of which is coupled to slide rods and locking devices, which in turn are denoted schematically by 5. In the illustration in FIG. 2, the type of mechanical connection of the hydraulic cylinder piston assemblies 7 to the slide rods 5 can be seen more clearly. The cylinder-piston units 7 have a sliding block 8, in which a bolt 9 of the slide rod 5 engages. When the slide rod 5 is actuated, the sliding block and thus the piston of the hydraulic cylinder piston units shifted, whereby medium is pressed out of the respective work space. The type of fixing of the hydraulic cylinder piston units 7 on the threshold 2 is illustrated in FIG. The determination is made via a stop plate 10, which is fixed on the threshold 2. The hydraulic. Cylinder piston units 7 require relatively little space so that the plugging of the substructure is not impaired.

Die Funktionsweise der hydraulischen Zylinderkolbenaggregate und ihre bevorzugte Ausgestaltung ist in den Fig.4 und 5 näher erläutert. In Fig.4 und 5 ist ein Plunger 11 aufweisendes hy¬ draulisches Zylinderkolbenaggregat 7 ersichtlich. Die Plunger 11 tauchen über Dichtungen 12 in die jeweiligen Arbeitsräume 13 der hydraulischen Zylinderkolbenaggregate, und bei einer Verschie- bung des Plungers 11 in einer der Richtungen des Doppelpfeiles 14 wird jeweils Medium aus dem entsprechenden Arbeitsraum 13 ausgepreßt. Die Hydraulikanschlüsse münden an die außenliegenden Durchbrechungen 15 im jeweiligen Arbeitsraum 13. Der Kulissen- εtein ist wiederum mit 8 bezeichnet, über welchen die mecha- nische Kopplung erfolgt. Zum Schutz der Einrichtung ist weiters eine Gummimanschette 16 vorgesehen.The operation of the hydraulic cylinder piston units and their preferred embodiment is explained in more detail in FIGS. 4 and 5. 4 and 5 show a hydraulic cylinder piston unit 7 having a plunger 11. The plungers 11 plunge into the respective work spaces 13 of the hydraulic cylinder piston units via seals 12, and when the plunger 11 is displaced in one of the directions of the double arrow 14, medium is pressed out of the corresponding work space 13. The hydraulic connections lead to the external openings 15 in the respective work space 13. The link block is again designated 8, via which the mechanical coupling takes place. To protect the device, a rubber sleeve 16 is also provided.

In Fig.5 ist die Einrichtung nach Fig.4 in der Draufsicht er¬ sichtlich. Wie sich aus der Darstellung nach Fig.4 gleichfalls ergibt, sind bei einer derartigen Ausbildung des hydraulischen Zylinderkolbenaggregates jeweils zu beiden Seiten gleiche Quer¬ schnitte wirksam. Die Festlegung der Zylinder des hydraulischen Zylinderkolbenaggregates erfolgt über Bolzen 17 am Winkelblech 10.5 shows the device according to FIG. 4 in a top view. As can also be seen from the illustration in FIG. 4, with such a design of the hydraulic cylinder-piston unit, identical cross sections are effective on both sides. The cylinders of the hydraulic cylinder-piston unit are fixed via bolts 17 on the angle plate 10.

Wie sich aus Fig.6 ergibt, werden die Arbeitsräume 13 des ersten als Pumpelement wirksamen hydraulischen Zylinderkolbenaggregates 7 über Hydraulikleitungen 18 mit entsprechenden Arbeitsräumen 13 benachbarter Hydraulikzylinderkolbenaggregate 7 verbunden, wobei die Verbindung dergestalt erfolgt, daß bei einer Verschiebung des als Pumpelement ersten hydraulischen Zylinderkolbenaggrega¬ tes alle weiteren Hydraulikzylinderkolbenaggregate 7 zu gleich- sinniger Verschiebung gekoppelt sind. Wenn parallel oder in Serie geschaltete Hydraulikzylinderkolbenaggregate einen vom Weg des als Pumpelement verwendeten hydraulischen Zylinderkolben¬ aggregates verschiedenen Weg zurücklegen soll, muß der Quer- schnitt entsprechend beeinflußt werden, wofür im Inneren der Zylinder ein entsprechendes Dichtungselement zur Verringerung des Querschnittes angeordnet werden kann. Die Hydraulikleitungen 18 enthalten nun eine Reihe von Ventilen, um den Druck unter Betriebsbedingungen konstant zu halten und um unzulässige Situ- ationen sicher erfassen zu können. Im einzelnen ist ein federbe¬ lastetes Ventil 19 vorgesehen, welches vom Hydraulikdruck in den Leitungen 18 beaufschlagt wird. Wenn der Druck in den Hydraulik¬ leitungen 18 unter einen Grenzwert absinkt, wird die Kraft der Feder des federbelasteten Ventiles 19 das federbelastete Ventil 19 in die Schließstellung verschieben, sodaß eine weitere Ver¬ schiebung des als Pumpelement wirksamen Hydraulikzylinderkolben- aggregates 7 verhindert wird. In diesem Falle wird der Weichen¬ antrieb blockiert und eine entsprechende Störmeldung abgegeben.As can be seen from FIG. 6, the working spaces 13 of the first hydraulic cylinder piston unit 7, which acts as a pump element, are connected via hydraulic lines 18 to corresponding working spaces 13 of adjacent hydraulic cylinder piston units 7, the connection being such that when the first hydraulic cylinder piston unit, as the pump element, is displaced all other hydraulic cylinder piston units 7 at the same meaningful shift are coupled. If hydraulic cylinder piston units connected in parallel or in series are to cover a different path from the path of the hydraulic cylinder piston unit used as a pump element, the cross section must be influenced accordingly, for which purpose a corresponding sealing element can be arranged inside the cylinder to reduce the cross section. The hydraulic lines 18 now contain a series of valves in order to keep the pressure constant under operating conditions and to be able to reliably detect impermissible situations. In particular, a spring-loaded valve 19 is provided, which is acted upon by the hydraulic pressure in the lines 18. If the pressure in the hydraulic lines 18 drops below a limit value, the force of the spring of the spring-loaded valve 19 will move the spring-loaded valve 19 into the closed position, so that a further displacement of the hydraulic cylinder piston unit 7, which acts as a pump element, is prevented. In this case, the point machine is blocked and a corresponding fault message is issued.

Es ist weites ein Druckspeicher 20 vorgesehen, welcher über Überströmventile bzw. Rückschlagventile 21 mit den jeweiligen Hydraulikleitungen 18 verbunden ist. Die Überströmventile bzw. Rückschlagventile sind so geschaltet, daß bei einem Anstieg des Druckes aufgrund von thermischer Ausdehnung Fluid in den Spei- eher 20 gepreßt wird und umgekehrt bei einem geringfügigen Absinken des Druckes Fluid aus dem Hydraulikspeicher 20 in die Leitungen 18 zurückgepreßt wird. Erst bei einem Leck und bei ei¬ nem entsprechenden Druckabfall auch im Speicher 20 werden die federbelasteten Sicherheitsventile 19 wirksam.A pressure accumulator 20 is also provided, which is connected to the respective hydraulic lines 18 via overflow valves or check valves 21. The overflow valves or non-return valves are switched in such a way that when the pressure rises due to thermal expansion, fluid is pressed into the reservoir 20 and conversely, when the pressure drops slightly, fluid is pressed out of the hydraulic accumulator 20 into the lines 18. The spring-loaded safety valves 19 only become effective in the event of a leak and a corresponding pressure drop in the accumulator 20.

In Fig.7 ist eine vereinfachte Ausbildung des hydraulischen Ge¬ stänges ersichtlich. Die Bezugszeichen aus Fig.6 wurden in Fig.7 beibehalten. Wie bei der vereinfachten Ausbildung nach Fig.7 ersichtlich, kann hier mit einer geringeren Anzahl von Ventilen das Auslangen gefunden werden, wobei der gleiche Effekt erziel¬ bar ist. Auch hier ist, um Leckölverluste auszugleichen, an den gesamten Hydraulikkreislauf ein Druckspeicher 20 angeschlossen, sodaß Hydraulikflüssigkeit bei Ansprechen eines Überdruckventi- les 21 in den Speicher 20 rückgeführt wird. Die Vorspannventile bzw. Sicherheitsventile 19 werden vom Speicherdruck des Kolben¬ speichers beaufschlagt. Ein Überdruck kann insbesondere bei zu starker Erwärmung infolge Sonneneinstrahlung entstehen. Bei der Darstellung nach Fig.7 sind die Kolbenräume wiederum in Reihe geschaltet miteinander verbunden, wobei das Pumpelement wiederum mit den Vorspannventilen bzw. Sicherheitsventilen 19 versehen ist. Beide Verbindungsleitungen sind wiederum separat mit Über- druckventilen abgesichert.7 shows a simplified design of the hydraulic linkage. The reference numerals from FIG. 6 have been retained in FIG. As can be seen in the simplified design according to FIG. 7, it is possible to find sufficiency here with a smaller number of valves, the same effect being achievable. Here too, in order to compensate for leakage oil losses, a pressure accumulator 20 is connected to the entire hydraulic circuit, so that hydraulic fluid is returned to the accumulator 20 when a pressure relief valve 21 responds. The preload valves or safety valves 19 are acted upon by the accumulator pressure of the piston accumulator. Overpressure can occur, especially if the temperature increases due to sunshine. In the illustration according to FIG. 7, the piston chambers are in turn connected to one another in series, the pump element in turn being provided with the preload valves or safety valves 19. Both connecting lines are protected separately with pressure relief valves.

Bei der Darstellung nach Fig.8 sind abgewandelte Hydraulikzylin¬ derkolbenaggregate 7 vorgesehen, welche jeweils an den Enden der Schieberstangen 5 angreifen. Im Prinzip erfüllen die abgewandel- ten Zylinderkolbenaggregate 7 den gleichen Zweck wie die Ausbil¬ dung gemäß Fig.l, wobei jedoch die Funktionen für Verschiebungen nach links bzw. nach rechts voneinander getrennt sind und kein gemeinsamer Plunger bzw. Kolben für beide Arbeitsräume Verwen¬ dung findet.In the illustration according to FIG. 8, modified hydraulic cylinder piston units 7 are provided, each of which engages at the ends of the slide rods 5. In principle, the modified cylinder-piston units 7 serve the same purpose as the design according to FIG. 1, but the functions for displacements to the left or to the right are separated from one another and no common plunger or piston is used for both working spaces finds.

In Fig.9 ist wiederum eine abgewandelte Ausbildung der hydrau¬ lischen Zylinderkolbenaggregate ersichtich. Auch hier ist wiederum zum Zwecke, gleiche Arbeitsflächen mit Fluid zu beauf¬ schlagen, die Ausbildung so getroffen, daß in die beiden Arbeitsräume 13 jeweils gleiche Querschnitte eines Kolbens zur Wirkung gelangen. Der Kolben 22 ist mit einer Kolbenstange 23 verbunden und es wird im vorliegenden Fall jeweils die Ring¬ fläche wirksam oder beaufschlagt. Im übrigen finden bei dieser Ausbildung die gleichen Bauteile wie bei der Ausbildung nach Fig.6 oder 7 Verwendung, und es wurden hier wiederum die glei¬ chen Bezugszeichen verwendet. Abweichend von der Ausbildung nach Fig.6 oder 7 wird hier eine Blockade bei Druckabfall irgend eines beliebigen Zylinderkolbenaggregates unmittelbar bewirkt und es sind alle Arbeitsräume 13 mit entsprechenden Sicherheits- ventilen ausgestattet. In den Fig.10 und 11 sind die Arbeitsräume 13 eines Zylinder¬ kolbenaggregates 7 durch eine Leitung 24 in Form einer Bohrung miteinander verbunden, wobei Aufstoßventile 25 eingebaut sind. Diese Ventile bewirken bei entsprechender Einstellung die exakte geforderte wegabhängige Verstellung, wodurch auf die alternativ möglichen Querschnittsänderungen verzichtet werden kann.FIG. 9 again shows a modified design of the hydraulic cylinder piston units. Again, for the purpose of loading the same work surfaces with fluid, the design is such that the same cross sections of a piston come into effect in the two work spaces 13. The piston 22 is connected to a piston rod 23 and in the present case the ring surface is effective or acted upon. Otherwise, the same components as in the embodiment according to FIG. 6 or 7 are used in this embodiment, and the same reference numerals have been used here again. In contrast to the design according to FIG. 6 or 7, a blockage in the event of a drop in pressure of any cylinder-piston unit is brought about directly and all work spaces 13 are equipped with corresponding safety valves. 10 and 11, the working spaces 13 of a cylinder-piston unit 7 are connected to one another by a line 24 in the form of a bore, with poppet valves 25 being installed. With the appropriate setting, these valves effect the exact required travel-dependent adjustment, which means that the cross-section changes that are possible as an alternative can be dispensed with.

Die einzelnen Verstellwege dieser Verschlüsse können grob durch Festlegung der Durchmesserverhältnisse vorgegeben werden, wobei durch die Aufstoßventile eine exakte Detailabstimmung erfolgen kann, in dem der Weg des Plungers durch Einstellung des Zylin¬ derbodens zum Aufstoßventil einreguliert wird. Nach jedem Umsteilvorgang erfolgt durch die Referenzschaltung der Aufsto߬ ventile eine NeuJustierung. Eine Verschiebung des Kolbens durch Leckagen ist somit nach erfolgtem Umstellvorgang durch Neuju¬ stierung wieder behoben.The individual adjustment paths of these closures can be roughly specified by determining the diameter ratios, and the poppet valves can be used to fine-tune the details by adjusting the path of the plunger by adjusting the cylinder base to the poppet valve. After each change-over process, the reference circuit of the push-open valves makes a new adjustment. A displacement of the piston due to leaks is thus remedied by re-adjustment after the changeover process has taken place.

Durch Verwendung dieser einstellbaren Aufstoßventile ist ein hydraulischer Gleichlauf gegeben, d.h. , daß kein Verstellzylin- der vorlaufen kann und somit auch keine Zungenverspannungen auf¬ treten. Die Endlagen der Zungenschiene werden damit gezielt erreicht. By using these adjustable poppet valves, hydraulic synchronization is given, i.e. that no adjustment cylinder can advance and thus no tongue tension occurs. The end positions of the tongue rail are thus specifically reached.

Claims

Patentansprüche: Claims: 1. Einrichtung zum Umstellen von Weichen, bei welcher eine Mehr¬ zahl von miteinander gekuppelten hydraulischen Stelleinrichtun- gen in Schienenlängsrichtung versetzt angeordnet ist, dadurch gekennzeichnet, daß mit einer ersten mechanischen Stelleinrich¬ tung wenigstens ein hydraulisches Zylinderkolbenaggregat (7) verbunden ist, dessen bzw. deren Zylinderräume als Pumpen¬ arbeitsräume (13) mit den Arbeitsräumen (13) von benachbarten, von hydraulischen Zylinderkolbenaggregaten (7) gebildeten Stell¬ einrichtungen zu gleichsinnigem Antrieb verbunden sind.1. Device for switching switches, in which a plurality of coupled hydraulic actuating devices is arranged offset in the longitudinal direction of the rail, characterized in that at least one hydraulic cylinder piston unit (7) is connected to a first mechanical actuating device, the or whose cylinder spaces as pump work spaces (13) are connected to the work spaces (13) of adjacent actuating devices formed by hydraulic cylinder piston units (7) to drive in the same direction. 2. Einrichtung nach Anspruch 1, dadurch gekennzeichnet, daß das Pumpelement und die hydraulischen Stelleinrichtungen je einen schwimmenden Kolben (22) bzw. Plunger (11) zwischen zwei Arbeitsräumen (13) geführt in einem Zylinder enthalten, wobei die jeweils in die einander gegenüberliegenden Arbeitsräume (13) eintauchenden Stirn- oder Ringflächen des Kolbens (22) bzw. Plungers (11) identische Querschnittsfläche aufweisen.2. Device according to claim 1, characterized in that the pumping element and the hydraulic actuating devices each contain a floating piston (22) or plunger (11) guided between two working spaces (13) in a cylinder, each in the opposite working spaces (13) immersed end or ring surfaces of the piston (22) or plunger (11) have identical cross-sectional area. 3. Einrichtung nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß der Kolben (22) bzw. Plunger (11) des Pumpelementes ein La¬ ger, inbesondere einen Kulissenstein (8) mit einer Ringnut oder ein Lagerauge zwischen seinen freien Enden aufweist und daß das Lager aus einer Durchbrechung des Zylinders vorragend oder zwi¬ schen zwei ortsfest festgelegten Zylindern angeordnet ist.3. Device according to claim 1 or 2, characterized in that the piston (22) or plunger (11) of the pump element has a bearing, in particular a sliding block (8) with an annular groove or a bearing eye between its free ends and in that the bearing is protruding from an opening in the cylinder or is arranged between two fixed cylinders. 4. Einrichtung nach Anspruch 2, dadurch gekennzeichnet, daß der Kolben (22) mit einer durchgehenden und die Zylinder dichtend durchsetzenden Kolbenstange (23) starr verbunden ist und daß die Kolbenstange (23) oder der Zylinder ortsfest festgelegt ist.4. Device according to claim 2, characterized in that the piston (22) with a continuous and the cylinder sealingly penetrating piston rod (23) is rigidly connected and that the piston rod (23) or the cylinder is fixed in place. 5. Einrichtung nach einem der Ansprüche 1 bis 4, dadurch gekenn¬ zeichnet, daß die Arbeitsräume der Zylinderkolbenaggregate (7) über Überdruckventile (21) mit einem Druckspeicher (20) verbun¬ den sind. 5. Device according to one of claims 1 to 4, characterized gekenn¬ characterized in that the working spaces of the cylinder piston units (7) via pressure relief valves (21) with a pressure accumulator (20) are the verbun. 6. Einrichtung nach Anspruch 5, dadurch gekennzeichnet, daß die Überdruckventile (21) als aufsteuerbare Rückschlagventile ausge¬ bildet sind.6. Device according to claim 5, characterized in that the pressure relief valves (21) are formed as controllable check valves. 7. Einrichtung nach einem der Ansprüche 1 bis 6, dadurch gekenn¬ zeichnet, daß an die Pumpenarbeitsräume (13) je ein druckge¬ steuertes Wegeventil (19) angeschlossen ist, welches bei Unter¬ schreiten eines vorgegebenen Druckes in Schließstellung gelangt.7. Device according to one of claims 1 to 6, characterized gekenn¬ characterized in that each Druckge¬ controlled directional valve (19) is connected to the pump work spaces (13), which comes in the closed position when falling below a predetermined pressure. 8. Einreichtung nach Anspruch 2 und 4, dadurch gekennzeichnet, daß in einer die beiden Arbeitsräume (13) eines Zylinderkolben¬ aggregates (7) verbindenden Leitung Aufstoßventile (25) angeord¬ net sind. 8. Device according to claim 2 and 4, characterized in that in one of the two working spaces (13) of a Zylinderkolben¬ aggregate (7) connecting line push-open valves (25) are angeord¬ net.
EP95921646A 1994-06-24 1995-06-21 Device for changing points Expired - Lifetime EP0715580B1 (en)

Priority Applications (1)

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AT14094 1994-06-24
AT758/95 1995-05-03
AT75895 1995-05-03
PCT/AT1995/000125 WO1996000160A1 (en) 1994-06-24 1995-06-21 Device for changing points

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AT (1) ATE172416T1 (en)
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AT403462B (en) * 1995-05-03 1998-02-25 Vae Ag DEVICE FOR MOVING SWITCHES
GB9524541D0 (en) * 1995-11-30 1996-01-31 Westinghouse Brake & Signal Point drive unit
AT403463B (en) * 1995-12-14 1998-02-25 Vae Ag DEVICE FOR SECURING THE END POSITIONS OF SWITCH AND CROSS-CONTROL ACTUATORS
DE19631174A1 (en) * 1996-08-05 1998-02-12 Butzbacher Weichenbau Gmbh Actuator
IT1298019B1 (en) * 1997-10-22 1999-12-20 Sasib Railway Spa CASE OF OPERATION FOR RAILWAY, RAILWAY, OR SIMILAR EXCHANGES.
AT407369B (en) * 1998-04-07 2001-02-26 Vae Ag DEVICE FOR ADJUSTING THE MOVABLE PARTS OF RAILS OR CROSSINGS
US6164602A (en) * 1999-02-17 2000-12-26 Abc Rail Products Corporation Railroad frog assembly with multi-position holdback
WO2000073119A1 (en) * 1999-06-01 2000-12-07 Horváth, József Driving gear for points
AT5706U1 (en) 2001-05-07 2002-10-25 Vae Eisenbahnsysteme Gmbh METHOD FOR INSTALLING SOURCES IN TRACKS AND SOFTWARE FOR IMPLEMENTING THIS METHOD
AT5757U1 (en) * 2001-07-31 2002-11-25 Vae Eisenbahnsysteme Gmbh DEVICE FOR MOVING SWITCHES
ITMI20061647A1 (en) * 2006-08-28 2008-02-29 Gen Electric HYDRAULIC ENGINE FOR RAILWAY EXCHANGES
ATE532690T1 (en) * 2008-11-27 2011-11-15 Alstom Transport Sa DEVICE FOR MOVING POINTS, PARTICULARLY HIGH-SPEED POINTS, AND METHOD FOR MOVING POINTS
EP2418135B1 (en) * 2010-07-22 2013-04-17 ALSTOM Transport SA Method and oil-hydraulic control unit for supplying oil-hydraulic actuators in switch machines of railway points
CN102582663B (en) * 2011-11-16 2015-03-18 北京国铁路阳技术有限公司 Synchronous transmission mechanism for electric hydraulic switch machine
CN102582662B (en) * 2011-11-16 2015-06-24 天津辉煌路阳科技有限公司 Hydraulic assembly of electro-hydraulic switch machine
CN102602427B (en) * 2011-11-16 2015-06-24 天津辉煌路阳科技有限公司 Electro-hydraulic point switch
JP6243258B2 (en) * 2014-02-28 2017-12-06 株式会社京三製作所 Adhesive checker and ID setting device
CN115162072A (en) * 2022-07-21 2022-10-11 中铁六局集团有限公司 Device for transversely moving turnout junction by adopting hydraulic synchronous control equipment and construction method

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR586627A (en) * 1924-09-26 1925-03-31 Signaux Entr Electriques Device for maneuvering railway points with control of the position of these points
US2367716A (en) * 1943-04-17 1945-01-23 Union Switch & Signal Co Apparatus for controlling railway switches
DE1005112B (en) * 1955-01-25 1957-03-28 Fritz Gruender Maschinenfabrik Point control system, especially for mine railways
DE1105450B (en) * 1956-07-26 1961-04-27 Hans Joachim Von Hippel Dr Ing Electrohydraulic adjustment device, in particular point setting device
DE2051882C2 (en) * 1970-10-22 1975-03-06 Elektro-Thermit Gmbh, 1000 Berlin Tongue switch with two pairs of tongues from track sections of the main and branch track
DE2144564A1 (en) * 1971-09-06 1973-03-15 Siemens Ag TURNOUT SYSTEM FOR RAILWAY SYSTEMS WITH SLIM SWITCHES
FR2196619A5 (en) * 1972-08-17 1974-03-15 Sncf
FR2280537A2 (en) * 1974-08-02 1976-02-27 Sncf Electrically controlled hydraulic point operation - when mechanically constrained device to actuate contacts in fluid control circuit
IN147860B (en) * 1977-02-03 1980-07-26 Westinghouse Brake & Signal
DE2817782C3 (en) * 1978-04-22 1981-02-19 Elektro-Thermit Gmbh, 1000 Berlin Tongue soft
IT1242226B (en) * 1990-10-10 1994-03-03 Sasib Spa MANEUVERING DEVICE FOR RAILWAY SWITCHES, IN PARTICULAR FOR HIGH SPEED LINES

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9600160A1 *

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DE59503982D1 (en) 1998-11-26
CN1058670C (en) 2000-11-22
CA2170128C (en) 1999-05-11
HU220656B1 (en) 2002-03-28
EP0715580B1 (en) 1998-10-21
CZ282833B6 (en) 1997-10-15
WO1996000160A1 (en) 1996-01-04
FI113160B (en) 2004-03-15
EE9600027A (en) 1996-06-17
DK0715580T3 (en) 1999-06-28
RU2128746C1 (en) 1999-04-10
BG100384A (en) 1996-10-31
CA2170128A1 (en) 1996-01-04
RO117012B1 (en) 2001-09-28
BG62563B1 (en) 2000-02-29
NO960729L (en) 1996-02-23
FI960830A0 (en) 1996-02-23
ATE172416T1 (en) 1998-11-15
CZ52696A3 (en) 1996-06-12
US5687935A (en) 1997-11-18
HUT74373A (en) 1996-12-30
SK14996A3 (en) 1996-06-05
HU9600280D0 (en) 1996-04-29
NO960729D0 (en) 1996-02-23
PL177783B1 (en) 2000-01-31
CN1130892A (en) 1996-09-11
PL312937A1 (en) 1996-05-27
ES2122623T3 (en) 1998-12-16
FI960830L (en) 1996-02-23

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