EP2562062B1 - Support device for vertical support of a coupling rod jointed to a vehicle subframe of a rail-bound vehicle - Google Patents

Description

The present invention relates to a supporting device according to the preamble of independent claim 1.

Accordingly, the invention relates in particular to a support device for vertical support preferably via an elastomer Federanlenkung on a car body frame of a track-guided vehicle, in particular rail vehicle, pivotally hinged in the vertical direction coupling rod, wherein the supporting device can be brought into contact with the coupling rod support and one with the support connected and attachable to the vehicle body frame of the vehicle mount, and wherein the support is movable when a critical, acting in the vertical direction on the support external force is exceeded relative to and in the direction of the holder.

A supporting device of the aforementioned type is already known in principle from the prior art, and in particular from rail vehicle technology. The support device is used for vertical support of a hinged to a car body frame in the vertical direction coupling rod.

The publication GB 1,056,340 relates to a support for a central buffer coupling of a rail vehicle. The known from this prior art Support allows an automatic central buffer coupling can be relatively quickly and easily connected to the undercarriage of a car body.

Furthermore, in Fig. 1 shown in a perspective view as an example of a known from the prior art outrigger 110, which via a support
111 is attached to the body frame 60 of a rail vehicle. This support device 110 is used for vertical support of a coupling rod 51, which in the in Fig. 1 illustrated example is hinged with its carriage box-side end portion of a hinge assembly 50 to the car body frame 60.

Specifically, the in Fig. 1 shown hinge assembly 50 to an elastomer Federanlenkung, as described for example in the document EP 1 785 329 A1 is described. Such an elastomer Federanlenkung 50 allows horizontal and vertical swinging and axial rotation of the coupling rod 51. In this way, the coupling rod 51, for example, perform pivotal movements relative to the Wagenkastenuntergestell 60, which occur in particular when cornering a train. Furthermore, the coupling rod 51 vertical displacements, for example, to compensate for height differences between two car bodies to be coupled follow.

In the articulation designed in particular as an elastomeric Federanlenkung 50 usually an elastomeric bearing is formed in which elastomeric spring elements are provided, which serve to dampen the transmitted during normal driving by the coupling rod 51 tensile and impact forces. In general, the elastomer bearing formed in the articulation is suitable for allowing the operationally required Ausschwenkwinkel the coupling rod 51 in the vertical direction V of about ± 6 ° and in the horizontal direction of about ± 15 °.

The support device 110 serves for the vertical support of the coupling rod 51, which is pivotably articulated, inter alia, in the vertical direction V. Such a support in the vertical direction V is necessary, in particular, in order to enable a perfect coupling of two adjacent car bodies. For this, care must be taken that the coupling rod 51 is always present in the horizontal center longitudinal plane during the coupling process.

This is what the in Fig. 1 Supporting device 110 shown a standing in contact with the coupling rod 51 support 112, which is connected via a Abstützstempel 113 with a holder 114. The bracket 114 is connected to the carbody base 60 via the already mentioned carrier 111.

The supporting device 110 is a resiliently formed support, in which the supporting punch 113 is connected to the holder 114 via a spring element 115. Due to the spring element 115, the support plunger 113 and the support 112 connected to the support plunger 113 are pressed against the coupling rod 51 with a certain prestress from below in the vertical direction V. The bias voltage with which the support 112 presses against the coupling rod 51 is adjustable by a suitable choice of the spring constant of the spring element 115 and should be selected so that in a resting state of the coupling rod 51, i. when no dynamic forces in the vertical direction V on the coupling rod 51 attack, the coupling rod 51 is present in the horizontal center position.

The carrier 111 of the supporting device 110, which on the one hand serves to hold the spring element 115 and the Abstützstempels 113, and on the other hand can be achieved on the other hand that the support 112 presses with a certain bias against the coupling rod 51 to be supported, is rigidly connected to the Wagenkastenuntergestell 60 or ., Connected to the housing of the car body frame 60.

In the support device 110 known from the prior art and described above, a direct-acting spring element 115 is usually used for vertical support of the coupling rod 51. Accordingly, the vertical support force introduced by the support 112 into the coupling rod 51 is determined essentially by the spring force resulting from the elastic deformation of the spring element 115. In particular, with increasing vertical deflection of the coupling rod 51, the degree of elastic deformation of the spring element 115 and thus the spring force resulting from the elastic deformation of the spring element 115 increases, which counteracts the vertical deflection of the coupling rod 51 as a supporting force.

This linear relationship between the spring force of the spring element 115 and the support force of the support 112 is unfavorable, in particular in applications, when with the support device 110 via an elastomer Federanlenkung 50 hinged to a car body frame 60 coupling rod 51 is to be supported in the vertical direction V. Since the coupling rod 51 is already partially supported in the vertical direction V by means of an elastomer spring element integrated in the articulation 50 via a coupling rod 51 which is articulated via an elastomeric spring linkage 50 to a carbody subframe 60, conventional supporting devices 110 are those in which the supporting force increases with increasing deformation of the spring element 115 contained in the supporting device 110 increases too hard. In other words, with such a supporting device 110, the coupling rod 51 can no longer sufficiently pivot in the vertical direction V relative to the car body frame 60, as a result, increased forces can occur in the Kupplungsstangenanlenkung 50, which can damage the linkage 50 and the vehicle chassis 60.

Based on this problem, the present invention, the object of developing a supporting device of the type mentioned in that this particular for supporting a via an elastomer Federanlenkung to a car body chassis hinged coupling rod is used without increased driving forces in the vertical direction occur, which can lead to damage to the hinge assembly and the car body frame.

This object is achieved by the subject matter of the independent claim 1.

Accordingly, it is proposed in the inventive solution that the support device of the type mentioned further comprises a spring mechanism with at least one spring element which is coupled via a power transmission mechanism with the support and the support of the support device, that the at least one spring element during a movement of the support is elastically deformed relative to the holder, wherein the force transmission mechanism is adapted to translate a resulting from the elastic deformation of the at least one spring element spring force in one of the force acting on the support external force opposing supporting force.

The achievable with the solution according to the invention are obvious: by providing a force transmission mechanism is achieved that the resulting from the elastic deformation of the at least one spring element of the support spring force is not transmitted directly to the support and there as a supporting force in the vertical direction on the Support counteracts acting external force. Rather, a mechanism is used in the support device according to the invention, with which a translation of the elastic deformation of the at least one spring element of the support spring force resulting in the supporting force, which counteracts the force acting on the support external force. The relationship between the spring force of the at least one spring element and the support force ultimately acting on the coupling rod to be supported in the vertical direction is determined by the construction of the power transmission mechanism. In particular, the response and the spring characteristic of the supporting force exerted on the support rod to be supported with the supporting rod to the specific application, so that in particular those vertical support forces can be taken into account, which is exercised for example by a provided in the articulation of the coupling rod elastomeric spring arrangement.

The force transmission preferably has a mechanism with which a distance traveled by the support during a movement relative to the holder can be translated into a spring travel about which the at least one spring element is elastically deformed during the movement of the support relative to the holder. With this embodiment, it is possible to decouple the characteristic of the supporting force from the spring characteristic of the at least one spring element. In applications in which a hinged via an elastomeric Federanlenkung coupling rod is to support in the vertical direction, it is particularly advantageous to perform the mechanics of power transmission such that between the spring characteristic of the supporting force and the spring characteristic of the at least one spring element an asynchronous relationship exists in that the supporting force decreases at least in a working region of the supporting device, the stronger the at least one spring element of the supporting device is elastically deformed.

For the mechanics of power transmission, it is conceivable to provide, for example, a gear arrangement with which the resulting from the elastic deformation of the at least one spring element spring force is translated into the supporting force, which is introduced by the support in the supportive coupling rod in the vertical direction. Technically simpler and in particular less susceptible to failure, however, is a force transmission mechanism which has at least one scissors arrangement consisting of a single pair of scissors with two legs of equal length, these two legs being movable relative to one another about a common horizontal axis passing through the centers of the legs. In this realization of the power transmission mechanism, each leg is connected in each case via a fixed bearing with the holder on the one hand and via a movable bearing with the support on the other. The at least one spring element is designed as a compression spring and engages on a first leg of the two legs of equal length on the one hand and on the second leg of the two legs of equal length on the other.

In this embodiment of the power transmission mechanism, it is particularly advantageous if a bias of the at least one spring element is adjustable. This can be done, for example, that the at least one spring element formed as a compression spring is connected via a first and a second stop with the first and second leg, wherein the distance between the two stops is reduced to increase the bias of the spring element.

By the term "fixed bearing" as used herein is meant a bearing with which a leg of a pair of scissors of the scissor assembly is connected to the support of the support device such that the leg relative to the support or the support of the support device around a Horizontal axis is rotatable while the other two translational degrees of freedom are fixed.

By the term "floating bearing" as used herein is meant a bearing in which a translational degree of freedom is fixed allowing rotation of the leg relative to the support and movement of the leg in the longitudinal direction of the support. Preferably, a floating bearing is realized by means of an elongated hole extending in the longitudinal direction of the support or the holder.

As an alternative to the last-mentioned embodiment, in which the force transmission mechanism has a scissors arrangement consisting of a single pair of scissors, in a preferred development of the solution according to the invention, the force transmission mechanism has at least one double scissors arrangement consisting of a first and a second pair of scissors. Each pair of scissors of the double-scissors arrangement has two legs of equal length, which are movable relative to each other about a common horizontal axis passing through the centers of the two legs. In each case, a first leg of each pair of scissors of the double scissor assembly is connected via a fixed bearing with the support and a floating bearing with the holder. A second leg of each pair of scissors of the double scissor assembly is connected via a fixed bearing with the bracket and a floating bearing with the support. In this realization of the power transmission mechanism, the at least one spring element is to be designed as a tension spring and should engage directly or indirectly on at least one leg of the first pair of scissors on the one hand and on at least one leg of the second pair of scissors on the other hand.

In an advantageous development of the last-mentioned embodiment, in which the support device has a power transmission mechanism with a double-scissors arrangement, it is provided that the longitudinal axis of the tension spring designed as a spring element is located on a horizontal axis which is perpendicular to the horizontal axis, around which the legs of the first pair of scissors of the double scissor assembly are movable relative to each other, and on the other hand perpendicular to the horizontal axis about which the legs of the second pair of scissors of the double scissor assembly are relatively movable. In this way, a particularly compact designed supporting device is provided. Of course, other embodiments are conceivable in this regard.

To be able to adjust the operating point of the support, ie the operating point on the characteristic of the supporting force, for example, depending on the specific application in a support device in which the force transmission mechanism has a double-scissors arrangement, is in a preferred embodiment the last-mentioned embodiment provides that the tension spring designed as at least one spring element between a first and a second abutment is arranged, wherein the distance between the first and the second abutment is adjustable, and wherein the tension spring designed as at least one spring element at maximum distance between the first and second abutment is already in a prestressed state when no external force acting in the vertical direction on the support.

In another advantageous realization of the power transmission mechanism used in the support device according to the invention, it is provided that this has at least one double scissors arrangement consisting of a first and a second scissors, wherein - as in the previously mentioned embodiment - each pair of scissors of the double-scissors arrangement comprises two equal-length legs which are movable relative to one another about a common horizontal axis extending through the centers of the two legs, wherein in each case a first leg of each pair of scissors of the double-scissor arrangement via a fixed bearing with the support and a floating bearing with the holder and a second leg of each pair of scissors of the double scissor assembly is connected via a fixed bearing with the holder and a floating bearing with the support. In contrast to the embodiment discussed above, however, the at least one spring element is now designed as a compression spring and is arranged between a first bolt, which lies on the horizontal axis about which the legs of the first pair of scissors of the double shear arrangement are movable relative to one another, and an abutment. wherein this abutment is connected via a pull rod to a second bolt which lies on the horizontal axis about which the legs of the second pair of scissors of the double scissor assembly are movable relative to each other.

Preferably, the first pin with the legs of the first pair of scissors shears assembly and the second pin with the legs of the second pair of scissors of the double shear arrangement are connected such that the respective legs are rotatable relative to the bolts.

In a preferred realization of the last-mentioned embodiment, it is provided that the at least one spring element is designed as a compression spring ring, through which the tie rods extend at least in regions, wherein the abutment has a first counterpart element arranged on a first end region of the drawbar, in particular a nut, and a second counterpart element, in particular a nut, arranged on an opposite second end region. The at least one spring element designed as a compression spring element is clamped between the first counter element and the first pin. Advantageously, it is provided that the distance between the first counter-element and the second counter-element is variable in order to adjust a bias of the at least one spring element and thus the operating point of the support can.

More preferably, it is provided in the last-mentioned embodiment that the spring mechanism has at least a first and a second spring element, which are each formed as a compression spring ring, wherein the at least one first spring element between the first counter-element and the first bolt and the at least one second spring element between the second counter element and the second bolt are arranged.

It is conceivable here that the at least one first spring element is accommodated in a first spring housing connected to the first bolt, and that the at least one second spring element is received in a second spring housing connected to the second bolt. These spring housings simultaneously take over a guide of the correspondingly received spring elements.

Finally, it is preferred if the support of the support device has a flange region, via which the support device can be preferably detachably fastened to the car body underframe of the vehicle. Accordingly, the support device is suitable for subsequent retrofitting, which is the case, for example, when a commonly arranged between two car bodies of a multi-unit rail vehicle close-coupling separated and the individual car bodies must be towed.

Hereinafter, exemplary embodiments of the inventive solution will be described with reference to the accompanying drawings.

Fig. 1

eine perspektivische Ansicht einer aus dem Stand der Technik bekannte Abstützvorrichtung;

Fig. 2

eine perspektivische Ansicht einer exemplarischen Ausführungsform der erfindungsgemäßen Abstützvorrichtung im eingebauten Zustand;

Fig. 3

eine Seitenansicht der Abstützvorrichtung gemäß Fig. 2;

Fig. 4a

eine Längsschnittansicht auf die Abstützvorrichtung gemäß Fig. 1 im unbelasteten Zustand;

Fig. 4b

eine Draufsicht auf die Abstützvorrichtung gemäß Fig. 4a in einer längsgeschnitten Darstellung;

Fig. 4c

eine Ansicht auf die Stirnseite der Abstützvorrichtung gemäß Fig. 4a;

Fig. 4d

eine perspektivische Ansicht auf die Abstützvorrichtung gemäß Fig. 4a;

Fig. 4e

eine teilgeschnittene perspektivische Ansicht auf die Abstützvorrichtung gemäß Fig. 4a;

Fig. 5a

eine perspektivische Ansicht auf die Abstützvorrichtung gemäß Fig. 1 in einem belasteten Zustand nach Ausschöpfung des vertikalen Abstützvermögens der Abstützvorrichtung;

Fig. 5b

eine Längsschnittansicht durch die Abstützvorrichtung gemäß Fig. 5a;

Fig. 6

ein Kraft-/Weg-Diagramm der Abstützvorrichtung gemäß Fig. 1; und

Fig. 7

eine Längsschnittansicht auf eine weitere exemplarische Ausführungsform der erfindungsgemäßen Abstützvorrichtung im unbelasteten Zustand.

Show it:

Fig. 1

a perspective view of a known from the prior art supporting device;

Fig. 2

a perspective view of an exemplary embodiment of the supporting device according to the invention in the installed state;

Fig. 3

a side view of the supporting device according to Fig. 2 ;

Fig. 4a

a longitudinal sectional view of the support device according to Fig. 1 in the unloaded condition;

Fig. 4b

a plan view of the support device according to Fig. 4a in a longitudinally cut representation;

Fig. 4c

a view of the front side of the supporting device according to Fig. 4a ;

Fig. 4d

a perspective view of the support device according to Fig. 4a ;

Fig. 4e

a partially cutaway perspective view of the support device according to Fig. 4a ;

Fig. 5a

a perspective view of the support device according to Fig. 1 in a loaded state after exhaustion of the vertical support capability of the support device;

Fig. 5b

a longitudinal sectional view through the support device according to Fig. 5a ;

Fig. 6

a force / displacement diagram of the supporting device according to Fig. 1 ; and

Fig. 7

a longitudinal sectional view of a further exemplary embodiment of the supporting device according to the invention in the unloaded state.

In Fig. 1 a supporting device 110 known from the prior art is shown, which serves for the vertical support of a coupling rod 51 which is articulated via an elastomeric spring linkage 50 to a carbody undercarriage 60. As already stated in the introduction to the description, this conventional supporting device 110 has a spring element 115 in the form of a helical compression spring which is arranged between a support 112 and a holder 114 and presses the support 112 in the direction of the coupling rod 51 to be vertically supported. The holder 114 itself is supported on the carrier body frame 60 via a carrier 111.

Accordingly, comes to vertical support of the coupling rod 51 in the conventional in Fig. 1 supporting device 110 shown a construction with a direct-acting helical compression spring 115 is used, with increasing vertical deflection of the coupling rod 51 from the elastic deformation of the designed as a helical compression spring spring element 115 resulting spring force according to the characteristic of the spring element 115 continues to increase. This phenomenon occurs regardless of whether as a spring element 115 is a helical compression spring formed of metal or an elastomeric spring, for example made of rubber material or a differently designed spring is used.

The conventional design of the support device 110 does not allow the vertical support force exerted on the coupling rod 51 by the support device 110 to be adapted to the individual application. In particular, no optimal vertical support of a coupling rod 51 can be effected with the conventional supporting device 115 when it already experiences a vertical supporting force, for example via an elastomer assembly integrated in the joint arrangement 50. The same applies to coupling rods 51, which are connected via a spherical bearing articulated to the car body frame 60 of a vehicle.

To remedy this disadvantage, the invention proposes to decouple the vertical supporting force to be introduced by the supporting device into the coupling rod to be supported by a suitable mechanism from the spring characteristic of the at least one spring element of the supporting device be able to achieve a favorable force curve for the particular application.

Possible implementations of the force transmission mechanism proposed according to the invention are described in more detail below with reference to the accompanying drawings.

Fig. 2 shows in detail a first exemplary embodiment of a supporting device 100 in the installed state, in which with the supporting device 100, a coupling rod 51 is supported in the vertical direction V. The coupling rod 51 is in the in Fig. 1 illustrated embodiment via an elastomer Federanlenkung 50 with a (not explicitly shown) Wagenkastenuntergestell a track-guided vehicle, in particular rail vehicle connected. The construction of the elastomeric Federanlenkung 50 will be subsequently with reference to the illustration in Fig. 3 described in more detail.

Specifically, the illustration is in Fig. 3 It can be seen that the elastomer Federanlenkung 50 has a connectable to the car body frame of the vehicle base plate 52 through which the transferred during driving the vehicle via the coupling rod 51 tensile and impact forces are introduced into the car body frame. The elastomeric Federanlenkung 50 further includes a zugstangenseitiges front elastomeric spring element 53 between a zugstangenseitigen front spring plate 54 and the pressure plate 52 and a carriage box side rear elastomeric spring element 55 between the pressure plate 52 and a rear spring plate 56, said elastomeric spring elements 53, 55 are clamped accordingly. The rear spring plate 56 is fixed by means of a lock nut 57 at a center piece 58, said center piece 58 runs through the designed as a hollow rubber springs elastomeric spring elements 53, 55 and by corresponding provided in the spring plates 54, 56 and in the base plate 52 through holes and with the coupling rod 51 is connected.

With the articulation 50 designed as an elastomer spring joint, not only can the tensile and impact forces transmitted by the coupling rod 51 during driving be damped, but also a vertical support of the coupling rod 51 causes, but which is not sufficient to keep the coupling rod 51 in the uncoupled state in the horizontal center longitudinal plane.

For this purpose comes in the in the Figures 2 and 3 illustrated embodiment, the support device 100 according to the invention for use, which - as in particular the representations in the FIGS. 4 and 5 can be removed - a can be brought into contact with the coupling rod 51 in contact support 1 and a connected to the support 1 and attachable to the car body frame of the vehicle bracket 2. As shown, the support 1 may be formed as a platform and the bracket 2 as a base frame. In this case, it is particularly appropriate to provide recesses in the support 1 designed as a platform and / or in the holder 2 designed as a base frame at suitable areas, in order to reduce the total weight of the supporting device 100.

The holder 2 is connected to a flange region 9 or has a flange region 9 (cf. Figures 2 and 3 ), via which the support device 100 can be preferably releasably secured to the car body frame of the vehicle.

In order to decouple the supporting force exerted by the supporting device 100 on the coupling rod 51 to be supported in the vertical direction V from the spring characteristic of a spring element of the supporting device 100, in the exemplary embodiment according to FIGS FIGS. 2 to 5 a power transmission mechanism 10 is used. About this force transmission mechanism 10 are in the support device 100 according to the FIGS. 2 to 5 provided spring elements 3a, 3b coupled to the support 1 and the holder 2, in such a way that these spring elements 3a, 3b are elastically deformed during a movement of the support 1 relative to the holder 2.

As explained below with reference to the illustrations in the FIGS. 4 and 5 will be described in more detail, the force transmission mechanism 10 is formed in particular for translating a spring force resulting from the elastic deformation of the spring elements 3a, 3b in a supporting force acting in the vertical direction V.

In detail, the power transmission mechanism 10 at the in the FIGS. 2 to 5 illustrated embodiment, a double-scissors arrangement consisting of a first and a second scissors 15, 16. Each pair of scissors 15, 16 of the double scissors arrangement consists of two equal-length legs 17a, 17b; 18a, 18b, which are movable relative to one another about a common horizontal axis H2, H3 extending through the centers of the two legs 17a, 17b, 18a, 18b. In each case, a first leg 17a, 18a of each pair of scissors 15, 16 is connected to the support 1 via a fixed bearing 19a, 19b and to the bracket 2 via a movable bearing 20a, 20b. The corresponding second leg 17b, 18b of each pair of scissors 15, 16, however, is connected to the support 2 via a fixed bearing 19c, 19d and to the support 1 via a floating bearing 20c, 20d.

In particular, in the in the FIGS. 2 to 5 illustrated exemplary embodiment provided that a total of two double-scissor assemblies of the type described above are used, each with a double scissor assembly is disposed on a side surface of the support device 100.

The spring elements 3a, 3b are designed as compression spring packets and lie in the illustrated embodiment between a first pin 4 and an abutment. The first bolt 4 lies on the horizontal axis H2 about which the legs 17a, 17b of the first pair of scissors 15 of the double-scissors arrangement are movable relative to one another. In detail, the first bolt 4 is connected to the two legs 17a, 17b of the first pair of scissors 15 such that the legs 17a, 17b are rotatable about the horizontal axis H2 relative to the first pin 4. For this purpose again a fixed bearing is used. The abutment is connected via a pull rod 8 with a second pin 5, said second pin 5 is located on the horizontal axis H3, about which the legs 18a, 18b of the second pair of scissors 16 of the double-scissors assembly are relatively movable. In detail, the legs 18a, 18b of the second pair of scissors 16 are connected via a fixed bearing to the second pin 5 such that the legs 18a, 18b are rotatable about the horizontal axis H3.

As in particular the partially cut perspective representation in Fig. 4e can be removed, the spring elements 3a, 3b are each formed as Druckfederringpakete through which the pull rod 8 at least partially extends, wherein the abutment has a arranged at a first end portion of the tie rod 8 first counter element 6a in the form of a nut and arranged at an opposite second end portion of the tie rod 8 second counter element 6b also in the form of a nut. The first formed as a compression spring ring package spring element 3a is disposed between the first counter-element 6a and the first pin 4. By contrast, the spring element 3b, which is also designed as a compression spring ring packet, lies between the second counter element 6b and the second bolt 5. By tightening the counter elements 6a, 6b designed as a nut, the distance between the first counter element 6a and the second counter element 6b can be varied to provide a preload the designed as a compression spring ring packages spring elements 3a, 3b set.

In detail, the spring elements 3a, 3b designed as compression spring ring packages are clamped between the corresponding counter element 6a, 6b and the bottom region of a cup-shaped spring housing 7a, 7b. The respective spring housings 7a, 7b are connected to the first bolt 4 and the second bolt 5, respectively.

By providing such a force transmission mechanism 10, a distance traveled by the support 1 during a movement relative to the holder 2 is translated into a spring travel about which the two spring elements 3a, 3b are elastically deformed relative to the holder 2 during the movement of the support 1 , In particular, a force transmission is realized in which the characteristic of the supporting force of the spring characteristics of the spring elements 3a, 3 is independent.

In Fig. 6 a force / displacement diagram of a support device 100 is shown, which has a power transmission mechanism 10, as in the first exemplary embodiment according to the FIGS. 2 to 5 is used.

Accordingly, when exerting an external force in the vertical direction on the support 1, the support force initially increases and then drops almost linearly after reaching a vertex. Thus, the power transmission mechanism 10 allows that between the characteristic of the supporting force and the spring characteristics the spring elements 3a, 3b is an asynchronous (non-linear) relationship, in such a way that at least in a working area of the supporting device 100 decreases the supporting force, the stronger the spring elements 3a, 3b of the supporting device 100 are elastically deformed.

The support device 100 according to the invention is therefore particularly suitable for (temporarily) supporting a coupling rod 51, for example, a short coupling, when this coupling rod with an elastomer Federanlenkung 50, as described for example in the document EP 1 785 329 B1 is described, is pivotally hinged to the car body chassis of a vehicle. Since short couplings are usually not equipped with vertical support devices, the coupling rod hangs on the bearing only held by the Elastomer Federanlenkung and decreases from the horizontal center longitudinal plane, when the coupling rod 51 is not connected to the coupling rod of an adjacent car body. Accordingly, it is appropriate in this case that the support device 100 according to the invention is mounted on the vehicle underframe to support the coupling rod 51 in the vertical direction, which is required for example for towing the car body. In this case, the spring elements 3a, 3b are adjusted by tightening the counter-elements 6a, 6b designed as a nut so that the support 1 bears against the coupling rod 51. By further tightening the counter elements 6a, 6b, a biasing force can additionally be applied.

Subsequently, for example, a transition coupling can be mounted on the coupling rod 51 to enable towing the vehicle. The support device 100 according to the invention allows a vertical movement of the coupling rod 51 relative to the car body undercarriage while driving.

The solution according to the invention is not based on the previously described with reference to the representations in the FIGS. 2 to 5 described special embodiment of the support 100 limited. In particular, it is conceivable that, instead of the spring elements 3a, 3b designed as compression spring packets, a spring element 3c designed as a tension spring packet is used, which is connected to at least one leg 17a, 17b of the first pair of scissors 15 of the double scissors arrangement on the one hand and on at least one leg 18a, 18b of the second scissors 16 of the double-scissors arrangement on the other hand, as in Fig. 7 is indicated.

Specifically, the in Fig. 7 illustrated embodiment, the longitudinal axis of the trained as Zugfederpaket spring element 3c on a horizontal axis, on the one hand perpendicular to the horizontal axis H2, about which the legs 17a, 17b of the first scissors 15 are relatively movable, and on the other hand perpendicular to the horizontal axis H3 around which the legs 18a, 18b of the second pair of scissors 16 are movable relative to each other.

To the operating point of the supporting force in the supporting device 100 according to the in Fig. 7 to be able to adjust the embodiment designed as Zugfederpaket spring element 3c between a first and a second abutment 21a, 21b arranged, wherein the distance between the first and the second abutment 21a, 21b is adjustable accordingly.

In a further, structurally simple implementation of the solution according to the invention comes as a power transmission mechanism 10, a scissor assembly consisting of a single scissors used, this single scissors has two equal legs, relative to a running through the centers of the two legs common horizontal axis are movable relative to each other. Each leg of the individual scissors is connected via a fixed bearing with the holder on the one hand and via a movable bearing with the support on the other. A designed as a compression spring or compression spring package spring element engages on a first leg of the two equal-length legs of the individual scissors on the one hand and on the corresponding second leg of the two legs of equal length on the other.

LIST OF REFERENCE NUMBERS

1

support

2

bracket

3a, b, c

spring element

4

first bolt

5

second bolt

6a, 6b

counter element

7a, 7b

spring housing

8th

pull bar

9

flange

10

Force transmission mechanism

12a, 12b

fixed bearing

13a, 13b

movable bearing

15, 16

Scissors of a double scissors arrangement

17a, 17b

Thighs of the scissors 15

18a, 18b

Thighs of the scissors 16

19a, 19b

fixed bearing

20a, 20b

movable bearing

21a, 21b

abutment

50

Elastomer spring connection

51

coupling rod

52

baseplate

53

front elastomeric spring element

54

spring plate

55

rear elastomer spring element

56

spring plate

60

Car body underframe

100

Support device

110

Support device (prior art)

111

Carrier (prior art)

112

Support (prior art)

113

Abstützstempel (prior art)

114

Bracket (prior art)

115

Spring element (prior art)

V

vertical direction

H2, H3

horizontal axis

Claims (15)

1. A support device (100) for vertically supporting a coupling rod (51) pivotably articulated vertically (V) to a car body undercarriage (60) of a rail-borne vehicle, particularly a railway vehicle, wherein the support device (100) comprises a support (1) able to be brought into contact with the coupling rod (51) and a mount (2) connected to the support (1) and able to be fixed to the car body undercarriage (60) of the vehicle, and wherein the support (1) can move relative to and toward the mount (2) upon a critical external force acting on the support (1) in the vertical direction (V) being exceeded, wherein the support device (100) further comprises a spring mechanism having at least one spring element (3a, 3b, 3c),
   characterized in that
   the at least one spring element is coupled to the support (1) and the mount (2) by means of a force-transmitting mechanism (10) such that the at least one spring element (3a, 3b, 3c) is elastically deformed upon the support (1) moving relative to the mount (2), wherein the force-transmitting mechanism (10) is designed to convert a spring force resulting from the elastic deformation of the at least one spring element (3a, 3b, 3c) into a supporting force opposite to the force acting on the support (1) and to convert a distance traveled by the support (1) in movement relative to the mount (2) into a spring deflection by which the at least one spring element (3a, 3b, 3c) is elastically deformed upon the movement of the support (1) relative to the mount (2), wherein the supporting force decreases in at least one operating range of the support device (100) the greater the at least one spring element (3a, 3b, 3c) of the support device (100) is elastically deformed.
2. The support device (100) according to claim 1,
   wherein the force-transmitting mechanism (10) is designed to convert a distance traveled by the support (1) in movement relative to the mount (2) into a spring deflection by which the at least one spring element (3a, 3b, 3c) is elastically deformed upon the movement of the support (1) relative to the mount (2).
3. The support device (100) according to claim 1 or 2,
   wherein the force-transmitting mechanism (10) comprises at least one shear assembly consisting of a shear, wherein the shear comprises two arms of equal length able to move relative to one another about a common horizontal axis extending through the centers of the two arms, wherein each arm is respectively connected on one side to the mount (2) via a fixed bearing and on the other side to the support (1) via a floating bearing, and wherein the at least one spring element is configured as a pressure spring and engages a first arm of the two arms of equal length on one side and the second arm of the two arms of equal length on the other side.
4. The support device (100) according to claim 3,
   wherein a pretensioning of the at least one spring element is adjustable.
5. The support device (100) according to claim 1 or 2,
   wherein the force-transmitting mechanism (10) comprises at least one double-shear assembly consisting of a first and second shear (15, 16), wherein each shear (15, 16) of the double-shear assembly has two arms (17a, 17b; 18a, 18b) of equal length able to move relative to one another about a common horizontal axis (H2; H3) extending through the centers of the two arms (17a, 17b; 18a, 18b), wherein a respective first arm (17a, 18a) of each shear (15, 16) is connected to the support (1) via a fixed bearing (19a, 19b) and to the mount (2) via a floating bearing (20a, 20b) and a second arm (17b; 18b) of each shear (15; 16) is connected to the mount (2) via a fixed bearing (19c, 19d) and to the support (1) via a floating bearing (20c, 20d), and wherein the at least one spring element (3c) is configured as a tension spring and engages at least one arm (17a, 17b) of the first shear (15) on one side and at least one arm (18a, 18b) of the second shear (16) on the other side.
6. The support device (100) according to claim 5,
   wherein the longitudinal axis of the at least one spring element (3c) configured as a tension spring lies on a horizontal axis extending perpendicular to the horizontal axis (H2) about which the arms (17a, 17b) of the first shear (15) can move relative to one another on the one hand and, on the other, perpendicular to the horizontal axis (H3) about which the arms (18a, 18b) of the second shear (16) can move relative to one another.
7. The support device (100) according to claim 6,
   wherein the at least one spring element (3c) configured as a tension spring is arranged between a first and a second counter bearing (21a, 21b), wherein the distance between the first and the second counter bearing (21a, 21b) can be adjusted, and wherein the at least one spring element (3c) configured as a tension spring is already in a pretensioned state upon maximum distance between the first and second counter bearing (21a, 21b) when no external force is acting on the support (1) in the vertical direction (V).
8. The support device (100) according to claim 1 or 2,
   wherein the force-transmitting mechanism (10) comprises at least one double-shear assembly consisting of a first and a second shear (15, 16), wherein each shear (15, 16) of the double-shear assembly has two arms (17a, 17b; 18a, 18b) of equal length able to move relative to one another about a common horizontal axis (H2; H3) extending through the centers of the two arms (17a, 17b; 18a, 18b), wherein a respective first arm (17a, 18a) of each shear (15, 16) is connected to the support (1) via a fixed bearing (19a, 19b) and to the mount (2) via a floating bearing (20a, 20b) and a second arm (17b; 18b) of each shear (15; 16) is connected to the mount (2) via a fixed bearing (19c, 19d) and to the support (1) via a floating bearing (20c, 20d), and wherein the at least one spring element (3a, 3b) is configured as a pressure spring and arranged between a first bolt (4) situated on the horizontal axis (H2) about which the arms (17a, 17b) of the first shear (50) can move relative to one another and a counter bearing connected by means of a tension rod (8) to a second bolt (5) situated on the horizontal axis (H3) about which the arms (18a, 18b) of the second shear (16) can move relative to one another.
9. The support device (100) according to claim 8,
   wherein the first bolt (4) is connected to the arms (17a, 17b) of the first shear (15) and the second bolt (5) is connected to the arms (18a, 18b) of the second shear (16).
10. The support device (100) according to claim 8 or 9,
    wherein the at least one spring element (3a, 3b) is configured as a pressure spring washer through which at least part of the tension rod (8) extends, wherein the counter bearing comprises a first counter element (6a), in particular a nut, arranged at a first end region of the tension rod (8) and a second counter element (6b), in particular a nut, arranged at an opposite second end region of the tension rod (8), wherein the at least one spring element (3a, 3b) is clamped between the first counter element (6a) and the first bolt (4).
11. The support device (100) according to claim 10,
    wherein the distance between the first counter element (6a) and the second counter element (6b) is variable in order to adjust the pretensioning of the at least one spring element (3a, 3b).
12. The support device (100) according to claim 10 or 11,
    wherein the spring mechanism comprises at least one first and one second spring element (3a, 3b), each configured as a pressure spring washer, wherein the at least one first spring element (3a) is arranged between the first counter element (6a) and the first bolt (4) and the at least one second spring element (3b) is arranged between the second counter element (6b) and the second bolt (5).
13. The support device (100) according to claim 12,
    wherein a first spring housing (7a) connected to the first bolt (4) is provided in which the at least one first spring element (3a) is accommodated, and wherein a second spring housing (7b) connected to the second bolt (5) is provided in which the at least one second spring element (3b) is accommodated.
14. The support device (100) according to any one of claims 1 to 13,
    wherein the mount (2) comprises a flange area (9) via which the support device (100) can be preferably detachably secured to the car body undercarriage (60) of the vehicle.
15. The support device (100) according to any one of claims 1 to 14,
    wherein the support (1) is designed as a platform and the mount (2) as a base frame.

Images