EP0779197A1 - Device for securing end positions of position driver for points and crossings - Google Patents
Device for securing end positions of position driver for points and crossings Download PDFInfo
- Publication number
- EP0779197A1 EP0779197A1 EP96890186A EP96890186A EP0779197A1 EP 0779197 A1 EP0779197 A1 EP 0779197A1 EP 96890186 A EP96890186 A EP 96890186A EP 96890186 A EP96890186 A EP 96890186A EP 0779197 A1 EP0779197 A1 EP 0779197A1
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- EP
- European Patent Office
- Prior art keywords
- piston
- sleeve
- locking members
- cylinder
- end position
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- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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- 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
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- 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
- B61L5/10—Locking mechanisms for points; Means for indicating the setting of points
Definitions
- the invention relates to a device for securing the end positions in hydraulic actuators for switch parts or crossing parts, in which at least one piston which can be acted upon by fluid interacts with a valve in its end position.
- Devices of the type mentioned can be operated either with a pressure accumulator or a hydraulic pump.
- a mechanical drive can be provided, the adjustment movement being recorded by a hydraulic cylinder piston unit and the volume displaced depending on the adjustment direction being fed to this first device, which acts as a hydraulic pump, to further hydraulic actuators, so that a corresponding synchronous displacement of switch parts, in particular long switch tongues, over a large one Length of the same, can be made.
- the adjustment path of such hydraulic drives can be limited by stops, a pusher valve preferably being actuated when such a stop is reached. Pressure and temperature fluctuations that extend over a longer period of time can be substantially compensated for with such valves.
- the invention now aims to provide a device of the type mentioned at the outset, with which the respectively selected end position is maintained even with strong mechanical vibrations and with permanently acting forces until a definite positive hydraulic pressure is applied again.
- the invention essentially consists in that radially displaceable locking members are arranged coaxially to the piston, which cooperate resiliently in the securing position with a contact shoulder of the piston in the axial direction.
- locking members which are radially displaceable coaxially to the piston and which cooperate resiliently in the securing position with a stop shoulder of the piston in the axial direction ensures a resilient locking of the pistons in the respective end position.
- pressure has to be applied again, this pressure first having to disengage the locking members, overcoming the force of the spring, whereupon the desired displacement path is released again.
- the spring force must be such that it can be surmounted at the usual operating pressure for the changeover movement.
- the spring force must be dimensioned sufficiently strong to hold the pistons securely in their respective end positions even in the event of strong vibrations.
- the construction according to the invention is such that the locking members are guided in radial openings in a sleeve, the sleeve being coaxially displaceable against the force of a spring.
- Locking members formed by balls can preferably be mounted in such a sleeve, the locking members and, in the case of balls, the diameter of the balls, being greater in the radial direction than the radial extent of the sleeve.
- the locking members can be moved from a first position, in which the locking members or balls elastically cooperate with an abutment shoulder of the piston, into a second position, in which the Balls or the locking members are displaced outwards in the radial direction, so that the stroke of the piston is no longer loaded by spring forces.
- the construction can be made in a particularly simple manner in such a way that the sleeve is resiliently supported on the piston and that the piston and the cylinder have at least one circumferential groove for immersion the locking members each have an end position.
- the design can advantageously be made such that the sleeve guiding the locking members is made in two parts, an inner sleeve being slidably mounted coaxially with an outer sleeve is and the openings for the locking members are looped over in a displacement position.
- the pistons can emerge from the sleeve without the locking members falling out of the radial openings in the sleeve.
- the inner sleeve holds the locking members, in particular formed by balls, in their position in which, after the plunger has been immersed, they can in turn be resiliently pressed against an abutment shoulder of the piston.
- the design is such that the inner sleeve is resiliently supported on the cylinder or the bottom of the cylinder, the piston advantageously having a stop shoulder for the inner sleeve of the two-part sleeve, thereby ensuring a particularly reliable design in which the Balls are held securely in place.
- FIG. 1 shows the basic arrangement of actuators connected in series for switch and crossing parts
- FIG. 2 shows a longitudinal section through a hydraulic actuator with end position securing
- FIG. 3 shows a longitudinal section through a hydraulic actuator with end position securing
- FIG. 4 shows a longitudinal section through a hydraulic actuator with end position securing
- FIG. 3 shows a safe end position
- FIG. 4 shows a transition position
- FIG. 5 shows a further development of the hydraulic actuator with end position securing in a safe end position (Fig. 3), in a transition position (Fig. 4), and in an adjustment position (Fig. 5).
- hydraulic actuators 1 are connected to one another via hydraulic lines 2.
- the hydraulic actuators are designed as cylinder piston units and have a piston 3, which is axially slidably mounted in two cylinders 4.
- the channel 6, in which two poppet valves 7 are introduced acting in opposite directions, connects the two working spaces 5 as a bore so that when an end position is reached, the shut-off valve, which is closed in accordance with the direction of movement, is opened and piston 3 assumes the end position.
- a stop shoulder 8 of the piston 3 interacts with a device for securing the end position 9, it being ensured that the piston 3 remains in the end position against the force of a spring 10.
- Fig. 2 shows the end position situation while retaining the reference numerals and shows the device for securing the end position in more detail.
- the hydraulic actuator 1 is formed while maintaining the reference numerals according to Fig. 1 from pistons 3 slidably mounted in a cylinder 4, the tightness of the working spaces is ensured by sealing rings 11.
- the piston 3 is hereby held in the respective end position by the securing device of the end position 9 on one side of the cylinder-piston unit.
- a radially displaceable locking member 13 for example in the form of a ball, which is carried by the cylinder piston 3 in a piston circumferential groove 12 during the displacement process, plunges into a cylinder circumferential groove 14 made in the cylinder, with a region of the locking member 13 touching the Front side 15 of the circumferential groove 14 and at the same time the area of the locking member 13 lying radially further inside abuts the abutment shoulder 16 of the driving sleeve 17 connected to the piston.
- the sleeve 17 for guiding the locking members 13 has openings 18 in which the locking members 13 are axially supported and is also axially displaceable against the force of the spring 10 axially supported in the circumferential groove 12.
- the sleeve 17 In order to bring the piston 3 out of the end position securing device, the sleeve 17 is to be displaced counter to the spring force in such a way that the shut-off member 13 dips into the piston circumferential groove 12.
- the operational readiness for any adjustment is given when the locking members 13 are completely immersed in the circumferential groove 12, so that the piston 3 is freely movable along the cylinder 4.
- the position of the radially displaceable locking members 13 during the displacement process corresponds to the situation on the side of the cylinder-piston unit in FIG. 2 opposite the securing device which is in the secured state.
- Fig. 3 shows a modified version of Fig. 2 of an actuator, now the construction is carried out so that the relocatable locking members 13, through which the end position is secured, do not need to be carried on the piston during the adjustment process.
- Fig. 3 shows the secured end position, in which a piston end part 19 is attached to the end of the piston.
- the entire piston is in turn axially displaceably mounted in a cylinder 4, the working spaces 3 being in turn sealed by seals 11.
- the two working spaces 5 of the hydraulic actuator are connected to one another by the bore 6 which coaxially penetrates the piston 3.
- the poppet valve 7 is also arranged.
- This is designed here as a check valve with a shut-off element, for example in the form of a ball 20.
- a shut-off element for example in the form of a ball 20.
- the ball 20 is lifted from the valve seat against the force of a valve spring 23 by a projection, for example in the form of a bolt 22, attached to the bottom 21 of the cylinder 4, as a result of which the fluid of the hydraulic actuator system through the bore 6 via an annular gap between Shut-off device 20 and valve seat flow into the working space 5 and through the openings 24 into the hydraulic lines 2 according to FIG. 1 can.
- the end position thus defined is ensured by the device for securing the end position 9 against the force of a spring 10 acting coaxially to the piston, so that any impacts or other external influences cannot cause the switch to be displaced from the switch position.
- a spherical, radially displaceable locking member 13 is in turn guided in a coaxially displaceably mounted driving sleeve 17 with openings 18.
- the driver sleeve 17 is guided on a stepped outer guide sleeve 25 which can be used from the front side in the cylinder 4 when the cylinder base 21 is removed, which has the advantage over the embodiment according to FIG. 2 that the radially displaceable locking members 13 do not have to be moved .
- the guide sleeve 25 On the face side, the guide sleeve 25 has an area of the smallest radius 26, which is adjoined by an area of larger radius 27, on which the driving sleeve 17 is axially displaceably mounted. In the securing position, as shown in Fig.
- the locking member 13 is displaced radially inward through the central region of the guide sleeve 25 so that part of the outer surface of the locking member 13 displaced radially inward abuts against the stop shoulder 8 of the piston end piece 19 and an offset of the piston can only take place when the force of the spring 10 is overcome.
- 4 shows the positions of the individual elements of the device for securing the end position during the transition from the end position into an axial displacement position of the piston 3.
- the locking member 13 guided in the driving sleeve 17 is carried along by the stop shoulder 8 until it plunges into an area adjoining the area 27 of the guide sleeve 25 with the largest clear cross-section 29 such that the stop shoulder 8, the driving sleeve 17 and that can move over displaceable locking member 13 carried by her and thus the piston is released from the secured position.
- an auxiliary spring 30 is supported on the bottom 21 of the cylinder and acts against the cover sleeve 31, the other end of which cooperates with the stop of the end piece 19.
- the piston 3 is axially displaced by a correspondingly applied pressure so that the end piece of the piston 19 is brought out of the area of interaction with the device for securing the end position 9.
- the maximum travel and the spring force of the auxiliary spring 30 and the length of the cover sleeve 31 are adjusted so that the outer wall of the cover sleeve 31, the falling out of the locking member 13 from the Breakthrough 18 prevented.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Actuator (AREA)
- Vehicle Body Suspensions (AREA)
- Fittings On The Vehicle Exterior For Carrying Loads, And Devices For Holding Or Mounting Articles (AREA)
- Fluid-Pressure Circuits (AREA)
- Lock And Its Accessories (AREA)
- Control Of Position Or Direction (AREA)
- Body Structure For Vehicles (AREA)
Abstract
Description
Die Erfindung bezieht sich auf eine Einrichtung zum Sichern der Endlagen bei hydraulischen Stellantrieben für Weichen- oder Kreuzungsteile, bei welchen wenigstens ein mit Fluid beaufschlagbarer Kolben in seiner Endlage mit einem Ventil zusammenwirkt.The invention relates to a device for securing the end positions in hydraulic actuators for switch parts or crossing parts, in which at least one piston which can be acted upon by fluid interacts with a valve in its end position.
Einrichtungen der eingangs genannten Art können entweder mit einem Druckspeicher oder einer Hydraulikpumpe betrieben werden. Alternativ kann ein mechanischer Antrieb vorgesehen sein, wobei die Verstellbewegung von einem hydraulischen Zylinderkolbenaggregat aufgenommen wird und das jeweils je nach Verstellrichtung verdrängte Volumen dieser als Hydraulikpumpe wirkenden ersten Einrichtung weiteren hydraulischen Stellantrieben zugeführt wird, sodaß eine entsprechende Synchronverschiebung von Weichenteilen, insbesondere langen Weichenzungen über eine große Länge derselben, vorgenommen werden kann. Zum Ausgleich unterschiedlicher Volumina des hydraulischen Fluids oder Volumsänderungen aufgrund unterschiedlicher Temperaturen kann der Verstellweg derartiger hydraulischer Antriebe durch Anschläge begrenzt sein, wobei mit Vorzug bei Erreichen eines derartigen Anschlages ein Aufstoßventil betätigt wird. Druck- und Temperaturschwankungen, welche sich über einen längeren Zeitraum erstrecken, können mit derartigen Ventilen im wesentlichen ausgeglichen werden. Da bei geöffnetem Aufstoßventil keine zusätzlichen Verstellkräfte wirksam werden, können aber Erschütterungen, wie sie beim rollenden Verkehr unvermeidlich sind, sowie permanent wirkende Kräfte aus der Weiche die Einhaltung der definierten Endlagen in Frage stellen, sodaß ein unerwünschtes Öffnen und Schließen der Aufstoßventile durch mechanische Erschütterungen und in der Folge durch neuerliche Druckbeaufschlagung erfolgt.Devices of the type mentioned can be operated either with a pressure accumulator or a hydraulic pump. Alternatively, a mechanical drive can be provided, the adjustment movement being recorded by a hydraulic cylinder piston unit and the volume displaced depending on the adjustment direction being fed to this first device, which acts as a hydraulic pump, to further hydraulic actuators, so that a corresponding synchronous displacement of switch parts, in particular long switch tongues, over a large one Length of the same, can be made. In order to compensate for different volumes of the hydraulic fluid or changes in volume due to different temperatures, the adjustment path of such hydraulic drives can be limited by stops, a pusher valve preferably being actuated when such a stop is reached. Pressure and temperature fluctuations that extend over a longer period of time can be substantially compensated for with such valves. Since no additional adjustment forces are effective when the poppet valve is open, vibrations such as are unavoidable in rolling traffic, as well as permanent forces from the switch, can jeopardize compliance with the defined end positions, so that undesired opening and closing of the poppet valves by mechanical vibrations and subsequently done by pressurization again.
Die Erfindung zielt nun darauf ab, eine Einrichtung der eingangs genannten Art zu schaffen, mit welcher auch bei starken mechanischen Erschütterungen sowie bei permanent wirkenden Kräften die jeweils gewählte Endlage bis zum neuerlichen Aufbringen eines definitiven positiven hydraulischen Druckes eingehalten wird.The invention now aims to provide a device of the type mentioned at the outset, with which the respectively selected end position is maintained even with strong mechanical vibrations and with permanently acting forces until a definite positive hydraulic pressure is applied again.
Zur Lösung dieser Aufgabe besteht die Erfindung im wesentlichen darin, daß koaxial zum Kolben radial verlagerbare Sperrglieder angeordnet sind, welche in der Sicherungslage federnd mit einer Anlageschulter des Kolbens in axialer Richtung zusammenwirken. Dadurch, daß koaxial zum Kolben radial verlagerbare Sperrglieder angeordnet sind, welche in der Sicherungslage federnd mit einer Anschlagschulter des Kolbens in axialer Richtung zusammenwirken, wird eine federnde Verrastung der Kolben in der jeweiligen Endlage gewährleistet. Zum Umsteuern muß neuerlich Druck aufgewendet werden, wobei dieser Druck zunächst unter Überwindung der Kraft der Feder die Sperrglieder wiederum außer Eingriff bringen muß, worauf der gewünschte Verschiebeweg wiederum freigegeben ist. Die Federkraft muß hierbei so bemessen sein, daß sie bei üblichem Betriebsdruck für die Umstellbewegung mit Sicherheit überwunden werden kann. Andererseits muß die Federkraft hinreichend stark bemessen sein, um auch bei starken Erschütterungen die Kolben in ihrer jeweils eingenommenen Endlage sicher zu halten.To achieve this object, the invention essentially consists in that radially displaceable locking members are arranged coaxially to the piston, which cooperate resiliently in the securing position with a contact shoulder of the piston in the axial direction. The fact that locking members which are radially displaceable coaxially to the piston and which cooperate resiliently in the securing position with a stop shoulder of the piston in the axial direction ensures a resilient locking of the pistons in the respective end position. For reversing, pressure has to be applied again, this pressure first having to disengage the locking members, overcoming the force of the spring, whereupon the desired displacement path is released again. The spring force must be such that it can be surmounted at the usual operating pressure for the changeover movement. On the other hand, the spring force must be dimensioned sufficiently strong to hold the pistons securely in their respective end positions even in the event of strong vibrations.
In besonders einfacher Weise ist die erfindungsgemäße Konstruktion hierbei so getroffen, daß die Sperrglieder in radialen Durchbrechungen einer Hülse geführt sind, wobei die Hülse entgegen der Kraft einer Feder koaxial verschieblich ist. In einer derartigen Hülse können bevorzugt von Kugeln gebildete Sperrglieder gelagert sein, wobei die Sperrglieder, und im Falle von Kugeln der Durchmesser der Kugeln, in radialer Richtung größer sein soll als die radiale Erstreckung der Hülse. Auf diese Weise wird sichergestellt, daß durch eine Verschiebung der Hülse entgegen der Kraft der Feder die Sperrglieder aus einer ersten Position, in welcher die Sperrglieder bzw. Kugeln elastisch mit einer Anlageschulter des Kolbens zusammenwirken, in eine zweite Position verschoben werden können, in welcher die Kugeln bzw. die Sperrglieder in radialer Richtung nach auswärts verlagert werden, sodaß der Hub des Kolbens in keiner Weise mehr durch Federkräfte belastet ist.In a particularly simple manner, the construction according to the invention is such that the locking members are guided in radial openings in a sleeve, the sleeve being coaxially displaceable against the force of a spring. Locking members formed by balls can preferably be mounted in such a sleeve, the locking members and, in the case of balls, the diameter of the balls, being greater in the radial direction than the radial extent of the sleeve. In this way it is ensured that by moving the sleeve against the force of the spring, the locking members can be moved from a first position, in which the locking members or balls elastically cooperate with an abutment shoulder of the piston, into a second position, in which the Balls or the locking members are displaced outwards in the radial direction, so that the stroke of the piston is no longer loaded by spring forces.
Um den jeweiligen Raum für das Ausweichen der Verriegelungsglieder in die Verriegelungslage oder in die Außereingriffslage sicherzustellen, kann in besonders einfacher Weise die Konstruktion so getroffen sein, daß die Hülse federnd am Kolben abgestützt ist und daß der Kolben und der Zylinder wenigstens eine Umfangsnut für das Eintauchen der Sperrglieder in jeweils einer Endlage aufweisen.In order to ensure the respective space for the locking members to escape into the locking position or into the disengaged position, the construction can be made in a particularly simple manner in such a way that the sleeve is resiliently supported on the piston and that the piston and the cylinder have at least one circumferential groove for immersion the locking members each have an end position.
Insbesondere dann, wenn ein großer Verstellhub eines Zylinderkolbenaggregates freigegeben werden soll und andererseits nur kleinbauende Hülsen zum Einsatz gelangen sollen, kann die Ausbildung mit Vorteil so getroffen werden, daß die die Sperrglieder führende Hülse zweiteilig ausgebildet ist, wobei eine Innenhülse koaxial zu einer Außenhülse verschieblich gelagert ist und in einer Verschiebelage die Durchbrechungen für die Sperrglieder überschleift. Bei einer derartigen Ausbildung können die Kolben aus der Hülse austauchen, ohne daß die Sperrglieder aus den radialen Durchbrechungen der Hülse herausfallen können. Die Innenhülse hält die insbesondere von Kugeln gebildeten Sperrglieder in ihrer Position, in welcher sie in der Folge nach dem Eintauchen des Kolbens wiederum gegen eine Anlageschulter des Kolbens federnd gepreßt werden können. Mit Vorteil ist die Ausbildung hierbei so getroffen, daß die Innenhülse federnd am Zylinder bzw. dem Boden des Zylinders abgestützt ist, wobei mit Vorteil der Kolben eine Anschlagschulter für die Innenhülse der zweiteiligen Hülse aufweist, wodurch eine besonders betriebssichere Ausbildung gewährleistet wird, bei welcher die Kugeln sicher in ihrer Position gehalten werden.In particular, if a large adjustment stroke of a cylinder-piston unit is to be released and, on the other hand, only small sleeves are to be used, the design can advantageously be made such that the sleeve guiding the locking members is made in two parts, an inner sleeve being slidably mounted coaxially with an outer sleeve is and the openings for the locking members are looped over in a displacement position. With such a design, the pistons can emerge from the sleeve without the locking members falling out of the radial openings in the sleeve. The inner sleeve holds the locking members, in particular formed by balls, in their position in which, after the plunger has been immersed, they can in turn be resiliently pressed against an abutment shoulder of the piston. Advantageously, the design is such that the inner sleeve is resiliently supported on the cylinder or the bottom of the cylinder, the piston advantageously having a stop shoulder for the inner sleeve of the two-part sleeve, thereby ensuring a particularly reliable design in which the Balls are held securely in place.
Die Erfindung wird nachfolgend anhand von in der Zeichnung schematisch dargestellten Ausführungsbeispielen näher erläutert. In dieser zeigen Fig. 1 die prinzipielle Anordnung hintereinander geschalteter Stellantriebe für Weichen- und Kreuzungsteile, Fig. 2 einen Längsschnitt durch einen hydraulischen Stellantrieb mit Endlagensicherung und Fig. 3, Fig. 4, Fig. 5 Querschnitte durch eine Weiterbildung des hydraulischen Stellantriebes mit Endlagensicherung in einer sicheren Endlage (Fig. 3), in einer Übergangslage (Fig. 4), und in einer Verstellage (Fig. 5).The invention is explained in more detail below on the basis of exemplary embodiments schematically illustrated in the drawing. 1 shows the basic arrangement of actuators connected in series for switch and crossing parts, FIG. 2 shows a longitudinal section through a hydraulic actuator with end position securing and FIG. 3, FIG. 4, FIG. 5 cross sections through a further development of the hydraulic actuator with end position securing in a safe end position (Fig. 3), in a transition position (Fig. 4), and in an adjustment position (Fig. 5).
In Fig. 1 sind hydraulische Stellantriebe 1 über hydraulische Leitungen 2 hintereinander miteinander verbunden. Die hydraulischen Stellantriebe sind als Zylinderkolbenaggregate ausgebildet und weisen einen Kolben 3 auf, welcher in zwei Zylindern 4 axial gleitend gelagert ist. Bei Druckbeaufschlagung der Arbeitsräume 5 durch über die Leitung 2 zugeführte Flüssigkeit wird der Kolben 3 axial verschoben. Der Kanal 6, in welchem zwei Aufstoßventile 7 entgegengesetzt wirkend eingebracht sind, verbindet die beiden Arbeitsräume 5 als Bohrung miteinander so, daß bei Erreichen einer Endlage, das jeweils der Bewegungsrichtung entsprechend geschlossene Sperrventil geöffnet wird und Kolben 3 die Endlage einnimmt. Eine Anschlagschulter 8 des Kolbens 3 wirkt in dieser Lage mit einer Einrichtung zum Sichern der Endlage 9 zusammen, wobei sichergestellt wird, daß der Kolben 3 entgegen der Kraft einer Feder 10 in der Endlage verbleibt.In Fig. 1, hydraulic actuators 1 are connected to one another via hydraulic lines 2. The hydraulic actuators are designed as cylinder piston units and have a
Fig. 2 zeigt unter Beibehaltung der Bezugszeichen die Endlagensituation und stellt die Einrichtung zum Sichern der Endlage detaillierter dar. Der hydraulische Stellantrieb 1 wird unter Beibehaltung der Bezugszeichen entsprechend Fig. 1 aus in einem Zylinder 4 gleitend gelagerten Kolben 3 gebildet, wobei die Dichtigkeit der Arbeitsräume durch Dichtringe 11 gewährleistet ist. Der Kolben 3 wird hiebei in der jeweiligen Endlage durch die Sicherungseinrichtung der Endlage 9 auf einer Seite des Zylinderkolbenaggregates gehalten. In dieser Lage taucht ein vom Zylinderkolben 3 während des Verschiebevorganges in einer Kolben-Umfangsnut 12 mitgeführtes, radial verlagerbares Sperrglied 13, z.B. in Form einer Kugel, in eine in den Zylinder eingebrachte Zylinder-Umfangsnut 14 ein, wobei ein Bereich des Sperrgliedes 13 an die Stirnseite 15 der Umfangsnut 14 und gleichzeitig der radial weiter innengelegene Bereich des Sperrgliedes 13 an die Anlageschulter 16 der mit dem Kolben in Verbindung stehenden Mitnehmerhülse 17 anschlägt. Die Hülse 17 zur Führung der Sperrglieder 13 weist hierbei Durchbrüche 18 auf, in welchen die Sperrglieder 13 axial gelagert sind und ist entgegen der Kraft der axial in der Umfangsnut 12 gelagerten Feder 10 ebenfalls axial verschiebbar gelagert. Um den Kolben 3 aus der Endlagensicherung zu bringen, ist die Hülse 17 entgegen der Federkraft so zu verschieben, daß das Absperrglied 13 in die Kolbenumfangsnut 12 eintaucht. Die Betriebsbereitschaft für einen etwaigen Verstellvorgang ist gegeben, wenn die Sperrglieder 13 zur Gänze in die Umfangsnut 12 eintauchen, so daß der Kolben 3 längs des Zylinders 4 freilaufend verschiebbar ist. Die Lage der radial verlagerbaren Sperrglieder 13 während des Verschiebevorganges entspricht hierbei den Verhältnissen auf der den sich im gesicherten Zustand befindlichen Sicherungseinrichtung gegenüberliegenden Seite des Zylinderkolbenaggregates in Fig. 2.Fig. 2 shows the end position situation while retaining the reference numerals and shows the device for securing the end position in more detail. The hydraulic actuator 1 is formed while maintaining the reference numerals according to Fig. 1 from
Fig. 3 stellt eine zu Fig. 2 abgewandelte Ausführung eines Stellantriebes dar, wobei nunmehr die Konstruktion so ausgeführt ist, daß die verlagerbaren Sperrglieder 13, durch welche die Endlagensicherung bewerkstelligt wird, nicht am Kolben gelagert während des Verstellvorganges eigens mitgeführt werden müssen. Fig. 3 zeigt dabei die gesicherte Endlagenstellung, bei der am Ende des Kolbens ein Kolbenendteil 19 angebracht ist. Der gesamte Kolben ist wiederum in einen Zylinder 4 axial verschieblich gelagert, wobei die Arbeitsräume 3 durch Dichtungen 11 wiederum abgedichtet sind. Die beiden Arbeitsräume 5 des hydraulischen Stellantriebes sind durch die den Kolben 3 koaxial durchsetzende Bohrung 6 miteinander verbunden. Am Ende des auf die Kolbenstange gesetzten Endstückes 19 ist ebenfalls das Aufstoßventil 7 angeordnet. Dieses ist hier als Rückschlagventil mit einem Absperrorgan, z.B. in Form einer Kugel 20 ausgeführt. Bei Erreichen der Endlage wird die Kugel 20 durch einen am Boden 21 des Zylinders 4 angebrachten Vorsprung, z.B. in Form eines Bolzens 22, vom Ventilsitz entgegen der Kraft einer Ventilfeder 23 abgehoben, wodurch das Fluid des hydraulischen Stellantriebsystems durch die Bohrung 6 über einen Ringspalt zwischen Absperrorgan 20 und Ventilsitz in den Arbeitsraum 5 und durch die Öffnungen 24 in die Hydraulikleitungen 2 gemäß Fig. 1 abfließen kann. Die somit definierte Endlage wird durch die Einrichtung zum Sichern der Endlage 9 entgegen der Kraft einer koaxial zum Kolben wirkenden Feder 10 gewährleistet, sodaß etwaige Schläge oder sonstige äußere Einflüsse keinen Versatz der Weiche aus der Weichenstellung verursachen können. Ein kugelförmiges radial verlagerbares Sperrglied 13 ist hiebei wiederum in einer koaxial verschlieblich gelagerten Mitnehmerhülse 17 mit Durchbrüchen 18 geführt. Die Mitnehmerhülse 17 ist auf einer abgestuften äußeren Führungshülse 25 geführt, welche bei abgenommenen Zylinderboden 21 in den Zylinder 4 von der Stirnseite her einsetzbar ist, was gegenüber der Ausführungsform gemäß Fig. 2 den Vorteil ergibt, daß die radial verlagerbaren Sperrglieder 13 nicht mitbewegt werden müssen. Stirnseitig weist die Führungshülse 25 einen Bereich geringsten Radius 26 auf, an welchem sich ein Bereich größeren Radius 27 anschließt, auf dem die Mitnehmerhülse 17 axial verschiebbar gelagert ist. In der Sicherungslage, wie in Fig. 3 dargestellt, ist das Sperrglied 13 durch den mittleren Bereich der Führungshülse 25 so radial nach innen verlagert, daß ein Teil der Außenfläche des radial einwärts verlagerten Sperrgliedes 13 gegen die Anschlagschulter 8 des Kolbenendstückes 19 anschlägt und ein Versatz des Kolbens nur bei Überwindung der Kraft der Feder 10 erfolgen kann. Aus Fig. 4 sind die Lagen der einzelnen Elemente der Einrichtung zum Sichern der Endlage beim Übergang aus der Endlage in eine axiale Verschiebelage des Kolbens 3 ersichtlich. Durch Beaufschlagung der Druckkammer 5 mit Druck durch über die Öffnung 24 einströmenden Fluid wird der Kolben 3 bei Überwindung der Kraft der Feder 10 in Richtung des Pfeiles 28 bewegt, wobei gleichzeitig das Rückschlagventil 7 geschlossen wird. Bei diesem Vorgang wird das in der Mitnehmerhülse 17 geführte Sperrorgan 13 durch die Anschlagschulter 8 soweit mitgeführt, bis es in einen sich an den Bereich 27 der Führungshülse 25 anschließenden Bereich mit größtem lichten Querschnitt 29 derart eintaucht, daß die Anschlagschulter 8 die Mitnehmerhülse 17 und das von ihr mitgenommene verlagerbare Sperrglied 13 überstreichen kann und somit der Kolben aus der Sicherungslage freikommt. Um die Lösung aus der gesicherten Endlage durch Überwindung der Kraft der Feder 10 zu unterstützen, ist eine Hilfsfeder 30 am Boden 21 des Zylinders abgestützt und wirkt gegen die Deckhülse 31, deren anderes Ende mit dem Anschlag des Endstückes 19 zusammenwirkt. In Fig. 5 ist durch entsprechend aufgebrachten Druck der Kolben 3 soweit axial verlagert, daß das Endstück des Kolbens 19 aus dem Bereich des Zusammenwirkens mit der Einrichtung zum Sichern der Endlage 9 gebracht ist. Um zu verhindern, daß das Sperrglied 13 aus der Durchbrechung 18 der Mitnehmerhülse 17 gleitet, sind der maximale Federweg und die Federkraft der Hilfsfeder 30 und die Länge der Deckhülse 31 so abgestimmt, daß die Außenwand der Deckhülse 31, das Herausfallen des Sperrgliedes 13 aus der Durchbrechung 18 verhindert.Fig. 3 shows a modified version of Fig. 2 of an actuator, now the construction is carried out so that the
Claims (8)
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| AT2026/95 | 1995-12-14 | ||
| AT202695 | 1995-12-14 | ||
| AT0202695A AT403463B (en) | 1995-12-14 | 1995-12-14 | DEVICE FOR SECURING THE END POSITIONS OF SWITCH AND CROSS-CONTROL ACTUATORS |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP0779197A1 true EP0779197A1 (en) | 1997-06-18 |
| EP0779197B1 EP0779197B1 (en) | 2002-03-20 |
Family
ID=3526208
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP96890186A Expired - Lifetime EP0779197B1 (en) | 1995-12-14 | 1996-12-05 | Device for securing end positions of position driver for points and crossings |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP0779197B1 (en) |
| AT (2) | AT403463B (en) |
| DE (1) | DE59608916D1 (en) |
| PT (1) | PT779197E (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1999030951A1 (en) * | 1997-12-17 | 1999-06-24 | Vae Aktiengesellschaft | Device for supporting the displacement and elastically locking switching parts |
| WO2003011671A1 (en) * | 2001-07-31 | 2003-02-13 | Vae Eisenbahnsysteme Gmbh | Device for resetting points |
| WO2005042330A1 (en) * | 2003-10-31 | 2005-05-12 | Vae Eisenbahnsysteme Gmbh | Device for locking mobile point elements, especially point closing elements |
| WO2011127874A3 (en) * | 2010-04-14 | 2012-05-18 | DT- VÝHYBKÁRNA A STROJĺRNA, A.S. | Active member of the hydraulic locking device equipped with mechanic locking and retention |
| US8684318B2 (en) | 2010-09-16 | 2014-04-01 | Spx International Limited | Mechanical lock |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1224547C (en) | 2001-01-11 | 2005-10-26 | Vae火车系统有限责任公司 | Device for switching and locking moving points components |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CH520009A (en) * | 1970-06-16 | 1972-03-15 | Int Standard Electric Corp | Electrohydraulic drive for switching between drive-on and non-drive-on switches in railway systems |
| DE2049873A1 (en) * | 1970-10-10 | 1972-04-13 | Goldschmidt Ag Th | Self-locking adjusting device |
| EP0603156A1 (en) * | 1992-12-17 | 1994-06-22 | VAE Aktiengesellschaft | Locking device for moveable railway-switch parts |
| WO1996000160A1 (en) * | 1994-06-24 | 1996-01-04 | Vae Aktiengesellschaft | Device for changing points |
| WO1996034786A1 (en) * | 1995-05-03 | 1996-11-07 | Vae Aktiengesellschaft | Points control device |
-
1995
- 1995-12-14 AT AT0202695A patent/AT403463B/en not_active IP Right Cessation
-
1996
- 1996-12-05 PT PT96890186T patent/PT779197E/en unknown
- 1996-12-05 DE DE59608916T patent/DE59608916D1/en not_active Expired - Lifetime
- 1996-12-05 EP EP96890186A patent/EP0779197B1/en not_active Expired - Lifetime
- 1996-12-05 AT AT96890186T patent/ATE214672T1/en not_active IP Right Cessation
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CH520009A (en) * | 1970-06-16 | 1972-03-15 | Int Standard Electric Corp | Electrohydraulic drive for switching between drive-on and non-drive-on switches in railway systems |
| DE2049873A1 (en) * | 1970-10-10 | 1972-04-13 | Goldschmidt Ag Th | Self-locking adjusting device |
| EP0603156A1 (en) * | 1992-12-17 | 1994-06-22 | VAE Aktiengesellschaft | Locking device for moveable railway-switch parts |
| WO1996000160A1 (en) * | 1994-06-24 | 1996-01-04 | Vae Aktiengesellschaft | Device for changing points |
| WO1996034786A1 (en) * | 1995-05-03 | 1996-11-07 | Vae Aktiengesellschaft | Points control device |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1999030951A1 (en) * | 1997-12-17 | 1999-06-24 | Vae Aktiengesellschaft | Device for supporting the displacement and elastically locking switching parts |
| WO2003011671A1 (en) * | 2001-07-31 | 2003-02-13 | Vae Eisenbahnsysteme Gmbh | Device for resetting points |
| US7178764B2 (en) | 2001-07-31 | 2007-02-20 | Vae Eisenbahnsysteme Gmbh | Device for operating rail switches |
| AU2002322136B2 (en) * | 2001-07-31 | 2008-06-05 | Vae Eisenbahnsysteme Gmbh | Device for operating rail switches |
| WO2005042330A1 (en) * | 2003-10-31 | 2005-05-12 | Vae Eisenbahnsysteme Gmbh | Device for locking mobile point elements, especially point closing elements |
| WO2011127874A3 (en) * | 2010-04-14 | 2012-05-18 | DT- VÝHYBKÁRNA A STROJĺRNA, A.S. | Active member of the hydraulic locking device equipped with mechanic locking and retention |
| US8684318B2 (en) | 2010-09-16 | 2014-04-01 | Spx International Limited | Mechanical lock |
Also Published As
| Publication number | Publication date |
|---|---|
| PT779197E (en) | 2002-07-31 |
| ATA202695A (en) | 1997-07-15 |
| AT403463B (en) | 1998-02-25 |
| EP0779197B1 (en) | 2002-03-20 |
| DE59608916D1 (en) | 2002-04-25 |
| ATE214672T1 (en) | 2002-04-15 |
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