EP3892515B1 - Hydropneumatic suspension for a vehicle - Google Patents

Hydropneumatic suspension for a vehicle Download PDF

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Publication number
EP3892515B1
EP3892515B1 EP21167034.4A EP21167034A EP3892515B1 EP 3892515 B1 EP3892515 B1 EP 3892515B1 EP 21167034 A EP21167034 A EP 21167034A EP 3892515 B1 EP3892515 B1 EP 3892515B1
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EP
European Patent Office
Prior art keywords
vehicle
suspension
hydraulic cylinder
spring
cylinder arrangement
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EP21167034.4A
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German (de)
French (fr)
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EP3892515A1 (en
Inventor
Richard Schneider
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Liebherr Transportation Systems GmbH and Co KG
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Liebherr Transportation Systems GmbH and Co KG
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B61—RAILWAYS
    • B61F—RAIL VEHICLE SUSPENSIONS, e.g. UNDERFRAMES, BOGIES OR ARRANGEMENTS OF WHEEL AXLES; RAIL VEHICLES FOR USE ON TRACKS OF DIFFERENT WIDTH; PREVENTING DERAILING OF RAIL VEHICLES; WHEEL GUARDS, OBSTRUCTION REMOVERS OR THE LIKE FOR RAIL VEHICLES
    • B61F5/00—Constructional details of bogies; Connections between bogies and vehicle underframes; Arrangements or devices for adjusting or allowing self-adjustment of wheel axles or bogies when rounding curves
    • B61F5/02—Arrangements permitting limited transverse relative movements between vehicle underframe or bolster and bogie; Connections between underframes and bogies
    • B61F5/04—Bolster supports or mountings
    • B61F5/10—Bolster supports or mountings incorporating fluid springs
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B61—RAILWAYS
    • B61F—RAIL VEHICLE SUSPENSIONS, e.g. UNDERFRAMES, BOGIES OR ARRANGEMENTS OF WHEEL AXLES; RAIL VEHICLES FOR USE ON TRACKS OF DIFFERENT WIDTH; PREVENTING DERAILING OF RAIL VEHICLES; WHEEL GUARDS, OBSTRUCTION REMOVERS OR THE LIKE FOR RAIL VEHICLES
    • B61F5/00—Constructional details of bogies; Connections between bogies and vehicle underframes; Arrangements or devices for adjusting or allowing self-adjustment of wheel axles or bogies when rounding curves
    • B61F5/02—Arrangements permitting limited transverse relative movements between vehicle underframe or bolster and bogie; Connections between underframes and bogies
    • B61F5/22—Guiding of the vehicle underframes with respect to the bogies
    • B61F5/24—Means for damping or minimising the canting, skewing, pitching, or plunging movements of the underframes
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B61—RAILWAYS
    • B61F—RAIL VEHICLE SUSPENSIONS, e.g. UNDERFRAMES, BOGIES OR ARRANGEMENTS OF WHEEL AXLES; RAIL VEHICLES FOR USE ON TRACKS OF DIFFERENT WIDTH; PREVENTING DERAILING OF RAIL VEHICLES; WHEEL GUARDS, OBSTRUCTION REMOVERS OR THE LIKE FOR RAIL VEHICLES
    • B61F5/00—Constructional details of bogies; Connections between bogies and vehicle underframes; Arrangements or devices for adjusting or allowing self-adjustment of wheel axles or bogies when rounding curves
    • B61F5/02—Arrangements permitting limited transverse relative movements between vehicle underframe or bolster and bogie; Connections between underframes and bogies
    • B61F5/22—Guiding of the vehicle underframes with respect to the bogies

Definitions

  • the present invention relates to a hydropneumatic suspension for a vehicle, in particular a rail vehicle, and a (rail) vehicle provided with this suspension.
  • a conventional non-hydropneumatic shock absorber device is from U.S. 2,91 7,321 known. What is special about this shock absorber device is that it has a device for locking the shock absorber in order to simplify changing a vehicle tire without the shock absorber being transferred to its maximum extended position when the vehicle is raised.
  • a device is also known from the prior art which provides hydropneumatic suspensions in series with roller supports ( WO 2013/189999 A1 ).
  • the advantage that can be derived from this state of the art is that practically any transverse characteristics can be generated by selecting the form of the roller support, both linear and progressive or also degressive.
  • rollers required there are attached to the hydraulic cylinder via roller bearings, which requires complex and difficult implementation and also increases the risk of the bearings jamming when they are dirty.
  • hydropneumatic suspension shows its strengths particularly when an integrated solution is provided together with the chassis concept of a vehicle, since all the advantages and positive properties of the hydropneumatic suspension lead to an additional reduction in the complexity of the chassis and the Art known disadvantages are overcome.
  • the present invention describes a hydropneumatic spring system which replaces both air springs of a chassis by means of a spring strut.
  • the emergency suspension and a longitudinal carrier are also integrated, the transverse rigidity of which can be designed in practically any linear manner and is suitable for all vehicle types, including vehicles with tilting technology.
  • the invention thus paves the way for the development of "airless" trains that no longer require a compressed air supply and therefore have smaller, lighter and cheaper running gear.
  • the invention is a hydropneumatic suspension suitable for use on/in a vehicle, in particular a rail vehicle, according to claim 1.
  • the distal end areas of the first and of the second spring segment are arched towards the hydraulic cylinder arrangement.
  • the hydropneumatic suspension is placed with its arched end areas on correspondingly arched supports of the components to be sprung. If the elements that are to be sprung against one another are now offset transversely to the longitudinal direction of the hydraulic arrangement, the curved shape ensures a certain freedom of movement without significantly impairing the vertical damping properties.
  • the arc shape is a circular arc shape, which is preferably a longitudinal axis of the Hydraulic cylinder assembly towards its low point or high point.
  • the arcuate shape is in the cross-sectional plane of the suspension to allow lateral displacement of the suspension.
  • the hydraulic cylinder as well as the cylinder piston are each rigidly connected to a fastening plate on which the respective spring segment is arranged, with each fastening plate in a cross section having an arc shape, e.g. a circular arc shape, falling inwards towards the longitudinal axis of the hydraulic cylinder arrangement , so that it has a minimum distance point near or at the longitudinal axis of the hydraulic assembly.
  • an arc shape e.g. a circular arc shape
  • the spring segments are layered spring segments, for example rubber layered springs, which have several layers arranged next to one another, so that several layers are provided perpendicular to the longitudinal axis of the hydraulic arrangement in order to achieve high vertical compressive rigidity.
  • the multiple layered spring segments are arranged next to one another in a transverse direction on the fastening plate.
  • the individual layered spring segments arranged next to one another adjoin one another.
  • a pressure accumulator can be provided, e.g. in the form of a bladder, a diaphragm or a spring accumulator, which is connected to the space of the hydraulic cylinder arrangement that can be compressed by the cylinder piston via a connecting line, with the connecting line preferably having a large line cross-section , so that there is no or only a minimal dampening effect.
  • the space that can be compressed by the hydraulic cylinder and cylinder piston is connected to a pressure accumulator which, depending on the pressure introduced into this space, influences the vertical damping characteristics of the suspension.
  • the line cross-section of the line leading to the accumulator is dimensioned sufficiently large to make the resulting damping effect negligibly small.
  • an orifice plate or a valve can be arranged in the connecting line in order to passively or actively influence the vertical damping characteristics.
  • the suspension also includes an inner cylinder piston in the hydraulic cylinder, which can be controlled via a separate fluid line and is designed to vary the size of the space of the hydraulic cylinder arrangement that can be compressed by the cylinder piston, with preferably the Inner cylinder piston is arranged between the hydraulic cylinder base and the plugged into the hydraulic cylinder end of the cylinder piston and the separate fluid line runs through the hydraulic cylinder base.
  • the cylinder piston protruding from the hydraulic cylinder can be moved out in a simple manner without having to give up the damping characteristics.
  • the inner cylinder piston which is typically arranged near the bottom of the hydraulic cylinder, can be moved away from the bottom of the hydraulic cylinder via a separate fluid line, which leads to the cylinder piston being pushed out due to the constant pressure level that prevails for the compressible piston chamber of the cylinder piston. In this way, the height level of the components that are to be spring-loaded against one another with the suspension can be changed.
  • the suspension is also provided with a hydraulic power unit to provide hydraulic fluid under a certain pressure to the hydraulic cylinder arrangement, the hydraulic power unit preferably being arranged on the hydraulic cylinder arrangement.
  • This hydraulic power unit can be used in particular to vary the position of the inner cylinder, ie it can be used to regulate the level of the damping generated by the suspension.
  • the present invention also relates to a vehicle, in particular a rail vehicle, which comprises a car body and a chassis unit, the car body being supported on the chassis unit via a spring system.
  • vehicle is characterized in that the suspension system has a hydropneumatic suspension according to one of the preceding claims, which contacts the overhead car body with one of the two spring segments and the chassis unit arranged underneath with the other spring segment.
  • the arc shape occurs in a cross-sectional view of the vehicle.
  • the spring segment facing the car body i.e. the upper spring segment
  • the spring segment facing the chassis unit i.e. the lower spring segment
  • the spring segment facing the chassis unit i.e. the lower spring segment
  • the suspension is arranged at a height of the vehicle, so that the lower spring segment, ie the spring segment assigned to the chassis unit, comes to rest in the pitch center of the chassis.
  • the upper spring segment ie the spring segment assigned to the car body
  • the upper spring segment is supported directly on the car body, a crossbeam or on a yoke, which serves to integrate an emergency spring.
  • At least two, ideally four cone springs above the upper spring segment in series Spring system between a cooperating with the spring system yoke and a traverse or the car body are provided to implement an emergency suspension, wherein preferably the at least two cone springs are offset in the longitudinal or transverse direction of the vehicle to each other.
  • conical springs are provided as emergency springs on an outer edge between a traverse and the car body and/or an elastic traverse in series with the hydropneumatic suspension serves as emergency springs.
  • the spring segment arranged at the top is in contact with a yoke, to which the hydropneumatic suspension has a certain amount of play in the longitudinal direction of the vehicle, and the upper component of the suspension, the so-called bell, has at least one longitudinal buffer, in particular in the form of a rubber spring with an internal stop, between the yoke connected to the car body and the bell, in order to produce a progressive longitudinal damping characteristic, the yoke preferably enclosing the bell in the longitudinal direction of the vehicle in a hood-like manner.
  • chassis unit can have stops for limiting a longitudinal movement of the hydraulic cylinder and the bell in order to transmit high impact forces in the longitudinal direction of the vehicle.
  • the hydraulic power unit can be arranged separately in the chassis unit or in the car body.
  • An advantage of an arrangement in the car body is that the hydraulic power unit can then supply energy to each of the chassis units connected to the car body.
  • the vehicle can be provided with a generator that generates electrical energy from pressure changes in the hydraulic cylinder arrangement, this energy preferably being used to supply the hydraulic power unit.
  • a generator that generates electrical energy from pressure changes in the hydraulic cylinder arrangement, this energy preferably being used to supply the hydraulic power unit.
  • the suspension 1 shows a sectional view of the hydropneumatic suspension 1 in a transversely deflected state, so that the longitudinal direction of the suspension 1 rises out of the plane of the drawing.
  • the suspension 1 comprises a hydraulic cylinder arrangement 2 with a hydraulic cylinder 3 and a cylinder piston 4 that can be moved back and forth therein Fig.1 not shown) connected, so that when a vertical force is applied, which leads to a pushing in of the hydraulic cylinder 4, the desired damping characteristics come into play.
  • Both the hydraulic cylinder 3 and the cylinder piston 4 have a fastening plate 7 on their respective distal section, on which a spring segment 5, 6 is arranged.
  • the fastening plate 7 has an arched shape that rises outwards from a longitudinal center axis of the hydraulic cylinder arrangement 2 .
  • an associated spring segment 5, 6 is arranged on the fastening plates 7 on the side facing away from the hydraulic cylinder arrangement 2, which has a plurality of layers 8 offset in the transverse direction with respect to one another.
  • the layers arranged next to one another in the transverse direction ensure mobility in the event of a transverse offset, but at the same time ensure rigidity in the vertical direction.
  • the suspension 1 is transversely deflected by the length A.
  • the not transversely deflected suspension 1 is still partially in the 1 sketched to get a better idea of the undeflected suspension.
  • the arcuate end of the respective spring segment 5, 6 facing away from the hydraulic cylinder arrangement 2 interacts with a correspondingly shaped spring segment counterpart 32, which, viewed in cross section, has a bulbous shape extending towards the suspension and is connected to the respective distal area of a spring segment 5, 6 .
  • the spring segment counterpart 32 is rigid and has no elastic properties, but has the primary task of creating a connection between an element to be sprung and the suspension.
  • FIG. 2 shows a cross-sectional view of a rail vehicle 15, which has the hydropneumatic suspension 1 according to the invention.
  • a chassis 17 can be seen, which is sprung with the suspension 1 in relation to a car body 16 .
  • the spring strut 1 is arranged in the middle of the chassis 17 .
  • the actual hydraulic cylinder arrangement 2 is arranged between two layer spring segments 5, 6.
  • the upper and the lower segment 5, 6 are each designed arcuate, the outer surface of the segments 5, 6 protruding from the hydraulic cylinder arrangement 2 being concave to the hydraulic cylinder arrangement 2.
  • Any desired transverse rigidity can be generated by appropriate selection of the radii and the shear rigidity of the segments 5, 6.
  • the vertical rigidity is determined by the diameter of the piston 4 and the volume of the spring accumulator 9.
  • the other functions for springing the car body 16 remain largely the same as a classic chassis 17 known from the prior art.
  • roll stabilizers 27 progressive transverse suspension 26 in the form of a rubber buffer or a transverse spring roller, a transverse damper 25 and a vertical damper 24.
  • the transverse damper 25 can typically be used as a semi-active damper, as an active transverse suspension, as an actuator for a hold-off device (system for limiting lateral displacement while driving a curve in order to prevent it from hitting a stop, which is perceived as uncomfortable) or as a tilting actuator to be executed.
  • the vertical dampers 24 are advantageously coupled or designed to be semi-active. To reduce or eliminate the negative influence of piston friction, the two vertical dampers are coupled or semi-active controlled so that they only dampen rolling movements, since the vertical damping is already provided by the friction. In addition, the vertical rigidity of the suspension 1 can be reduced in order to additionally reduce the influence of friction.
  • the damping of the vertical movements can be additionally adjusted. Active control of the damping valve can also be implemented.
  • a suspension 1 arranged in between, which together with other stabilization mechanisms, such as roll stabilizers 27, transverse dampers 25, vertical dampers 24, etc., creates an entire spring system for the vehicle 15.
  • the wheel set 31 rolling on the track 33 is connected to the chassis unit 17 via a wheel set guide 30 and a primary damping 29 and primary suspension 28, which only dampens or cushions the wheel 31 rolling on the track 33.
  • the suspension 1 according to the invention is provided for vertical damping of the running gear unit 17 and the car body 16 arranged above it.
  • the upper spring segment 5 is in direct contact with the car body 16 or a cross member 18 of the Car body 16 and the lower spring segment 6 in direct contact with the chassis unit 17.
  • the respective spring segment 5, 6 and the car body 16 or the chassis unit 17 without the losing significant advantages of the invention.
  • a so-called emergency suspension is required, which allows safe operation of the vehicle even if the hydropneumatic suspension 1 fails.
  • This emergency suspension can be installed in series or in parallel with the suspension 1 according to the invention.
  • Variant "a” does not have an emergency spring, but only shows the suspension 1 in direct connection with a cross member 18 for attachment to the car body 16.
  • Variant "b” shows the possible implementation of an emergency spring, in that a conical spring 20 is integrated into the cylinder piston 4. If the hydropneumatic suspension 1 fails, for example because it has a leak, the cylinder piston 4 sinks onto the hydraulic cylinder base 14 , but still has a vertical damping property, since a conical spring 20 is integrated into the piston 4 .
  • the conical spring 20 is arranged between the side of the fastening plate 7 facing towards the hydraulic cylinder 3 and a section of the piston that dips into the cylinder 3 .
  • two cone springs 20 are offset in the transverse direction by a width center.
  • the interaction with the upper spring segment 5 of the suspension 1 takes place via a so-called yoke 19, which creates a connection to the traverse 18 via the two conical springs 20.
  • This cone springs are arranged at the two end portions in the transverse direction of the yoke 19 and ensure that the cone springs 20 are arranged in series with the hydropneumatic suspension 1. If the hydropneumatic suspension 1 now fails, the two cone springs 20 provide emergency suspension.
  • the yoke 19 with its two conical springs 20 can also be arranged rotated by 90°, so that the two conical springs 20 are not spaced apart in the transverse direction but in the longitudinal direction of the vehicle 15 .
  • Variant “d” shows the implementation of an emergency spring, in that two conical springs 20 are mounted in the traverse 18, the conical springs 20 being integrated directly into a fastening with the car body 16.
  • an elastic traverse 18' is used, which can assume the function of an emergency spring should the hydropneumatic suspension 1 fail.
  • the hydraulic cylinder 3 is inserted directly into a cone spring, which assumes the emergency spring function.
  • the conical spring 20 is further connected to the lower layered spring segment 6 via a so-called bell 21 .
  • suspension elements of the emergency suspension are implemented in the above variants "b" to "f” as cone springs 20, which are preferably rubber cone springs.
  • cone springs 20 which are preferably rubber cone springs.
  • other shapes such as pure rubber layer springs, etc. are also conceivable.
  • the so-called longitudinal entrainment is usually arranged in the central area of the chassis 17 .
  • This usually consists of a pivot, sliding elements or a so-called lemniscate.
  • the longitudinal forces are transmitted via this construction, so that they can be transmitted independently of the unscrewing movement and the transverse path.
  • a longitudinal entrainment that is independent of the suspension 1 according to the invention leads to an expensive and complex mechanical construction. It is therefore advantageous to integrate the longitudinal entrainment into the suspension 1. 4 therefore shows a sectional view in the longitudinal direction through a complete suspension 1 with emergency suspension and longitudinal entrainment.
  • the lower layered spring segment 6 is designed as a single spring and is arranged in the pitch center of the chassis 17 .
  • the two upper spring segments 5 are offset in the longitudinal direction of the vehicle 15, so that the hydraulic cylinder arrangement 2, which can also be referred to as a strut, is stabilized in the vertical direction.
  • a so-called yoke 19 with integrated emergency springs in the form of two conical springs 20 spaced apart in the longitudinal direction of the vehicle is arranged between the traverse 18 and the upper layer spring segments 5 .
  • the inner cone pin is mounted directly on the traverse 18 and the part of the cone spring 20 in the shape of a cone segment surrounding this pin is fastened to the yoke 19 .
  • Two longitudinal buffers 22 and four longitudinal stops 23 are additionally provided for the actual longitudinal entrainment.
  • FIG 5 a sectional view of the hydraulic arrangement 2 is shown, in which the functionality of a level control is realized via an inner cylinder 12 .
  • this can also be done by a mechanical level control valve.
  • the distance from the running gear 17 to the car body 16 can be measured and the pressure prevailing in the spring accumulator can be varied as a function of this, so that the piston 4 moves in or out of the cylinder 3 .
  • a distance measurement between the running gear 17 and the car body 16 can be integrated in the vertical dampers 24, although it is also possible to provide a separate distance measurement in the area of the vertical dampers, which is preferably carried out in the middle of the vehicle 15.
  • the distance measurement is also possible for the distance measurement to be integrated in the hydraulic cylinder arrangement 2 .
  • a height or distance measurement from the car body 16 to the platform is carried out and the spring is raised or lowered accordingly via an electric valve.
  • the distance between the chassis unit 17 and the car body 16 must be adjustable.
  • a second piston 12 the so-called inner piston 12, can be installed in the hydraulic system 2, which can be controlled via a separate oil supply and control/regulation.
  • the inner cylinder piston 12 is arranged between the hydraulic cylinder base 14 and the cylinder piston 4 protruding from the cylinder 3 .
  • Via a separate fluid line 13 it is possible to move the inner cylinder piston 12 inside the hydraulic cylinder 3 so that it can reduce the piston space 10 available for the cylinder piston 4 .
  • the pressure in the pressure accumulator 9 and the piston chamber 10 will rise and cause the cylinder piston 4 to be lifted out of the hydraulic cylinder 3 .
  • the fluid supply can also be adjusted automatically via the separate fluid line 13 as a function of a measured distance from the car body 16 to a platform or the chassis unit 17 .
  • the appropriate amount of fluid is simply introduced or discharged via the separate fluid line 13 so that the desired height of the car body 16 is reached.
  • a hydraulic power unit can be provided to generate the hydraulic pressure, which can be used, for example, to regulate the level and to compensate for leaks.
  • This can either be arranged in a compact form directly on the hydraulic cylinder arrangement 2 or separately in the chassis unit 17 .
  • An arrangement on the car body 16 in order to connect the typically two running gear units 17 connected to the car body 16 and thus those arranged there Supplying consumers with hydraulic fluid is also conceivable.
  • the electrical and/or electronic control is also integrated in such a hydraulic power unit.
  • the system can also be equipped with a self-sufficient energy supply.
  • the ongoing pressure changes in the hydraulic cylinder assembly 2 can be used as an energy source.
  • This energy is used by a small generator to charge a battery, which ensures the power supply for the electronics, sensors, valves and pump.
  • the principle of the generator is preferably based on the use of pressure changes in the hydraulic cylinder arrangement 2, which are converted into electrical energy via small movements via corresponding generators.

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  • Mechanical Engineering (AREA)
  • Vehicle Body Suspensions (AREA)

Description

Die vorliegende Erfindung betrifft eine hydropneumatische Federung für ein Fahrzeug, insbesondere ein Schienenfahrzeug, sowie ein mit dieser Federung versehenes (Schienen-)Fahrzeug.The present invention relates to a hydropneumatic suspension for a vehicle, in particular a rail vehicle, and a (rail) vehicle provided with this suspension.

Praktisch alle modernen Schienenfahrzeuge sind mit Luftfedern ausgerüstet, da aus Komfortgründen eine niedrige Vertikalsteifigkeit verlangt wird, was wiederum eine Niveauregulierung nach sich zieht. Daneben ist meist noch eine pneumatische Bremse eingebaut, wohingegen Scheibenwischer und Türen heute meist schon rein elektrisch betrieben werden. Seit Jahrzehnten versuchen Fahrzeughersteller auf die aufwendige Druckluftversorgung zu verzichten, scheiterten jedoch bis heute an einer vernünftigen Lösung eines Ersatzes der Luftfederung.Practically all modern rail vehicles are equipped with air springs, since a low level of vertical rigidity is required for reasons of comfort, which in turn entails level control. In addition, a pneumatic brake is usually installed, whereas windscreen wipers and doors are usually operated purely electrically today. For decades, vehicle manufacturers have been trying to do without the costly compressed air supply, but have so far failed to come up with a reasonable solution to replace the air suspension.

Jeder Versuch der Substitution einer Luftfeder durch eine hydropneumatische Federung führte zu sehr aufwendigen und komplexen mechanischen Lösungen, weil neben der rein vertikalen Federung, ebenso die Querfederung, die Längsbewegung sowie Drehungen um alle Achsen ermöglicht werden müssen.Every attempt to replace an air spring with a hydropneumatic suspension led to very expensive and complex mechanical solutions, because in addition to the purely vertical suspension, transverse suspension, longitudinal movement and rotation around all axes must also be possible.

Der Ansatz einer reinen Substitution der Luftfeder hat sich demnach als nicht erfolgsversprechend erwiesen.The approach of simply substituting the air spring has therefore not proven to be promising.

Eine herkömmliche nicht-hydropneumatische Stoßdämpfereinrichtung ist aus der US 2,91 7,321 bekannt. Das Besondere an dieser Stoßdämpfereinrichtung ist, dass sie eine Vorrichtung zum Sperren des Stoßdämpfers aufweist, um das Wechseln eines Fahrzeugreifens zu vereinfachen, ohne dass beim Anheben des Fahrzeugs der Stoßdämpfer in seine maximal ausgefahrene Position überführt wird.A conventional non-hydropneumatic shock absorber device is from U.S. 2,91 7,321 known. What is special about this shock absorber device is that it has a device for locking the shock absorber in order to simplify changing a vehicle tire without the shock absorber being transferred to its maximum extended position when the vehicle is raised.

Aus dem Stand der Technik ist zudem eine Einrichtung bekannt, welche hydropneumatische Federungen in Serie mit Rollenabstützungen vorsieht ( WO 2013/189999 A1 ). Der aus diesem Stand der Technik ableitbare Vorteil ist, dass mittels Wahl der Form der Rollenabstützung praktisch beliebige Quercharakteristiken erzeugt werden können, sowohl linear, wie progressiv oder auch degressiv.A device is also known from the prior art which provides hydropneumatic suspensions in series with roller supports ( WO 2013/189999 A1 ). The advantage that can be derived from this state of the art is that practically any transverse characteristics can be generated by selecting the form of the roller support, both linear and progressive or also degressive.

Dennoch ist auch diese aus dem Stand der Technik bekannte Lösung nachteilhaft. Unter anderem sind die dort erforderlichen Rollen über Wälzlagerungen am Hydraulikzylinder angebracht, was eine aufwendige und schwere Umsetzung erfordert und zudem die Gefahr erhöht, dass die Lager bei Verschmutzung blockieren.Nevertheless, this solution known from the prior art is also disadvantageous. Among other things, the rollers required there are attached to the hydraulic cylinder via roller bearings, which requires complex and difficult implementation and also increases the risk of the bearings jamming when they are dirty.

Es ist demnach das Ziel der vorliegenden Erfindung eine hydropneumatische Federung für ein Fahrzeug vorzusehen, das die oben aufgeführten Nachteile teilweise oder vollständig überwindet, so dass eine verbesserte Federung für ein Fahrzeug, insbesondere ein Schienenfahrzeug erreicht wird. Dies gelingt mit einer Federung, die sämtliche Merkmale des Anspruchs 1 aufweist. Vorteilhafte Ausgestaltungen sind dabei in den abhängigen Ansprüchen angegeben.It is therefore the object of the present invention to provide a hydropneumatic suspension for a vehicle which partially or completely overcomes the disadvantages listed above, so that an improved suspension for a vehicle, in particular a rail vehicle, is achieved. This is achieved with a suspension that has all the features of claim 1. Advantageous configurations are specified in the dependent claims.

Das Vorsehen einer hydropneumatischen Federung spielt seine Stärken besonders dann aus, wenn eine integrierte Lösung zusammen mit dem Fahrwerkkonzept eines Fahrzeugs vorgesehen ist, da dann sämtliche Vorteile und positiven Eigenschaften der hydropneumatischen Federung zu einer zusätzlichen Reduktion der Komplexität des Fahrwerks führen und die aus dem Stand der Technik bekannten Nachteile überwunden werden.The provision of a hydropneumatic suspension shows its strengths particularly when an integrated solution is provided together with the chassis concept of a vehicle, since all the advantages and positive properties of the hydropneumatic suspension lead to an additional reduction in the complexity of the chassis and the Art known disadvantages are overcome.

Die vorliegende Erfindung beschreibt ein hydropneumatisches Federsystem, welches mittels eines Federbeins beide Luftfedern eines Fahrwerks ersetzt. In vorteilhaften Ausführungen wird zudem die Notfederung sowie eine Längsmitnahme integriert, deren Quersteifigkeit praktisch beliebig linear gestaltet werden kann und für alle Fahrzeugtypen geeignet ist, inkl. Neigetechnik-Fahrzeuge. Die Erfindung eröffnet damit den Weg zur Entwicklung von "Airless"-Zügen, die keine Druckluftversorgung mehr benötigen, und daher kleinere, leichtere und günstigere Fahrwerke aufweisen.The present invention describes a hydropneumatic spring system which replaces both air springs of a chassis by means of a spring strut. In advantageous versions, the emergency suspension and a longitudinal carrier are also integrated, the transverse rigidity of which can be designed in practically any linear manner and is suitable for all vehicle types, including vehicles with tilting technology. The invention thus paves the way for the development of "airless" trains that no longer require a compressed air supply and therefore have smaller, lighter and cheaper running gear.

Die Erfindung ist eine Hydropneumatische Federung geeignet für die Verwendung bei/ in einem Fahrzeug, insbesondere Schienenfahrzeug, gemäß Anspruch 1.The invention is a hydropneumatic suspension suitable for use on/in a vehicle, in particular a rail vehicle, according to claim 1.

Die distalen Endbereiche des ersten und des zweiten Federsegments sind dabei zur Hydraulikzylinderanordnung hin gewölbt. Vorteilhafterweise wird, um einen gewünschten Federeffekt zu erzielen, die hydropneumatische Federung mit ihren gewölbten Endbereichen auf korrespondierend gewölbte Auflagen der zu federnden Bestandteile aufgelegt. Erfolgt nun ein Versatz der gegeneinander zu federnden Elemente quer zur Längsrichtung der Hydraulikanordnung, sorgt die Bogenform für einen gewissen Bewegungsspielraum ohne dabei die vertikalen Dämpfeigenschaften signifikant zu verschlechtern.The distal end areas of the first and of the second spring segment are arched towards the hydraulic cylinder arrangement. Advantageously, in order to achieve a desired spring effect, the hydropneumatic suspension is placed with its arched end areas on correspondingly arched supports of the components to be sprung. If the elements that are to be sprung against one another are now offset transversely to the longitudinal direction of the hydraulic arrangement, the curved shape ensures a certain freedom of movement without significantly impairing the vertical damping properties.

Nach einer vorteilhaften Variation der Erfindung kann vorgesehen sein, dass die Bogenform eine Kreisbogenform ist, die vorzugsweise zu einer Längsachse der Hydraulikzylinderanordnung hin ihren Tiefpunkt bzw. Hochpunkt aufweist. Typischerweise verläuft die Bogenform in Querschnittsebene der Federung, um einen Querversatz der Federung zu ermöglichen.According to an advantageous variation of the invention it can be provided that the arc shape is a circular arc shape, which is preferably a longitudinal axis of the Hydraulic cylinder assembly towards its low point or high point. Typically, the arcuate shape is in the cross-sectional plane of the suspension to allow lateral displacement of the suspension.

Nach der Erfindung ist vorgesehen, dass der Hydraulikzylinder wie auch der Zylinderkolben jeweils starr mit einem Befestigungsteller verbunden sind, auf der das jeweilige Federsegment angeordnet ist, wobei jeder Befestigungsteller in einem Querschnitt eine nach innen zur Längsachse der Hydraulikzylinderanordnung abfallende Bogenform, bspw. eine Kreisbogenform aufweist, so dass diese einen Punkt mit minimalen Abstand nahe oder an der Längsachse der Hydraulikanordnung besitzt.According to the invention, it is provided that the hydraulic cylinder as well as the cylinder piston are each rigidly connected to a fastening plate on which the respective spring segment is arranged, with each fastening plate in a cross section having an arc shape, e.g. a circular arc shape, falling inwards towards the longitudinal axis of the hydraulic cylinder arrangement , so that it has a minimum distance point near or at the longitudinal axis of the hydraulic assembly.

Nach der Erfindung ist zudem vorgesehen, dass die Federsegmente Schichtfedersegmente sind, bspw. Gummischichtfedern, die mehrere nebeneinander angeordnete Schichten aufweisen, so dass mehrere Schichten senkrecht zur Längsachse der Hydraulikanordnung vorgesehen sind, um eine hohe vertikale Drucksteifigkeit zu erreichen. Die mehreren Schichtfedersegmente sind dabei in einer Querrichtung nebeneinander an dem Befestigungsteller angeordnet. Die einzelnen nebeneinander angeordneten Schichtfedersegmente grenzen dabei aneinander an.According to the invention, it is also provided that the spring segments are layered spring segments, for example rubber layered springs, which have several layers arranged next to one another, so that several layers are provided perpendicular to the longitudinal axis of the hydraulic arrangement in order to achieve high vertical compressive rigidity. The multiple layered spring segments are arranged next to one another in a transverse direction on the fastening plate. The individual layered spring segments arranged next to one another adjoin one another.

Ferner kann nach einer vorteilhaften Ausführungsform ein Druckspeicher vorgesehen sein, bspw. in Form eines Blasen-, eines Membran- oder eines Federspeichers, der mit dem durch den Zylinderkolben kompressierbaren Raum der Hydraulikzylinderanordnung über eine Verbindungsleitung verbunden ist, wobei vorzugsweise die Verbindungsleitung einen großen Leitungsquerschnitt aufweist, damit keine oder nur eine minimal dämpfende Wirkung entsteht.Furthermore, according to an advantageous embodiment, a pressure accumulator can be provided, e.g. in the form of a bladder, a diaphragm or a spring accumulator, which is connected to the space of the hydraulic cylinder arrangement that can be compressed by the cylinder piston via a connecting line, with the connecting line preferably having a large line cross-section , so that there is no or only a minimal dampening effect.

Der durch Hydraulikzylinder und Zylinderkolben kompressierbare Raum ist mit einem Druckspeicher verbunden, der in Abhängigkeit des in diesen Raum eingeführten Drucks die vertikale Dämpfungscharakteristik der Federung beeinflusst. Der Leitungsquerschnitt der zum Druckspeicher führenden Leitung ist dabei ausreichend groß dimensioniert, um eine hierdurch dämpfende Wirkung zu vernachlässigbar klein zu gestalten.The space that can be compressed by the hydraulic cylinder and cylinder piston is connected to a pressure accumulator which, depending on the pressure introduced into this space, influences the vertical damping characteristics of the suspension. The line cross-section of the line leading to the accumulator is dimensioned sufficiently large to make the resulting damping effect negligibly small.

Zudem kann eine Blende oder ein Ventil in der Verbindungsleitung angeordnet sein, um die vertikale Dämpfcharakteristik passiv oder aktiv zu beeinflussen.In addition, an orifice plate or a valve can be arranged in the connecting line in order to passively or actively influence the vertical damping characteristics.

Möchte man beispielweise ein straffere vertikale Dämpfungscharakteristik, kann man dies durch Verringern des Leitungsquerschnitts der Verbindungsleitung erreichen, da bei einer den Hydraulikzylinder stauchenden Kraft nun nur eine geringere Menge an Fluid den Kolbenraum verlassen kann.If, for example, a tighter vertical damping characteristic is desired, this can be achieved by reducing the line cross-section of the connecting line, since only a smaller amount of fluid can now leave the piston chamber when the hydraulic cylinder is compressed.

Nach einer optionalen Fortbildung der Erfindung kann vorgesehen sein, dass die Federung ferner eine Innenzylinderkolben in dem Hydraulikzylinder umfasst, der über eine separate Fluidleitung ansteuerbar ist und dazu ausgelegt ist, den durch den Zylinderkolben kompressierbaren Raum der Hydraulikzylinderanordnung in seiner Größe zu variieren, wobei vorzugsweise der Innenzylinderkolben zwischen Hydraulikzylinderboden und dem in den Hydraulikzylinder eingesteckten Ende des Zylinderkolbens angeordnet ist und die separate Fluidleitung durch den Hydraulikzylinderboden verläuft.According to an optional development of the invention, it can be provided that the suspension also includes an inner cylinder piston in the hydraulic cylinder, which can be controlled via a separate fluid line and is designed to vary the size of the space of the hydraulic cylinder arrangement that can be compressed by the cylinder piston, with preferably the Inner cylinder piston is arranged between the hydraulic cylinder base and the plugged into the hydraulic cylinder end of the cylinder piston and the separate fluid line runs through the hydraulic cylinder base.

Durch das Vorsehen des Innenzylinderkolbens kann der aus dem Hydraulikzylinder hervorstehende Zylinderkolben auf einfache Art und Weise herausgefahren werden, ohne dass dafür die Dämpfungscharakteristik aufgegeben werden muss. Der typischerweise in der Nähe des Hydraulikzylinderbodens angeordnete Innenzylinderkolben kann über eine separate Fluidleitung vom Hydraulikzylinderboden wegbewegt werden, was aufgrund des gleichbleibenden Druckniveaus, das für den kompressierbaren Kolbenraum des Zylinderkolbens vorherrscht, zu einem Ausschieben des Zylinderkolbens führt. Somit kann das Höhenniveau der mit der Federung gegeneinander zu federnden Bestandteile verändert werden.By providing the inner cylinder piston, the cylinder piston protruding from the hydraulic cylinder can be moved out in a simple manner without having to give up the damping characteristics. The inner cylinder piston, which is typically arranged near the bottom of the hydraulic cylinder, can be moved away from the bottom of the hydraulic cylinder via a separate fluid line, which leads to the cylinder piston being pushed out due to the constant pressure level that prevails for the compressible piston chamber of the cylinder piston. In this way, the height level of the components that are to be spring-loaded against one another with the suspension can be changed.

Von Vorteil ist dies insbesondere bei einem Schienenfahrzeug, wenn die Räder einer gewissen Abnutzung erfahren haben, die zu einem Absinken in der Höhe führt. Ein Höhenausgleich lässt sich dann relativ einfach durch Anheben des Innenzylinderkolbens realisieren, so dass eine gleichbleibende Höhe des auf dem Fahrwerk federnd abgestützten Wagenkastens möglich ist.This is particularly advantageous in the case of a rail vehicle when the wheels have experienced a certain amount of wear, which leads to a drop in height. A height compensation can then be implemented relatively easily by raising the inner cylinder piston, so that a constant height of the car body, which is resiliently supported on the chassis, is possible.

Nach einer optionalen Fortbildung der vorliegenden Erfindung kann vorgesehen sein, dass die Federung ferner mit einer hydraulischen Leistungseinheit versehen ist, um Hydraulikfluid unter einem gewissen Druck der Hydraulikzylinderanordnung bereitzustellen, wobei vorzugsweise die hydraulische Leistungseinheit an der Hydraulikzylinderanordnung angeordnet ist.According to an optional development of the present invention, it can be provided that the suspension is also provided with a hydraulic power unit to provide hydraulic fluid under a certain pressure to the hydraulic cylinder arrangement, the hydraulic power unit preferably being arranged on the hydraulic cylinder arrangement.

Diese hydraulische Leistungseinheit kann insbesondere zum Variieren der Stellung des Innenzylinders dienen, also für eine Niveauregulierung der durch die Federung erzeugten Dämpfung genutzt werden.This hydraulic power unit can be used in particular to vary the position of the inner cylinder, ie it can be used to regulate the level of the damping generated by the suspension.

Die vorliegende Erfindung betrifft ferner ein Fahrzeug, insbesondere ein Schienenfahrzeug, welches einen Wagenkasten, und eine Fahrwerkseinheit umfasst, wobei der Wagenkasten über ein Federungssystem auf der Fahrwerkseinheit abgestützt ist. Das Fahrzeug ist dadurch gekennzeichnet, dass das Federungssystem eine hydropneumatische Federung nach einem der vorhergehenden Ansprüche aufweist, die den oben liegenden Wagenkasten mit einem der beiden Federsegmente und die darunter angeordnete Fahrwerkseinheit mit dem anderen Federsegment kontaktiert.The present invention also relates to a vehicle, in particular a rail vehicle, which comprises a car body and a chassis unit, the car body being supported on the chassis unit via a spring system. The vehicle is characterized in that the suspension system has a hydropneumatic suspension according to one of the preceding claims, which contacts the overhead car body with one of the two spring segments and the chassis unit arranged underneath with the other spring segment.

Dabei kann vorgesehen sein, dass die hydropneumatische Federung in dem Fahrzeug so orientiert ist, dass die Schichtfedersegmente in Querrichtung des Fahrzeugs nebeneinander angeordnet sind.Provision can be made for the hydropneumatic suspension in the vehicle to be oriented in such a way that the layered spring segments are arranged next to one another in the transverse direction of the vehicle.

Ferner kann vorgesehen sein, dass die Bogenform in einer Querschnittansicht des Fahrzeugs auftritt.Furthermore, it can be provided that the arc shape occurs in a cross-sectional view of the vehicle.

Nach einer Fortbildung der Erfindung kann vorgesehen sein, dass das zum Wagenkasten gerichtete Federsegment (also das obere Federsegment) mehrere in Längsrichtung des Fahrzeugs zueinander beabstandeten Federsegmenteinheiten umfasst, und vorzugsweise das zur Fahrwerkseinheit gerichtete Federsegment (also das untere Federsegment) mehrere in Längsrichtung des Fahrzeugs zueinander beabstandeten Federsegmenteinheiten umfasst.According to a further development of the invention, it can be provided that the spring segment facing the car body (i.e. the upper spring segment) comprises a plurality of spring segment units spaced apart from one another in the longitudinal direction of the vehicle, and preferably the spring segment facing the chassis unit (i.e. the lower spring segment) comprises a plurality of one another in the longitudinal direction of the vehicle spaced spring segment units includes.

Es kann demnach nicht nur ein einzelnes oberes und/oder unteres Federsegment vorgesehen sein, sondern auch mehrere davon, die in Längsrichtung des Fahrzeugs zueinander versetzt angeordnet sind.Accordingly, not only a single upper and/or lower spring segment can be provided, but also several of them, which are offset from one another in the longitudinal direction of the vehicle.

Ferner kann nach der Erfindung vorgesehen sein, dass die Federung in einer Höhe des Fahrzeugs angeordnet ist, so dass das untere, also das der Fahrwerkseinheit zugeordnete Federsegment im Nickzentrum des Fahrwerks zum Liegen kommt.Furthermore, it can be provided according to the invention that the suspension is arranged at a height of the vehicle, so that the lower spring segment, ie the spring segment assigned to the chassis unit, comes to rest in the pitch center of the chassis.

Dies ist für die zu erzielende Stabilisierung des Fahrzeugs von Vorteil, da dann lediglich der obere Teil des Federung, der also nicht im Nickzentrum des Fahrzeugs angeordnet ist, mit entsprechenden Dämpfungsmitteln, die gegen das Nicken wirken, versehen werden muss, so dass sich ein insgesamt weniger komplexer Aufbau der Federung ergibt.This is advantageous for the stabilization of the vehicle to be achieved, since then only the upper part of the suspension, which is not located in the pitch center of the vehicle, has to be provided with appropriate damping means, which act against pitching, so that an overall less complex structure of the suspension results.

Zudem kann nach einer bevorzugten Modifikation der Erfindung vorgesehen sein, dass sich das obere, also das dem Wagenkasten zugeordnete Federsegment direkt am Wagenkasten, einer Traverse oder an einem Joch, das zur Integration einer Notfederung dient, abstützt.In addition, according to a preferred modification of the invention, it can be provided that the upper spring segment, ie the spring segment assigned to the car body, is supported directly on the car body, a crossbeam or on a yoke, which serves to integrate an emergency spring.

Ebenso kann vorgesehen sein, dass eine Konusfeder, vorzugsweise aus Gummi, zwischen dem Hydraulikzylinder und dem unteren Federsegment angeordnet ist, um eine Notfederung umzusetzen.Provision can also be made for a conical spring, preferably made of rubber, to be arranged between the hydraulic cylinder and the lower spring segment in order to implement emergency springing.

Zudem kann nach der Erfindung vorgesehen sein, dass mindestens zwei, idealerweise vier Konusfedern oberhalb des oberen Federsegments in Serie zum Federsystem zwischen einem mit dem Federsystem zusammenwirkenden Joch und einer Traverse oder dem Wagenkasten vorgesehen sind, um eine Notfederung umzusetzen, wobei vorzugsweise die mindestens zwei Konusfedern in Längs- oder Querrichtung des Fahrzeugs versetzt zueinander angeordnet sind.In addition, it can be provided according to the invention that at least two, ideally four cone springs above the upper spring segment in series Spring system between a cooperating with the spring system yoke and a traverse or the car body are provided to implement an emergency suspension, wherein preferably the at least two cone springs are offset in the longitudinal or transverse direction of the vehicle to each other.

Ferner kann nach der Erfindung vorgesehen sein, dass an einem äußeren Rand zwischen einer Traverse und dem Wagenkasten Konusfedern als Notfederung vorgesehen sind und/oder eine elastische Traverse in Serie zur hydropneumatischen Federung als Notfederung dient.Furthermore, it can be provided according to the invention that conical springs are provided as emergency springs on an outer edge between a traverse and the car body and/or an elastic traverse in series with the hydropneumatic suspension serves as emergency springs.

Nach einer Fortbildung der Erfindung kann vorgesehen sein, dass das oben angeordnete Federsegment mit einem Joch in Kontakt ist, zu dem die hydropneumatische Federung in Längsrichtung des Fahrzeug ein gewisses Spiel aufweist, und der obere Bestandteil der Federung, die sogenannte Glocke, mindestens einen Längspuffer, insbesondere in Form einer Gummifeder mit internem Anschlag, zwischen dem mit dem Wagenkasten verbundenen Joch und der Glocke besitzt, um eine progressive Längsdämpfungscharakteristik zu erzeugen, wobei vorzugsweise das Joch die Glocke in Längsrichtung des Fahrzeugs haubenartig umgreift.According to a development of the invention, it can be provided that the spring segment arranged at the top is in contact with a yoke, to which the hydropneumatic suspension has a certain amount of play in the longitudinal direction of the vehicle, and the upper component of the suspension, the so-called bell, has at least one longitudinal buffer, in particular in the form of a rubber spring with an internal stop, between the yoke connected to the car body and the bell, in order to produce a progressive longitudinal damping characteristic, the yoke preferably enclosing the bell in the longitudinal direction of the vehicle in a hood-like manner.

Ferner kann dabei die Fahrwerkseinheit Anschläge zum Begrenzen einer Längsbewegung des Hydraulikzylinders und der Glocke aufweisen, um hohe Stoßkräfte in Längsrichtung des Fahrzeugs zu übertragen.Furthermore, the chassis unit can have stops for limiting a longitudinal movement of the hydraulic cylinder and the bell in order to transmit high impact forces in the longitudinal direction of the vehicle.

Weiter kann dabei die hydraulische Leistungseinheit separat in der Fahrwerkseinheit oder in dem Wagenkasten angeordnet sein. Vorteilhaft an einer Anordnung im Wagenkasten ist, dass die hydraulische Leistungseinheit dann Energie an jeden der mit dem Wagenkasten in Verbindung stehenden Fahrwerkseinheiten liefern kann. So sind bei Schienenfahrzeugen in der Regel mindestens zwei Fahrwerkseinheiten mit dem Wagenkasten in Verbindung.Furthermore, the hydraulic power unit can be arranged separately in the chassis unit or in the car body. An advantage of an arrangement in the car body is that the hydraulic power unit can then supply energy to each of the chassis units connected to the car body. In rail vehicles, for example, there are usually at least two chassis units connected to the car body.

Zudem kann das Fahrzeug mit einem Generator versehen sein, der aus Druckänderungen der Hydraulikzylinderanordnung elektrische Energie erzeugt, wobei vorzugsweise diese Energie dazu genutzt wird, die hydraulische Leistungseinheit zu versorgen. Damit ist es beispielsweise möglich, dass die hydraulische Leistungseinheit autark zu der Energieversorgung des Fahrzeugs ist, da ihr gesamter Energiebedarf durch den Generator gedeckt ist.In addition, the vehicle can be provided with a generator that generates electrical energy from pressure changes in the hydraulic cylinder arrangement, this energy preferably being used to supply the hydraulic power unit. This makes it possible, for example, for the hydraulic power unit to be self-sufficient in relation to the vehicle's energy supply, since its entire energy requirement is covered by the generator.

Weitere Merkmale, Einzelheiten und Vorteile der Erfindung werden anhand der nachfolgenden Figurenbeschreibung ersichtlich. Dabei zeigen:

Fig. 1:
eine Schnittansicht der hydropneumatischen Federung in einem querausgelenktem Zustand,
Fig. 2:
eine Querschnittsansicht durch ein Schienenfahrzeug, das die erfindungsgemäße hydropneumatische Federung aufweist,
Fig. 3:
insgesamt sechs unterschiedliche Varianten zur Umsetzung einer Notfederung für die erfindungsgemäße hydropneumatische Federung,
Fig. 4:
eine Längsschnittansicht einer erfindungsgemäßen Variante der hydropneumatische Federung in einem Fahrzeug, und
Fig. 5:
eine Schnittansicht durch die Hydraulikzylinderanordnung, die einen zwischen Zylinderkolben und Hydraulikzylinderboden angeordneten Innenzylinder zur Niveauregulierung umfasst.
Further features, details and advantages of the invention can be seen from the following description of the figures. show:
Figure 1:
a sectional view of the hydropneumatic suspension in a transversely deflected state,
Figure 2:
a cross-sectional view through a rail vehicle having the hydropneumatic suspension according to the invention,
Figure 3:
a total of six different variants for implementing an emergency suspension for the hydropneumatic suspension according to the invention,
Figure 4:
a longitudinal sectional view of a variant of the hydropneumatic suspension according to the invention in a vehicle, and
Figure 5:
a sectional view through the hydraulic cylinder arrangement, which includes an inner cylinder arranged between the cylinder piston and the hydraulic cylinder base for level control.

Fig. 1 zeigt eine Schnittansicht der hydropneumatischen Federung 1 in einem querausgelenktem Zustand, so dass sich die Längsrichtung der Federung 1 aus der Blattebene erhebt. Die Federung 1 umfasst eine Hydraulikzylinderanordnung 2 mit einem Hydraulikzylinder 3 und einem darin hin- und herbewegbaren Zylinderkolben 4. Der Kolbenraum 10, also der durch den Zylinderkolben kompressierbare Raum im Hydraulikzylinder 3 ist mit einem Druckspeicher 9 (in Fig.1 nicht dargestellt) verbunden, so dass bei einer vertikalen Krafteinwirkung, welche zu einem Einschieben des Hydraulikzylinders 4 führt, die gewünschte Dämpfungscharakteristik zum Tragen kommt. 1 shows a sectional view of the hydropneumatic suspension 1 in a transversely deflected state, so that the longitudinal direction of the suspension 1 rises out of the plane of the drawing. The suspension 1 comprises a hydraulic cylinder arrangement 2 with a hydraulic cylinder 3 and a cylinder piston 4 that can be moved back and forth therein Fig.1 not shown) connected, so that when a vertical force is applied, which leads to a pushing in of the hydraulic cylinder 4, the desired damping characteristics come into play.

Sowohl der Hydraulikzylinder 3 wie auch der Zylinderkolben 4 weisen an ihrem jeweils distalen Abschnitt einen Befestigungsteller 7 auf, an dem ein Federsegment 5, 6 angeordnet ist.Both the hydraulic cylinder 3 and the cylinder piston 4 have a fastening plate 7 on their respective distal section, on which a spring segment 5, 6 is arranged.

Der Befestigungsteller 7 weist in der dargestellten Querschnittsansicht eine Bogenform auf, die von einer Längsmittelachse der Hydraulikzylinderanordnung 2 nach außen hin ansteigt. Dabei ist an den Befestigungstellern 7 jeweils an der von der Hydraulikzylinderanordnung 2 abgewandten Seite ein zugehöriges Federsegment 5, 6 angeordnet, das mehrere in Querrichtung zueinander versetzte Schichten 8 aufweist. Die in Querrichtung nebeneinander angeordneten Schichten sorgen für eine Bewegbarkeit bei einem Querversatz, sorgen aber gleichzeitig für eine Steifigkeit in vertikaler Richtung.In the cross-sectional view shown, the fastening plate 7 has an arched shape that rises outwards from a longitudinal center axis of the hydraulic cylinder arrangement 2 . In this case, an associated spring segment 5, 6 is arranged on the fastening plates 7 on the side facing away from the hydraulic cylinder arrangement 2, which has a plurality of layers 8 offset in the transverse direction with respect to one another. The layers arranged next to one another in the transverse direction ensure mobility in the event of a transverse offset, but at the same time ensure rigidity in the vertical direction.

In Fig. 1 ist die Federung 1 um die Länge A querausgelenkt. Die nicht querausgelenkte Federung 1 ist dabei noch teilweise in der Fig. 1 skizziert, um eine bessere Vorstellung der nicht-ausgelenkten Federung zu erhalten. Das von der Hydraulikzylinderanordnung 2 abgewandte bogenförmige Ende des jeweiligen Federsegments 5, 6 wirkt dabei mit einem korrespondierend geformten Federsegmentgegenstück 32 zusammen, das im Querschnitt gesehen eine bauchige sich hin zur Federung erstreckende Form aufweist und mit dem jeweiligen distalen Bereich eines Federsegments 5, 6 verbunden ist. Das Federsegmentgegenstück 32 ist dabei starr und besitzt keine elastischen Eigenschaften, sondern hat die primäre Aufgabe eine Verbindung zwischen einem zu federnden Element und der Federung zu schaffen.In 1 the suspension 1 is transversely deflected by the length A. The not transversely deflected suspension 1 is still partially in the 1 sketched to get a better idea of the undeflected suspension. The arcuate end of the respective spring segment 5, 6 facing away from the hydraulic cylinder arrangement 2 interacts with a correspondingly shaped spring segment counterpart 32, which, viewed in cross section, has a bulbous shape extending towards the suspension and is connected to the respective distal area of a spring segment 5, 6 . The spring segment counterpart 32 is rigid and has no elastic properties, but has the primary task of creating a connection between an element to be sprung and the suspension.

Bei der dargestellten Querauslenkung der Federung 1 erkennt man zudem die hierdurch hervorgerufene Deformation der einzelnen Schichten 8 der Federsegmente 5, 6. Gut zu erkennen ist dies bspw. in den unterem Federsegment 6, da dort die links angeordneten Schichten 8 gestreckt und die rechts angeordneten Schichten 8 gestaucht dargestellt sind. Dennoch bleibt auch bei einer Querauslenkung die prinzipielle durch die Federung erzielbare Vertikaldämpfung erhalten.In the case of the transverse deflection of the suspension 1 shown, one can also see the deformation of the individual layers 8 of the spring segments 5, 6 caused by this. This can be clearly seen, for example, in the lower spring segment 6, since the layers 8 arranged on the left are shown stretched there and the layers 8 arranged on the right are shown compressed. Nevertheless, even with a transverse deflection, the vertical damping that can be achieved in principle by the springing is retained.

Fig. 2 zeigt eine Querschnittsansicht eines Schienenfahrzeugs 15, das die erfindungsgemäße hydropneumatische Federung 1 aufweist. Man erkennt ein Fahrwerk 17, das mit der Federung 1 gegenüber einem Wagenkasten 16 gefedert ist. Das Federbein 1 ist dabei in der Mitte des Fahrwerks 17 angeordnet. Die eigentliche Hydraulikzylinderanordnung 2 ist zwischen zwei Schichtfedersegmenten 5, 6 angeordnet. Dabei kann es mehr als ein oberes Schichtfedersegment 5 geben, die dann in Längsrichtung versetzt vorgesehen sind. Das obere und das untere Segment 5, 6 sind jeweils bogenförmig ausgeführt, wobei die von der Hydraulikzylinderanordnung 2 abstehende Außenfläche der Segmente 5, 6 konkav zur Hydraulikzylinderanordnung 2 ausgebildet ist. Durch entsprechende Wahl der Radien sowie der Schubsteifigkeit der Segmente 5, 6, kann eine beliebige Quersteifigkeit erzeugt werden. Die Vertikalsteifigkeit wird durch den Durchmesser des Kolbens 4 sowie das Volumen des Federspeichers 9 bestimmt. 2 shows a cross-sectional view of a rail vehicle 15, which has the hydropneumatic suspension 1 according to the invention. A chassis 17 can be seen, which is sprung with the suspension 1 in relation to a car body 16 . The spring strut 1 is arranged in the middle of the chassis 17 . The actual hydraulic cylinder arrangement 2 is arranged between two layer spring segments 5, 6. There can be more than one upper layered spring segment 5, which is then offset in the longitudinal direction. The upper and the lower segment 5, 6 are each designed arcuate, the outer surface of the segments 5, 6 protruding from the hydraulic cylinder arrangement 2 being concave to the hydraulic cylinder arrangement 2. Any desired transverse rigidity can be generated by appropriate selection of the radii and the shear rigidity of the segments 5, 6. The vertical rigidity is determined by the diameter of the piston 4 and the volume of the spring accumulator 9.

Die weiteren Funktionen zum Federn des Wagenkastens 16 bleiben weitgehend gleich zu einem klassischen, aus dem Stand der Technik bekannten Fahrwerk 17. So gibt es Wankstabilisatoren 27, eine progressive Querfederung 26 in Form eines Gummipuffers oder einer Querfederrolle, einen Querdämpfer 25 und einen Vertikaldämpfer 24. Der Querdämpfer 25 kann typischerweise als semi-aktiver Dämpfer, als aktive Querfederung, als Aktuator für ein Hold-off-Device (System zur Begrenzung einer Seitenverschiebung während einer gefahrenen Kurve, um das als unkomfortabel empfundene Anliegen an einem Anschlag zu verhindern) oder als Neigeaktuator ausgeführt werden.The other functions for springing the car body 16 remain largely the same as a classic chassis 17 known from the prior art. There are roll stabilizers 27, progressive transverse suspension 26 in the form of a rubber buffer or a transverse spring roller, a transverse damper 25 and a vertical damper 24. The transverse damper 25 can typically be used as a semi-active damper, as an active transverse suspension, as an actuator for a hold-off device (system for limiting lateral displacement while driving a curve in order to prevent it from hitting a stop, which is perceived as uncomfortable) or as a tilting actuator to be executed.

Die Vertikaldämpfer 24 werden vorteilhafterweise gekoppelt oder semi-aktiv ausgeführt. Zur Minderung bzw. Elimination des negativen Einflusses der Reibung des Kolbens werden die beiden Vertikaldämpfer gekoppelt oder semi-aktiv angesteuert, so dass diese nur Wankbewegungen dämpfen, da die vertikale Dämpfung bereits durch die Reibung gegeben ist. Zusätzlich kann die Vertikalsteifigkeit der Federung 1 reduziert werden, um zusätzlich den Reibungseinfluss zu reduzieren. Mittels einer entsprechender Gestaltung der Kinematik des Wankstabilisators 27 (Schrägstellung der Stangen führt zu einer Erzeugung eines virtuellen Drehpunktes im Bereich des Wagenkasten-Schwerpunkts), entsprechender Wahl der Radien der oberen und unteren Schichtfedersegmente 5, 6 sowie optionalerweise Verwendung eines Aktuators anstelle des Querdämpfers 25 kann mit der erfindungsgemäßen Federung 1 eine Wankkompensation oder auch eine vollständig aktive Neigung realisiert werden.The vertical dampers 24 are advantageously coupled or designed to be semi-active. To reduce or eliminate the negative influence of piston friction, the two vertical dampers are coupled or semi-active controlled so that they only dampen rolling movements, since the vertical damping is already provided by the friction. In addition, the vertical rigidity of the suspension 1 can be reduced in order to additionally reduce the influence of friction. By means of a corresponding design of the kinematics of the roll stabilizer 27 (inclined position of the rods leads to the generation of a virtual pivot point in the area of the center of gravity of the car body), appropriate selection of the radii of the upper and lower layered spring segments 5, 6 and optionally using an actuator instead of the transverse damper 25 With the suspension 1 according to the invention, a roll compensation or a fully active inclination can be realized.

Mittels Wahl des Leitungsquerschnitts der Verbindung 11 vom Hydraulikzylinder 3 zum Federspeicher 9 und/oder einem zusätzlichem Ventil oder einer Drossel in der Verbindungsleitung 11, kann die Dämpfung der vertikalen Bewegungen zusätzlich angepasst werden. Eine aktive Regelung des Dämpfungsventils ist ebenfalls umsetzbar.By choosing the line cross-section of the connection 11 from the hydraulic cylinder 3 to the spring accumulator 9 and/or an additional valve or a throttle in the connecting line 11, the damping of the vertical movements can be additionally adjusted. Active control of the damping valve can also be implemented.

In Fig. 2 erkennt man neben der Fahrwerkseinheit 17 und dem darüber angeordnetem Wagenkasten 16 eine dazwischen angeordnete Federung 1, die zusammen mit weiteren Stabilisationsmechanismen, wie Wankstabilisatoren 27, Querdämpfer 25, Vertikaldämpfer 24, etc. ein gesamtes Federsystem für das Fahrzeug 15 erzeugt. Der auf dem Gleis 33 abrollende Radsatz 31 ist dabei über eine Radsatzführung 30 sowie einer Primärdämpfung 29 und Primärfederung 28, welche nur das auf dem Gleis 33 abrollende Rad 31 dämpft bzw. federt, an die Fahrwerkseinheit 17 angebunden.In 2 In addition to the chassis unit 17 and the car body 16 arranged above, one can see a suspension 1 arranged in between, which together with other stabilization mechanisms, such as roll stabilizers 27, transverse dampers 25, vertical dampers 24, etc., creates an entire spring system for the vehicle 15. The wheel set 31 rolling on the track 33 is connected to the chassis unit 17 via a wheel set guide 30 and a primary damping 29 and primary suspension 28, which only dampens or cushions the wheel 31 rolling on the track 33.

Für eine Vertikaldämpfung von Fahrwerkseinheit 17 und dem darüber angeordneten Wagenkasten 16 ist die erfindungsgemäße Federung 1 vorgesehen, die mit ihrem oberen Federsegment 5 zum Wagenkasten 16 und ihrem unteren Federsegment 6 zur Fahrwerkseinheit 17 gerichtet ist. In einer -wie in Fig. 2 dargestellten- einfachen Umsetzung, steht das obere Federsegment 5 dabei in direktem Kontakt mit dem Wagenkasten 16 oder einer Traverse 18 des Wagenkastens 16 und das untere Federsegment 6 in einem direktem Kontakt mit der Fahrwerkseinheit 17. Dem Fachmann ist aber klar, dass auch ein oder mehrere Elemente zwischen dem jeweiligen Federsegment 5, 6 und dem Wagenkasten 16 bzw. der Fahrwerkseinheit 17 zwischengeschoben werden können, ohne die wesentlichen Vorteile der Erfindung zu verlieren.The suspension 1 according to the invention is provided for vertical damping of the running gear unit 17 and the car body 16 arranged above it. In a -like in 2 shown- simple implementation, the upper spring segment 5 is in direct contact with the car body 16 or a cross member 18 of the Car body 16 and the lower spring segment 6 in direct contact with the chassis unit 17. However, it is clear to the person skilled in the art that one or more elements can also be inserted between the respective spring segment 5, 6 and the car body 16 or the chassis unit 17 without the losing significant advantages of the invention.

Im Falle eines Ausfalls der hydropneumatischen Federung 1 wird eine sogenannte Notfederung benötigt, welche einen sicheren Betrieb des Fahrzeugs auch bei ausgefallener hydropneumatischer Federung 1 erlaubt. Diese Notfederung kann in Serie oder auch parallel zur erfindungsgemäßen Federung 1 eingebaut werden.In the event of a failure of the hydropneumatic suspension 1, a so-called emergency suspension is required, which allows safe operation of the vehicle even if the hydropneumatic suspension 1 fails. This emergency suspension can be installed in series or in parallel with the suspension 1 according to the invention.

Fig. 3 zeigt dabei verschiedene Varianten möglicher Ausführungen von Notfedern, wobei die Varianten "c" und "f" in Kombination mit der erfindungsgemäßen Federung 1 als besonders vorteilhaft angesehen werden. 3 shows different variants of possible designs of emergency springs, variants "c" and "f" in combination with the suspension 1 according to the invention are considered to be particularly advantageous.

Die Variante "a" weist keine Notfeder auf, sondern zeigt lediglich die Federung 1 in direkter Verbindung mit einer Traverse 18 zur Befestigung am Wagenkasten 16.Variant "a" does not have an emergency spring, but only shows the suspension 1 in direct connection with a cross member 18 for attachment to the car body 16.

Variante "b" zeigt die mögliche Umsetzung einer Notfeder, indem eine Konusfeder 20 in den Zylinderkolben 4 integriert ist. Fällt die hydropneumatische Federung 1 aus, da sie bspw. ein Leck aufweist, sinkt der Zylinderkolben 4 auf den Hydraulikzylinderboden 14 ab, besitzt aber weiterhin eine vertikale Dämpfeigenschaft, da in den Kolben 4 eine Konusfeder 20 integriert ist. Die Konusfeder 20 ist dabei zwischen der zu dem Hydraulikzylinder 3 zugewandten Seite des Befestigungstellers 7 und einem in den Zylinder 3 eintauchenden Abschnitt des Kolbens angeordnet.Variant "b" shows the possible implementation of an emergency spring, in that a conical spring 20 is integrated into the cylinder piston 4. If the hydropneumatic suspension 1 fails, for example because it has a leak, the cylinder piston 4 sinks onto the hydraulic cylinder base 14 , but still has a vertical damping property, since a conical spring 20 is integrated into the piston 4 . The conical spring 20 is arranged between the side of the fastening plate 7 facing towards the hydraulic cylinder 3 and a section of the piston that dips into the cylinder 3 .

Bei Variante "c" werden zwei Konusfedern 20 um eine Breitenmitte in Querrichtung versetzt angeordnet. Das Zusammenwirken mit dem oberen Federsegment 5 der Federung 1 erfolgt dabei über ein sogenanntes Joch 19, das eine Verbindung zu der Traverse 18 über die beiden Konusfedern 20 erzeugt. Diese Konusfedern sind dabei an den beiden Endabschnitten in Querrichtung des Jochs 19 angeordnet und sorgen für eine Anordnung der Konusfedern 20 in Serie zu der hydropneumatischen Federung 1. Fällt nun die hydropneumatische Federung 1 aus, ist durch die beiden Konusfedern 20 eine Notfederung vorhanden.In variant “c”, two cone springs 20 are offset in the transverse direction by a width center. The interaction with the upper spring segment 5 of the suspension 1 takes place via a so-called yoke 19, which creates a connection to the traverse 18 via the two conical springs 20. This cone springs are arranged at the two end portions in the transverse direction of the yoke 19 and ensure that the cone springs 20 are arranged in series with the hydropneumatic suspension 1. If the hydropneumatic suspension 1 now fails, the two cone springs 20 provide emergency suspension.

Das Joch 19 mit seinen beiden Konusfedern 20 kann dabei auch um 90° rotiert angeordnet werden, so dass die beiden Konusfedern 20 nicht in Querrichtung sondern in Längsrichtung des Fahrzeugs 15 beabstandet sind.The yoke 19 with its two conical springs 20 can also be arranged rotated by 90°, so that the two conical springs 20 are not spaced apart in the transverse direction but in the longitudinal direction of the vehicle 15 .

Variante "d" zeigt die Umsetzung einer Notfeder, indem zwei Konusfedern 20 in der Traverse 18 gelagert sind, wobei die Konusfedern 20 direkt in einer Befestigung mit dem Wagenkasten 16 integriert sind.Variant "d" shows the implementation of an emergency spring, in that two conical springs 20 are mounted in the traverse 18, the conical springs 20 being integrated directly into a fastening with the car body 16.

Bei Variante "e" wird eine elastische Traverse 18' verwendet, die die Funktion einer Notfeder übernehmen kann, sollte die hydropneumatische Federung 1 ausfallen. Durch das Aufsetzen des Wagenkastens 16 auf die elastische Traverse 18' ist eine vertikale Dämpfung direkt durch die Elastizität der Traverse 18' gegeben.In variant "e" an elastic traverse 18' is used, which can assume the function of an emergency spring should the hydropneumatic suspension 1 fail. By placing the car body 16 on the elastic cross member 18 'a vertical damping is given directly by the elasticity of the cross member 18'.

Bei Variante "f" wird der Hydraulikzylinder 3 direkt in eine Konusfeder eingesetzt, welche die Notfederfunktion übernimmt. Die Konusfeder 20 ist weiter über eine sog. Glocke 21 mit dem unteren Schichtfedersegment 6 verbunden.In variant "f", the hydraulic cylinder 3 is inserted directly into a cone spring, which assumes the emergency spring function. The conical spring 20 is further connected to the lower layered spring segment 6 via a so-called bell 21 .

Die Federungselemente der Notfederung sind in den voranstehenden Varianten "b" bis "f" als Konusfedern 20, die vorzugsweise Gummi-Konusfedern sind, umgesetzt. Es sind jedoch auch andere Formen wie z.B. reine Gummischichtfedern, etc. denkbar.The suspension elements of the emergency suspension are implemented in the above variants "b" to "f" as cone springs 20, which are preferably rubber cone springs. However, other shapes such as pure rubber layer springs, etc. are also conceivable.

Fig. 4 zeigt eine an die Variante "c" der Fig. 3 angelehnte Umsetzung in einer etwas detailreicheren Darstellung, wobei hier die beiden Konusfedern 20 jedoch in Längsrichtung zueinander versetzt angeordnet sind. 4 indicates a variant "c" of the 3 based implementation in a somewhat more detailed representation, in which case the two cone springs 20 are offset from one another in the longitudinal direction.

Im zentralen Bereich des Fahrwerks 17 ist in der Regel die sog. Längsmitnahme angeordnet. Diese besteht in der Regel aus einem Drehzapfen, Gleitelementen oder einer sog. Lemniskate. Über diese Konstruktion werden die Längskräfte übertragen, so dass diese unabhängig von der Ausdrehbewegung sowie vom Querweg übertragen werden können. Eine von der erfindungsgemäßen Federung 1 unabhängige Längsmitnahme, führt zu einer aufwendigen und komplexen mechanischen Konstruktion. Deshalb ist es von Vorteil, die Längsmitnahme in die Federung 1 zu integrieren. Fig. 4 zeigt daher eine Schnittansicht in Längsrichtung durch eine vollständige Federung 1 mit Notfederung und Längsmitnahme.The so-called longitudinal entrainment is usually arranged in the central area of the chassis 17 . This usually consists of a pivot, sliding elements or a so-called lemniscate. The longitudinal forces are transmitted via this construction, so that they can be transmitted independently of the unscrewing movement and the transverse path. A longitudinal entrainment that is independent of the suspension 1 according to the invention leads to an expensive and complex mechanical construction. It is therefore advantageous to integrate the longitudinal entrainment into the suspension 1. 4 therefore shows a sectional view in the longitudinal direction through a complete suspension 1 with emergency suspension and longitudinal entrainment.

Das untere Schichtfedersegment 6 ist als einzelne Feder ausgeführt und ist im Nickzentrum des Fahrwerks 17 angeordnet. Die beiden oberen Federsegmente 5 sind in Längsrichtung des Fahrzeugs 15 versetzt angeordnet, so dass das Hydraulikzylinderanordnung 2, das auch als Federbein bezeichnet werden kann, in vertikaler Richtung stabilisiert wird. Zwischen der Traverse 18 und den oberen Schichtfedersegmenten 5 ist ein sog. Joch 19 mit integrierten Notfedern in Form von zwei in Längsrichtung des Fahrzeugs beabstandeten Konusfedern 20 angeordnet. Dabei ist der innere Konuszapfen direkt an der Traverse 18 montiert und der diesen Zapfen umgebende kegelabschnittförmige Bestandteil der Konusfeder 20 an dem Joch 19 befestigt. Für die eigentliche Längsmitnahme sind zusätzlich zwei Längspuffer 22 und vier Längsanschläge 23 vorgesehen.The lower layered spring segment 6 is designed as a single spring and is arranged in the pitch center of the chassis 17 . The two upper spring segments 5 are offset in the longitudinal direction of the vehicle 15, so that the hydraulic cylinder arrangement 2, which can also be referred to as a strut, is stabilized in the vertical direction. A so-called yoke 19 with integrated emergency springs in the form of two conical springs 20 spaced apart in the longitudinal direction of the vehicle is arranged between the traverse 18 and the upper layer spring segments 5 . The inner cone pin is mounted directly on the traverse 18 and the part of the cone spring 20 in the shape of a cone segment surrounding this pin is fastened to the yoke 19 . Two longitudinal buffers 22 and four longitudinal stops 23 are additionally provided for the actual longitudinal entrainment.

Die Charakteristik der Längsmitnahme teilt sich bei der vorliegenden Erfindung in die folgenden drei Bereiche auf:

    1. a) bei kleinen Bewegungen liegt eine niedrige Steifigkeit vor, so dass sich dadurch eine optimale Entkoppelung des Fahrwerks 17 vom Wagenkasten 16 erreichen lässt. Die Steifigkeit wird über die Schubsteifigkeiten der oberen und unteren Schichtfedersegmente 5, 6 gebildet. Ferner ist diese Charakteristik vor allem in den Zuständen ohne Antriebs- und Bremskräften wirksam.
    2. b) eine elastische, progressive Charakteristik wird vorliegend über die Längspuffer 22 definiert. Der zum Längspuffer 22 zugehörige Anschlag 23 zwischen Zylinderanordnung 2 und Fahrwerkrahmen 17 ist dabei in Kontakt. Diese Charakteristik ist vor allem in den Zuständen mit Antriebs- und Bremskräften wirksam.
    3. c) ein Anschlag mit sehr hoher Steifigkeit tritt bspw. dann auf, wenn ein Längsstoß von bis zu 5g der Fahrwerkmasse zu so hohen Kräften führt, welche nicht mehr über den Federung 1 bzw. über die Gummipuffer 22 geführt werden können. Bei so hohen Kräften kommen alle Anschläge 23 in Aktion. Die Kraft geht dann von der Traverse 18 über die Konusfedern 20, das Joch 19 in den Puffer 22 mit internem Anschlag 23, dann auf die Glocke 21 und direkt wieder über den Anschlag 23 auf den Rahmen 17.
In the case of the present invention, the characteristic of the longitudinal entrainment is divided into the following three areas:
    1. a) there is low rigidity in the case of small movements, so that an optimal decoupling of the running gear 17 from the car body 16 can be achieved as a result. The stiffness is formed by the shear stiffnesses of the upper and lower layered spring segments 5, 6. Furthermore, this characteristic is mainly effective in the states without driving and braking forces.
    2. b) an elastic, progressive characteristic is defined by the longitudinal buffers 22 in the present case. The stop 23 associated with the longitudinal buffer 22 between the cylinder arrangement 2 and the chassis frame 17 is in contact. This characteristic is particularly effective in the states with driving and braking forces.
    3. c) A stop with very high rigidity occurs, for example, when a longitudinal impact of up to 5 g of the chassis mass leads to such high forces that the suspension 1 or the rubber buffers 22 can no longer be used. With such high forces, all stops 23 come into action. The force then goes from the traverse 18 via the conical springs 20, the yoke 19 into the buffer 22 with an internal stop 23, then to the bell 21 and directly again via the stop 23 to the frame 17.

In Fig. 5 ist eine Schnittansicht der Hydraulikanordnung 2 gezeigt, bei der über einen Innenzylinder 12 die Funktionalität einer Niveauregulierung realisiert wird.In figure 5 a sectional view of the hydraulic arrangement 2 is shown, in which the functionality of a level control is realized via an inner cylinder 12 .

Neben der in Fig. 5 gezeigten Umsetzung einer Niveauregulierung kann diese auch durch ein mechanisches Niveauregulierventil erfolgen. So kann bspw. der Abstand vom Fahrwerk 17 zum Wagenkasten 16 gemessen werden und in Abhängigkeit davon der im Federspeicher vorherrschende Druck variiert, so dass es zu einem Ein- oder Ausfahren des Kolbens 4 aus dem Zylinder 3 kommt. Eine Abstandsmessung von Fahrwerk 17 und Wagenkasten 16 kann in den Vertikaldämpfern 24 integriert sein, wobei es aber auch möglich ist, eine separate Abstandsmessung im Bereich der Vertikaldämpfer vorzusehen, die vorzugsweise in der Mitte des Fahrzeugs 15 erfolgt.In addition to the figure 5 shown implementation of a level control, this can also be done by a mechanical level control valve. For example, the distance from the running gear 17 to the car body 16 can be measured and the pressure prevailing in the spring accumulator can be varied as a function of this, so that the piston 4 moves in or out of the cylinder 3 . A distance measurement between the running gear 17 and the car body 16 can be integrated in the vertical dampers 24, although it is also possible to provide a separate distance measurement in the area of the vertical dampers, which is preferably carried out in the middle of the vehicle 15.

Weiter ist möglich, dass die Abstandsmessung in der Hydraulikzylinderanordnung 2 integriert ist.It is also possible for the distance measurement to be integrated in the hydraulic cylinder arrangement 2 .

Für eine betriebliche Höhenverstellung (das sogenannte Levelling) wird eine Höhen- bzw. Abstandsmessung vom Wagenkasten 16 zum Bahnsteig (z.B. via Radar, Laser, etc.) durchgeführt und über ein elektrisches Ventil die Feder entsprechend angehoben oder abgesenkt.For an operational height adjustment (the so-called levelling), a height or distance measurement from the car body 16 to the platform (e.g. via radar, laser, etc.) is carried out and the spring is raised or lowered accordingly via an electric valve.

Zum Durchführen eines Levellings oder auch zum Ausgleich der Radabnutzung muss der Abstand von Fahrwerkseinheit 17 und Wagenkasten 16 anpassbar sein.To carry out a leveling or to compensate for wheel wear, the distance between the chassis unit 17 and the car body 16 must be adjustable.

Wie in der Schnittansicht der Fig. 5 ersichtlich, kann dazu in der Hydraulikanordnung 2 ein zweiter Kolben 12, der sogenannte Innenkolben 12 installiert sein, welcher über eine separate Ölversorgung und Steuerung/Regelung ansteuerbar ist. Der Innenzylinderkolben 12 ist dabei zwischen dem Hydraulikzylinderboden 14 und dem aus dem Zylinder 3 herausstehenden Zylinderkolben 4 angeordnet. Über eine separate Fluidleitung 13 ist es möglich, den Innenzylinderkolben 12 im Inneren des Hydraulikzylinders 3 zu bewegen, so dass dieser den für den Zylinderkolben 4 zu Verfügung stehenden Kolbenraum 10 verringern kann. Dadurch wird der Druck in dem Druckspeicher 9 und dem Kolbenraum 10 ansteigen und ein Anheben des Zylinderkolbens 4 aus dem Hydraulikzylinder 3 bewirken.As in the sectional view of the figure 5 As can be seen, a second piston 12, the so-called inner piston 12, can be installed in the hydraulic system 2, which can be controlled via a separate oil supply and control/regulation. The inner cylinder piston 12 is arranged between the hydraulic cylinder base 14 and the cylinder piston 4 protruding from the cylinder 3 . Via a separate fluid line 13 it is possible to move the inner cylinder piston 12 inside the hydraulic cylinder 3 so that it can reduce the piston space 10 available for the cylinder piston 4 . As a result, the pressure in the pressure accumulator 9 and the piston chamber 10 will rise and cause the cylinder piston 4 to be lifted out of the hydraulic cylinder 3 .

Für den Ausgleich der Radabnutzung und zum Durchführen eines Levelling wird lediglich ein Schnellanschluss zur Verfügung gestellt, so dass in der Werkstätte mit einer entsprechenden Vorrichtung rasch ein Höhenausgleich realisiert werden kann, indem die für das korrekte Levelling erforderliche Fluidmenge unter den Innenzylinderkolben eingebracht wird.To compensate for wheel wear and to carry out levelling, only a quick connector is provided, so that in the workshop, with a suitable device, height compensation can be carried out quickly by introducing the amount of fluid required for correct leveling under the inner cylinder piston.

Alternativ oder zusätzlich kann die Fluidzufuhr über die separate Fluidleitung 13 auch in Abhängigkeit eines gemessenen Abstands vom Wagenkasten 16 zu einem Bahnsteig oder der Fahrwerkseinheit 17 automatisch eingestellt werden. Dazu wird einfach über die separate Fluidleitung 13 die entsprechende Menge an Fluid eingeführt bzw. abgelassen, so dass man die gewünschte Höhe des Wagenkastens 16 erreicht.Alternatively or additionally, the fluid supply can also be adjusted automatically via the separate fluid line 13 as a function of a measured distance from the car body 16 to a platform or the chassis unit 17 . For this purpose, the appropriate amount of fluid is simply introduced or discharged via the separate fluid line 13 so that the desired height of the car body 16 is reached.

Zur Erzeugung des hydraulischen Drucks, welche bspw. zur Niveauregulierung sowie zum Ausgleich von Leckagen genutzt werden kann, kann eine hydraulische Leistungseinheit vorgesehen sein. Diese kann entweder in kompakter Form direkt an der Hydraulikzylinderanordnung 2 oder separat in der Fahrwerkseinheit 17 angeordnet sein. Eine Anordnung am Wagenkasten 16, um damit die typischerweise zwei mit dem Wagenkasten 16 in Verbindung stehenden Fahrwerkseinheiten 17 zu verbinden und so die dort angeordneten Abnehmer von Hydraulikfluid zu versorgen, ist ebenfalls denkbar. Vorteilhafterweise ist in eine solche hydraulische Leistungseinheit ist mit Vorteil auch gleich die elektrische und/oder elektronische Steuerung integriert.A hydraulic power unit can be provided to generate the hydraulic pressure, which can be used, for example, to regulate the level and to compensate for leaks. This can either be arranged in a compact form directly on the hydraulic cylinder arrangement 2 or separately in the chassis unit 17 . An arrangement on the car body 16 in order to connect the typically two running gear units 17 connected to the car body 16 and thus those arranged there Supplying consumers with hydraulic fluid is also conceivable. Advantageously, the electrical and/or electronic control is also integrated in such a hydraulic power unit.

Da zur reinen Niveauregulierung sowie zum Ausgleich von Leckage sehr wenig Energie benötigt wird, kann das System auch mit einer autarken Energieversorgung ausgerüstet werden.Since very little energy is required for pure level control and for compensating for leakage, the system can also be equipped with a self-sufficient energy supply.

So können beispielsweise die laufend Druckänderungen in der Hydraulikzylinderanordnung 2 als Energiequelle genutzt werden. Diese Energie wird über einen kleinen Generator genutzt, um eine Batterie zu laden, welche die Stromversorgung der Elektronik, Sensorik, der Ventile sowie auch der Pumpe sicherstellt. Das Prinzip des Generators basiert vorzugsweise auf der Nutzung von Druckänderungen in der Hydraulikzylinderanordnung 2, welche über kleine Bewegungen über entsprechende Generatoren in elektrische Energie umgewandelt werden.For example, the ongoing pressure changes in the hydraulic cylinder assembly 2 can be used as an energy source. This energy is used by a small generator to charge a battery, which ensures the power supply for the electronics, sensors, valves and pump. The principle of the generator is preferably based on the use of pressure changes in the hydraulic cylinder arrangement 2, which are converted into electrical energy via small movements via corresponding generators.

Bezugszeichenliste:Reference list:

11
hydropneumatische Federunghydropneumatic suspension
22
Hydraulikzylinderanordnunghydraulic cylinder arrangement
33
Hydraulikzylinderhydraulic cylinder
44
Zylinderkolbencylinder piston
55
oberes Federsegmentupper spring segment
66
unteres Federsegmentlower spring segment
77
Befestigungstellermounting plate
88th
Schichten eines FedersegmentsLayers of a feather segment
99
Druckspeicheraccumulator
1010
kompressierbarer Raum der Hydraulikzylinderanordnungcompressible space of the hydraulic cylinder arrangement
1111
Verbindungsleitungconnection line
1212
Innenzylinderkolbeninner cylinder piston
1313
separate Fluidleitungseparate fluid line
1414
Hydraulikzylinderbodenhydraulic cylinder floor
1515
Fahrzeugvehicle
1616
Wagenkastencar body
1717
Fahrwerkseinheit / FahrwerksrahmenUndercarriage unit / undercarriage frame
1818
Traversetraverse
18'18'
elastische Traverseelastic traverse
1919
Jochyoke
2020
Konusfedercone spring
2121
GlockeBell jar
2222
Längspufferlongitudinal buffer
2323
Anschläge zum Begrenzen einer LängsbewegungStops to limit a longitudinal movement
2424
Vertikaldämpfervertical damper
2525
Querdämpfercross damper
2626
Querpuffercross buffer
2727
Wankstabilisatorroll stabilizer
2828
Primärfederung RadsatzPrimary suspension wheelset
2929
Primärdämpfung RadsatzPrimary damping wheelset
3030
Radsatzführungwheelset guidance
3131
Radsatzwheelset
3232
Federsegmentgegenstückspring segment counterpart
3333
GleisTrack
AA
Querauslenkungtransverse deflection

Claims (17)

  1. Hydropneumatic suspension (1) suitable for use in a vehicle (15), in particular a rail vehicle, comprising:
    a hydraulic cylinder arrangement (2) having a hydraulic cylinder (3) and a cylinder piston (4) that is movable back and forth in the hydraulic cylinder (3),
    a first spring segment (5), which is arranged at one of the two longitudinal ends of the hydraulic cylinder arrangement (2), and
    a second spring segment (6), which is arranged at the other of the two longitudinal ends of the hydraulic cylinder arrangement (2), wherein
    the respective longitudinal ends of the hydraulic cylinder arrangement (2) and the associated spring segments (5, 6) are designed in each case in such a way that they form an arc shape curving inwards towards the hydraulic cylinder arrangement (2),
    the hydraulic cylinder (3) as well as the cylinder piston (4) are each rigidly connected to a mounting plate (7), which, in cross-section, has an arc shape, for example a circular arc shape, sloping inwards towards the longitudinal axis of the hydraulic cylinder arrangement (2), such that this arc shape has a point at a minimal distance near or on the longitudinal axis of the hydraulic cylinder arrangement (2),
    the spring segments (5, 6) are each arranged on the side of the respective mounting plate (7) facing away from the hydraulic cylinder arrangement (2), and
    the spring segments (5, 6) are layered spring segments, for example layered rubber springs, which preferably have a plurality of layers (8) arranged side by side, such that a plurality of layers (8) are provided perpendicularly to the longitudinal axis of the hydraulic cylinder arrangement (2) in order to achieve a high vertical compressive strength.
  2. Suspension (1) according to claim 1, wherein the arc shape is a circular arc shape, which preferably has its lowest point or highest point facing a longitudinal axis of the hydraulic cylinder arrangement (2).
  3. Suspension (1) according to one of the preceding claims, wherein, furthermore, a pressure accumulator (9), for example in the form of a bladder accumulator, diaphragm accumulator or spring-loaded accumulator, is provided, which is connected by way of a connecting line (11) to the chamber (10) of the hydraulic cylinder arrangement (2) that is compressible by the cylinder piston (4), wherein the connecting line (11) preferably has a large line cross-section such that only a minimum or no damping effect occurs.
  4. Suspension (1) according to claim 3, further comprising a restrictor or a valve in the connecting line (11) for passively or actively influencing the vertical damping characteristic.
  5. Suspension (1) according to one of the preceding claims, further comprising an internal cylinder piston (12) in the hydraulic cylinder (3), which can be driven via a separate fluid line (13) and is designed to vary the size of the chamber (10) of the hydraulic cylinder arrangement (2) that is compressible by the cylinder piston (4), wherein the internal cylinder piston (12) is preferably arranged between the hydraulic cylinder base (14) and the end of the cylinder piston (4) that is inserted in the hydraulic cylinder (3), and the separate fluid line (13) is routed through the hydraulic cylinder base (14).
  6. Suspension (1) according to one of the preceding claims, further comprising a hydraulic power unit for providing hydraulic fluid under a certain pressure to the hydraulic cylinder arrangement (2), wherein the hydraulic power unit is preferably arranged on the hydraulic cylinder arrangement (2).
  7. A vehicle (15), in particular a rail vehicle, comprising:
    a vehicle body (16), and
    a chassis unit (17), wherein
    the vehicle body (16) is supported on the chassis unit (17) by way of a suspension system,
    characterized in that
    the suspension system comprises a hydropneumatic suspension (1) according to one of the preceding claims, wherein the suspension (1) preferably contacts the vehicle body (16) on top with one of the two spring segments (5, 6) and the chassis unit (17) arranged below with the other spring segment (5, 6).
  8. Vehicle (15) according to claim 7, wherein the spring segment (5) directed towards the vehicle body (16) comprises a plurality of separate spring segment units spaced apart in the longitudinal direction of the vehicle (15), and the spring segment (6) directed towards the chassis unit (17) preferably comprises a plurality of separate spring segment units spaced apart in the longitudinal direction of the vehicle (15).
  9. Vehicle (15) according to one of the preceding claims 7 or 8, wherein the suspension (1) is arranged at a height of the vehicle (15) such that the lower spring segment (6), i.e. the spring segment associated with the chassis unit (17), comes to rest at the pitch centre of the chassis unit (17).
  10. Vehicle (15) according to one of the preceding claims 7 to 9, wherein the upper spring segment (5), i.e., the spring segment associated with the vehicle body (16), is supported directly on the vehicle body (16), on a cross-member (18) or on a yoke (19), which serves to integrate an emergency suspension.
  11. Vehicle (15) according to one of the preceding claims 7 to 10, wherein a conical spring (20), preferably made of rubber, is arranged between the hydraulic cylinder (3) and the lower spring segment (6) so as to implement an emergency suspension.
  12. Vehicle (15) according to one of the preceding claims 7 to 11, wherein at least two, ideally four, conical springs (20) are provided above the upper spring segment (5) in series with the suspension (1) between a yoke (19) that cooperates with the suspension (1) and a cross-member (18) or the vehicle body (16) so as to implement an emergency suspension, wherein the at least two conical springs (20) are preferably arranged offset with respect to one another in the longitudinal or transverse direction of the vehicle (15).
  13. Vehicle (15) according to one of the preceding claims 7 to 12, wherein conical springs (20) are provided as an emergency suspension on an outer edge between a cross-member (18) and the vehicle body (16), and/or an elastic cross-member (18) in series with the hydropneumatic suspension (1) serves as an emergency suspension.
  14. Vehicle (15) according to one of the preceding claims 7 to 13, wherein the spring segment (5) arranged on top is in contact with a yoke (19), in respect of which the hydropneumatic suspension (1) exhibits a certain play in the longitudinal direction of the vehicle (15), and the upper component of the suspension (1), known as the bell (21), has at least one longitudinal buffer (22), in particular in the form of a rubber spring having an internal stop, between the yoke (19) connected to the vehicle body (16) and the bell (21), in order to generate a progressive longitudinal damping characteristic, wherein the yoke (19) preferably engages around the bell (21) in the longitudinal direction of the vehicle (15) like a cap.
  15. Vehicle (15) according to claim 14, wherein, furthermore, the chassis unit (17) comprises stops (23) for limiting a longitudinal movement of the hydraulic cylinder (3) and the bell (21), so as to transmit high impact forces in the longitudinal direction of the vehicle (15).
  16. Vehicle (15) according to one of the preceding claims 7 to 14, further developed with the features of claim 6, wherein the hydraulic power unit is arranged separately in the chassis unit (17) or in the vehicle body (16).
  17. Vehicle (15) according to one of the preceding claims 7 to 15, further comprising a generator, which generates electrical energy from pressure changes in the hydraulic cylinder arrangement (2), wherein this energy is preferably used to supply the hydraulic power unit of claim 6.
EP21167034.4A 2020-04-07 2021-04-06 Hydropneumatic suspension for a vehicle Active EP3892515B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102020109599.6A DE102020109599A1 (en) 2020-04-07 2020-04-07 Hydropneumatic suspension for a vehicle

Publications (2)

Publication Number Publication Date
EP3892515A1 EP3892515A1 (en) 2021-10-13
EP3892515B1 true EP3892515B1 (en) 2023-06-21

Family

ID=75426384

Family Applications (1)

Application Number Title Priority Date Filing Date
EP21167034.4A Active EP3892515B1 (en) 2020-04-07 2021-04-06 Hydropneumatic suspension for a vehicle

Country Status (3)

Country Link
EP (1) EP3892515B1 (en)
CN (1) CN113492889A (en)
DE (1) DE102020109599A1 (en)

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2917321A (en) * 1957-10-08 1959-12-15 Fennell Alfred Thomas Car jacking device
DE9304837U1 (en) * 1993-03-30 1993-05-27 Knorr-Bremse AG, 8000 München Pendulum support with spring-loaded support body and additional and emergency spring
AT411349B (en) * 2001-12-11 2003-12-29 Siemens Sgp Verkehrstech Gmbh SUSPENSION DEVICE
DE10238059B4 (en) 2002-08-20 2014-02-13 Liebherr-Aerospace Lindenberg Gmbh spring element
DE10360516C5 (en) * 2003-12-22 2010-12-16 Knorr-Bremse Systeme für Schienenfahrzeuge GmbH Device for secondary suspension of a car body in a rail vehicle with an active spring element
DE102010011211A1 (en) 2010-03-08 2011-09-08 Siemens Aktiengesellschaft Device for limiting pitching motion in rail vehicles
DE102012105310A1 (en) 2012-06-19 2013-12-19 Bombardier Transportation Gmbh Vehicle with a spring device with specifiable cross spring characteristic

Also Published As

Publication number Publication date
EP3892515A1 (en) 2021-10-13
CN113492889A (en) 2021-10-12
DE102020109599A1 (en) 2021-10-07

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