EP2562062B1 - Support device for vertical support of a coupling rod jointed to a vehicle subframe of a rail-bound vehicle - Google Patents
Support device for vertical support of a coupling rod jointed to a vehicle subframe of a rail-bound vehicle Download PDFInfo
- Publication number
- EP2562062B1 EP2562062B1 EP11178426.0A EP11178426A EP2562062B1 EP 2562062 B1 EP2562062 B1 EP 2562062B1 EP 11178426 A EP11178426 A EP 11178426A EP 2562062 B1 EP2562062 B1 EP 2562062B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- support
- spring
- shear
- spring element
- support device
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Not-in-force
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- 238000010168 coupling process Methods 0.000 title claims description 69
- 238000005859 coupling reaction Methods 0.000 title claims description 68
- 230000008878 coupling Effects 0.000 title claims description 67
- 230000007246 mechanism Effects 0.000 claims description 36
- 238000007667 floating Methods 0.000 claims description 12
- 230000005489 elastic deformation Effects 0.000 claims description 10
- 230000007423 decrease Effects 0.000 claims description 4
- 210000002414 leg Anatomy 0.000 description 51
- 230000005540 biological transmission Effects 0.000 description 27
- 230000006835 compression Effects 0.000 description 18
- 238000007906 compression Methods 0.000 description 18
- 229920001971 elastomer Polymers 0.000 description 17
- 239000000806 elastomer Substances 0.000 description 15
- 238000010276 construction Methods 0.000 description 3
- 238000006073 displacement reaction Methods 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- 210000000689 upper leg Anatomy 0.000 description 2
- 230000000712 assembly Effects 0.000 description 1
- 238000000429 assembly Methods 0.000 description 1
- 238000000418 atomic force spectrum Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 230000036316 preload Effects 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 230000000284 resting effect Effects 0.000 description 1
- 238000009420 retrofitting Methods 0.000 description 1
- 230000003319 supportive effect Effects 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
Images
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B61—RAILWAYS
- B61G—COUPLINGS; DRAUGHT AND BUFFING APPLIANCES
- B61G7/00—Details or accessories
- B61G7/10—Mounting of the couplings on the vehicle
Definitions
- the present invention relates to a supporting device according to the preamble of independent claim 1.
- 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.
- 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.
- 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.
- the coupling rod 51 for example, perform pivotal movements relative to the Wagenkastenuntergestell 60, which occur in particular when cornering a train.
- the coupling rod 51 vertical displacements, for example, to compensate for height differences between two car bodies to be coupled follow.
- 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.
- 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.
- 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.
- 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.
- 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.
- 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.
- 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 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.
- 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.
- 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.
- 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.
- 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.
- 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.
- 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.
- a floating bearing is realized by means of an elongated hole extending in the longitudinal direction of the support or the holder.
- the force transmission mechanism has a scissors arrangement consisting of a single pair of scissors
- 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.
- 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.
- 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.
- 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.
- a particularly compact designed supporting device is provided.
- other embodiments are conceivable in this regard.
- 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.
- 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.
- 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.
- 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.
- 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.
- 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.
- 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.
- 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.
- 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.
- a supporting device 110 known from the prior art 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.
- 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.
- 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.
- 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 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.
- 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.
- 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 zugstangen solved front elastomeric spring element 53 between a zugstangen concentrateen 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.
- the support device 100 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.
- 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.
- a power transmission mechanism 10 is used.
- 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.
- 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.
- 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.
- 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.
- 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.
- 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.
- 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.
- 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.
- the spring elements 3a, 3b are each formed as Druckfederringwee 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.
- 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.
- 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.
- 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 ,
- 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.
- 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.
- the support force 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.
- 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.
- 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.
- 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.
- a biasing force can additionally be applied.
- a transition coupling can be mounted on the coupling rod 51 to enable towing the vehicle.
- the support device 100 allows a vertical movement of the coupling rod 51 relative to the car body undercarriage while driving.
- 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.
- the longitudinal axis of the trained as Switzerlandfederp 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.
- 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.
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Description
Die vorliegende Erfindung betrifft eine Abstützvorrichtung nach dem Oberbegriff des unabhängigen Patentanspruches 1.The present invention relates to a supporting device according to the preamble of
Demgemäß betrifft die Erfindung insbesondere eine Abstützvorrichtung zu vertikalen Abstützen einer vorzugsweise über eine Elastomer-Federanlenkung an einem Wagenkastenuntergestell eines spurgeführten Fahrzeuges, insbesondere Schienenfahrzeuges, in vertikaler Richtung verschwenkbar angelenkten Kupplungsstange, wobei die Abstützvorrichtung eine mit der Kupplungsstange in Kontakt bringbare Abstützung und eine mit der Abstützung verbundene und an dem Wagenkastenuntergestell des Fahrzeuges befestigbare Halterung aufweist, und wobei die Abstützung bei Überschreiten einer kritischen, in vertikaler Richtung auf die Abstützung einwirkenden externen Kraft relativ zu und in Richtung der Halterung bewegbar ist.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.
Eine Abstützvorrichtung der vorstehend genannten Art ist dem Prinzip nach bereits aus dem Stand der Technik, und insbesondere aus der Schienenfahrzeugtechnik bekannt. Dabei dient die Abstützvorrichtung zum vertikalen Abstützen einer an einem Wagenkastenuntergestell in vertikaler Richtung verschwenkbar angelenkten Kupplungsstange.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.
Die Druckschrift
Ferner ist in
111 an dem Wagenkastenuntergestell 60 eines Schienenfahrzeuges befestigt ist. Diese Abstützvorrichtung 110 dient zum vertikalen Abstützen einer Kupplungsstange 51, welche in dem in
111 is attached to the
Im Einzelnen handelt es sich bei der in
In der insbesondere als Elastomer-Federanlenkung 50 ausgebildeten Anlenkung ist üblicherweise ein Elastomerlager ausgebildet, in welchem Elastomer-Federelemente vorgesehen sind, die zum Abdämpfen der im normalen Fahrbetrieb von der Kupplungsstange 51 übertragenen Zug- und Stoßkräften dienen. In der Regel ist das in der Anlenkung ausgebildete Elastomerlager geeignet, die betriebsmäßig geforderten Ausschwenkwinkel der Kupplungsstange 51 in der vertikalen Richtung V von etwa ± 6° und in der horizontalen Richtung von etwa ± 15° zuzulassen.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
Die Abstützvorrichtung 110 dient zum vertikalen Abstützen der unter anderem in vertikaler Richtung V verschwenkbar angelenkten Kupplungsstange 51. Eine derartige Abstützung in vertikaler Richtung V ist insbesondere notwendig, um ein einwandfreies Kuppeln zweier benachbarter Wagenkästen zu ermöglichen. Hierfür ist Sorge zu tragen, dass die Kupplungsstange 51 beim Kupplungsvorgang stets in der horizontalen Mittenlängsebene vorliegt.The
Hierzu wiest die in
Bei der Abstützvorrichtung 110 handelt es sich um eine federnd ausgebildete Abstützung, bei welcher der Abstützstempel 113 über ein Federelement 115 mit der Halterung 114 verbunden ist. Aufgrund des Federelements 115 wird der Abstützstempel 113 und die mit dem Abstützstempel 113 verbundene Abstützung 112 mit einer gewissen Vorspannung von unten in vertikaler Richtung V gegen die Kupplungsstange 51 gedrückt. Die Vorspannung, mit welcher die Abstützung 112 gegen die Kupplungsstange 51 drückt, ist durch eine geeignete Wahl der Federkonstante des Federelements 115 einstellbar und sollte so gewählt sein, dass in einem Ruhezustand der Kupplungsstange 51, d.h. wenn keine dynamischen Kräfte in vertikaler Richtung V an der Kupplungsstange 51 angreifen, die Kupplungsstange 51 in der horizontalen Mittenlage vorliegt.The supporting
Der Träger 111 der Abstützvorrichtung 110, welcher einerseits zum Halten des Federelements 115 und des Abstützstempels 113 dient, und über welchen andererseits erreicht werden kann, dass die Abstützung 112 mit einer gewissen Vorspannung gegen die abzustützende Kupplungsstange 51 drückt, ist starr mit dem Wagenkastenuntergestell 60 bzw. mit dem Gehäuse des Wagenkastenuntergestells 60 verbunden.The
Bei der aus dem Stand der Technik bekannten und vorstehend beschriebenen Abstützvorrichtung 110 kommt zur vertikalen Abstützung der Kupplungsstange 51 üblicherweise ein direkt wirkendes Federelement 115 zum Einsatz. Demnach wird die von der Abstützung 112 in die Kupplungsstange 51 eingeleitete vertikale Abstützkraft im Wesentlichen durch die aus der elastischen Verformung des Federelements 115 resultierende Federkraft bestimmt. Insbesondere nimmt bei zunehmender vertikaler Auslenkung der Kupplungsstange 51 der elastische Verformungsgrad des Federelements 115 und somit die aus der elastischen Verformung des Federelements 115 resultierende Federkraft zu, welche als Abstützkraft der vertikalen Auslenkung der Kupplungsstange 51 entgegenwirkt.In the
Dieser lineare Zusammenhang zwischen der Federkraft des Federelements 115 und der Abstützkraft der Abstützung 112 ist insbesondere in Anwendungsfällen ungünstig, wenn mit der Abstützvorrichtung 110 eine über eine Elastomer-Federanlenkung 50 an einem Wagenkastenuntergestell 60 angelenkte Kupplungsstange 51 in vertikaler Richtung V abgestützt werden soll. Da bei einer über eine Elastomer-Federanlenkung 50 an einem Wagenkastenuntergestell 60 angelenkte Kupplungsstange 51 die Kupplungsstange 51 über das in der Anlenkung 50 integrierte Elastomer-Federelement bereits teilweise in vertikaler Richtung V abgestützt wird, sind herkömmliche Abstützvorrichtungen 110, bei welchen die Abstützkraft mit zunehmender Verformung des in der Abstützvorrichtung 110 enthaltenen Federelements 115 zunimmt, zu hart. Mit anderen Worten, mit einer derartigen Abstützvorrichtung 110 lässt sich die Kupplungsstange 51 nicht mehr ausreichend in vertikaler Richtung V relativ zu dem Wagenkastenuntergestell 60 verschwenken, infolgedessen in der Kupplungsstangenanlenkung 50 erhöhte Kräfte auftreten können, die die Anlenkung 50 bzw. das Fahrzeuguntergestell 60 beschädigen können.This linear relationship between the spring force of the
Auf Grundlage dieser Problemstellung liegt der vorliegenden Erfindung die Aufgabe zugrunde, eine Abstützvorrichtung der eingangs genannten Art dahingehend weiterzubilden, dass diese insbesondere auch zum Abstützen von über eine Elastomer-Federanlenkung an einem Wagenkastenuntergestell angelenkte Kupplungsstange einsetzbar ist, ohne dass im Fahrbetrieb erhöhte Kräfte in vertikaler Richtung auftreten, die zu einer Beschädigung der Gelenkanordnung bzw. des Wagenkastenuntergestells führen können.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.
Diese Aufgabe wird erfindungsgemäß durch den Gegenstand des unabhängigen Patentanspruches 1 gelöst.This object is achieved by the subject matter of the
Demgemäß wird bei der erfindungsgemäßen Lösung vorgeschlagen, dass die Abstützvorrichtung der eingangs genannten Art ferner einen Federmechanismus mit mindestens einem Federelement aufweist, welches über eine Kraftübersetzungsmechanik derart mit der Abstützung und der Halterung der Abstützvorrichtung gekoppelt ist, dass das mindestens eine Federelement bei einer Bewegung der Abstützung relativ zu der Halterung elastisch verformt wird, wobei die Kraftübersetzungsmechanik ausgebildet ist zum Übersetzen einer aus der elastischen Verformung des mindestens einen Federelements resultierenden Federkraft in eine der auf die Abstützung einwirkenden externen Kraft entgegen gerichtete Abstützkraft.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.
Die mit der erfindungsgemäßen Lösung erzielbaren Vorteile liegen auf der Hand: durch das Vorsehen einer Kraftübersetzungsmechanik wird erreicht, dass die aus der elastischen Verformung des mindestens einen Federelements der Abstützvorrichtung resultierende Federkraft nicht direkt auf die Abstützung übertragen und dort als Abstützkraft der in vertikaler Richtung auf die Abstützung einwirkenden externen Kraft entgegenwirkt. Vielmehr kommt bei der erfindungsgemäßen Abstützvorrichtung eine Mechanik zum Einsatz, mit welcher eine Übersetzung der aus der elastischen Verformung des mindestens einen Federelements der Abstützvorrichtung resultierenden Federkraft in die Abstützkraft erfolgt, welche der auf die Abstützung einwirkenden externen Kraft entgegenwirkt. Das Verhältnis zwischen der Federkraft des mindestens einen Federelements und der letztendlich auf die abzustützende Kupplungsstange in vertikaler Richtung wirkende Abstützkraft wird durch die Konstruktion der Kraftübersetzungsmechanik festgelegt. Insbesondere ist das Ansprechverhalten und die Federkennlinie der mit der Abstützvorrichtung auf die abzustützende Kupplungsstange ausgeübte Abstützkraft an den bestimmten Anwendungsfall anpassbar, so dass insbesondere auch solche vertikalen Abstützkräfte mitberücksichtigt werden können, die beispielsweise durch eine in der Anlenkung der Kupplungsstange vorgesehene Elastomer-Federanordnung ausgeübt wird.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.
Vorzugsweise weist die Kraftübersetzung eine Mechanik auf, mit welcher eine von der Abstützung bei einer Bewegung relativ zu der Halterung zurückgelegte Wegstrecke in einen Federweg übersetzbar ist, um welchen das mindestens eine Federelement bei der Bewegung der Abstützung relativ zu der Halterung elastisch verformt wird. Mit dieser Ausführungsform ist es möglich, die Kennlinie der Abstützkraft von der Federkennlinie des mindestens einen Federelements zu entkoppelt. Bei Anwendungen, in denen eine über ein Elastomer-Federanlenkung angelenkte Kupplungsstange in vertikaler Richtung abzustützen ist, ist es insbesondere von Vorteil, die Mechanik der Kraftübersetzung derart auszuführen, dass zwischen der Federkennlinie der Abstützkraft und der Federkennlinie des mindestens einen Federelements ein asynchroner Zusammenhang besteht derart, dass zumindest in einem Arbeitsbereich der Abstützvorrichtung die Abstützkraft abnimmt, je stärker das mindestens eine Federelement der Abstützvorrichtung elastisch verformt wird.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.
Für die Mechanik der Kraftübersetzung ist es denkbar, beispielsweise eine Getriebeanordnung vorzusehen, mit welcher die aus der elastischen Verformung des mindestens einen Federelements resultierende Federkraft in die Abstützkraft übersetzt wird, welche von der Abstützung in die abzustützende Kupplungsstange in vertikaler Richtung eingeleitet wird. Technisch einfacher und insbesondere weniger störungsanfällig ist jedoch eine Kraftübersetzungsmechanik, welche mindestens eine Scherenanordnung bestehend aus einer Einzel-Schere mit zwei gleichlangen Schenkeln aufweist, wobei diese beiden Schenkel um eine durch die Mittelpunkte der Schenkel verlaufende gemeinsame horizontale Achse relativ zueinander bewegbar sind. Bei dieser Realisierung der Kraftübersetzungsmechanik ist jeder Schenkel jeweils über ein Festlager mit der Halterung einerseits und über ein Loslager mit der Abstützung andererseits verbunden. Das mindestens eine Federelement ist dabei als Druckfeder ausgebildet und greift an einem ersten Schenkel der beiden gleichlangen Schenkel einerseits und an dem zweiten Schenkel der beiden gleichlangen Schenkel andererseits an.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.
Bei dieser Ausführungsform der Kraftübersetzungsmechanik ist es insbesondere von Vorteil, wenn eine Vorspannung des mindestens einen Federelements einstellbar ist. Dies kann beispielsweise dadurch erfolgen, dass das als Druckfeder ausgebildete mindestens eine Federelement über einen ersten und einen zweiten Anschlag mit dem ersten bzw. zweiten Schenkel verbunden wird, wobei zum Erhöhen der Vorspannung des Federelements der Abstand zwischen den beiden Anschlägen reduziert wird.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.
Unter dem hierin verwendeten Begriff "Festlager" ist ein Lager zu verstehen, mit welchem ein Schenkel einer Schere der Scherenanordnung mit der Halterung bzw. der Abstützung der Abstützvorrichtung derart verbunden wird, dass der Schenkel relativ zu der Abstützung bzw. der Halterung der Abstützvorrichtung um eine horizontale Achse drehbar ist, während die anderen zwei Translations-Freiheitsgrade fixiert sind.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.
Unter dem hierin verwendeten Begriff "Loslager" ist eine Lagerung zu verstehen, bei welcher ein Translations-Freiheitsgrad fixiert wird, wobei eine Drehung des Schenkels relativ zur Abstützung bzw. Halterung sowie eine Bewegung des Schenkels in Längsrichtung der Abstützung bzw. Halterung ermöglicht wird. Vorzugsweise wird ein Loslager mit Hilfe eines sich in Längsrichtung der Abstützung bzw. der Halterung erstreckenden Langloches realisiert.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.
Alternativ zu der zuletzt genannten Ausführungsform, bei welcher die Kraftübersetzungsmechanik eine aus einer Einzel-Schere bestehende Scherenanordnung aufweist, ist in einer bevorzugten Weiterbildung der erfindungsgemäßen Lösung vorgesehen, dass die Kraftübersetzungsmechanik mindestens eine Doppel-Scherenanordnung bestehend aus einer ersten und einer zweiten Schere aufweist. Jede Schere der Doppel-Scherenanordnung weist dabei zwei gleichlange Schenkel auf, die um eine durch die Mittelpunkte der beiden Schenkel verlaufende gemeinsame horizontale Achse relativ zueinander bewegbar sind. Jeweils ein erster Schenkel einer jeden Schere der Doppel-Scherenanordnung ist über ein Festlager mit der Abstützung und über ein Loslager mit der Halterung verbunden. Ein zweiter Schenkel einer jeden Schere der Doppel-Scherenanordnung ist über ein Festlager mit der Halterung und über ein Loslager mit der Abstützung verbunden. Bei dieser Realisierung der Kraftübersetzungsmechanik ist das mindestens eine Federelement als Zugfeder auszubilden und sollte direkt oder indirekt an mindestens einem Schenkel der ersten Schere einerseits und an mindestens einem Schenkel der zweiten Schere andererseits angreifen.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 einer vorteilhaften Weiterbildung der zuletzt genannten Ausführungsform, bei welcher die Abstützvorrichtung eine Kraftübertragungsmechanik mit einer Doppel-Scherenanordnung aufweist, ist vorgesehen, dass die Längsachse des als Zugfeder ausgebildeten mindestens einen Federelements auf einer horizontalen Achse liegt, die einerseits senkrecht zu der horizontalen Achse verläuft, um welche die Schenkel der ersten Schere der Doppel-Scherenanordnung relativ zueinander bewegbar sind, und andererseits senkrecht zu der horizontalen Achse verläuft, um welche die Schenkel der zweiten Schere der Doppel-Scherenanordnung relativ zueinander bewegbar sind. Auf diese Weise wird eine besonders kompakt ausgeführte Abstützvorrichtung bereitgestellt. Selbstverständlich sind aber auch andere Ausführungsformen diesbezüglich denkbar.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.
Um bei einer Abstützvorrichtung, bei welcher die Kraftübersetzungsmechanik eine Doppel-Scherenanordnung aufweist, den Arbeitspunkt der Abstützung, d.h. den Arbeitspunkt auf der Kennlinie der Abstützkraft, beispielsweise abhängig von dem speziellen Anwendungsfall einstellen zu können, ist in einer bevorzugten Weiterbildung der zuletzt genannten Ausführungsform vorgesehen, dass das als Zugfeder ausgebildete mindestens eine Federelement zwischen einem ersten und einem zweiten Widerlager angeordnet ist, wobei der Abstand zwischen dem ersten und dem zweiten Widerlager einstellbar ist, und wobei das als Zugfeder ausgebildete mindestens eine Federelement bei maximalen Abstand zwischen dem ersten und zweiten Widerlager bereits in einem vorgespannten Zustand vorliegt, wenn keine externe Kraft in vertikaler Richtung auf die Abstützung einwirkt.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 einer anderen vorteilhaften Realisierung der bei der erfindungsgemäßen Abstützvorrichtung zum Einsatz kommenden Kraftübertragungsmechanik ist vorgesehen, dass diese mindestens eine Doppel-Scherenanordnung bestehend aus einer ersten und einer zweiten Schere aufweist, wobei - wie auch bei der zuvor angegebenen Ausführungsform - jede Schere der Doppel-Scherenanordnung zwei gleichlange Schenkel umfasst, die um eine durch die Mittelpunkte der beiden Schenkel verlaufende gemeinsame horizontale Achse relativ zueinander bewegbar sind, wobei jeweils ein erster Schenkel einer jeden Schere der Doppel-Scherenanordnung über ein Festlager mit der Abstützung und über ein Loslager mit der Halterung und ein zweiter Schenkel einer jeden Schere der Doppel-Scherenanordnung über ein Festlager mit der Halterung und über ein Loslager mit der Abstützung verbunden ist. Im Unterschied zu der zuvor diskutierten Ausführungsform ist nun allerdings das mindestens eine Federelement als Druckfeder ausgebildet und zwischen einem ersten Bolzen, welcher auf der horizontalen Achse liegt, um welche die Schenkel der ersten Schere der Doppelschereanordnung relativ zueinander bewegbar sind, und einem Widerlager angeordnet ist, wobei dieses Widerlager über eine Zugstange mit einem zweiten Bolzen verbunden ist, welcher auf der horizontalen Achse liegt, um welche die Schenkel der zweiten Schere der Doppel-Scherenanordnung relativ zueinander bewegbar sind.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.
Vorzugsweise sind dabei der erste Bolzen mit den Schenkeln der ersten Schere der Doppel-Scherenanordnung und der zweite Bolzen mit den Schenkeln der zweiten Schere der Doppelschereanordnung derart verbunden, dass die entsprechenden Schenkel relativ zu den Bolzen drehbar sind.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 einer bevorzugten Realisierung der zuletzt genannten Ausführungsform ist vorgesehen, dass das mindestens eine Federelement als Druckfederring ausgebildet ist, durch welches sich die Zugstangen zumindest bereichsweise erstreckt, wobei das Widerlager ein an einem ersten Endbereich der Zugstange angeordnetes erstes Konterelement, insbesondere Mutter, und ein an einem gegenüberliegenden zweiten Endbereich angeordnetes zweites Konterelement, insbesondere Mutter, aufweist. Das mindestens eine als Druckfederring ausgebildete Federelement ist dabei zwischen dem ersten Konterelement und dem ersten Bolzen eingespannt. In vorteilhafter Weise ist dabei vorgesehen, dass der Abstand zwischen dem ersten Konterelement und dem zweiten Konterelement variabel ist, um eine Vorspannung des mindestens einen Federelements und somit den Arbeitspunkt der Abstützung einstellen zu können.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.
Noch bevorzugter ist bei der zuletzt genannten Ausführungsform vorgesehen, dass der Federmechanismus mindestens ein erstes und ein zweites Federelement aufweist, welche jeweils als Druckfederring ausgebildet sind, wobei das mindestens eine erste Federelement zwischen dem ersten Konterelement und dem ersten Bolzen und das mindestens eine zweite Federelement zwischen dem zweiten Konterelement und dem zweiten Bolzen angeordnet sind.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.
Denkbar hierbei ist es, dass das mindestens eine erste Federelement in einem mit dem ersten Bolzen verbundenen ersten Federgehäuse aufgenommen ist, und dass das mindestens eine zweite Federelement in einem mit dem zweiten Bolzen verbundenen zweiten Federgehäuse aufgenommen ist. Diese Federgehäuse übernehmen gleichzeitig eine Führung der entsprechend aufgenommenen Federelemente.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.
Schließlich ist es bevorzugt, wenn die Halterung der Abstützvorrichtung einen Flanschbereich aufweist, über den die Abstützvorrichtung mit dem Wagenkastenuntergestell des Fahrzeuges vorzugsweise lösbar befestigt werden kann. Demnach eignet sich die Abstützvorrichtung für ein nachträgliches Umrüsten, was beispielsweise dann der Fall ist, wenn eine üblicherweise zwischen zwei Wagenkästen eines mehrgliedrigen Schienenfahrzeuges angeordnete Kurzkupplung getrennt und die einzelnen Wagenkästen abgeschleppt werden müssen.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.
Nachfolgend werden unter Bezugnahme auf die beigefügten Zeichnungen exemplarische Ausführungsformen der erfindungsgemäßen Lösung beschrieben.Hereinafter, exemplary embodiments of the inventive solution will be described with reference to the accompanying drawings.
Es zeigen:
- 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.
- 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
Demnach kommt zum vertikalen Abstützen der Kupplungsstange 51 bei der herkömmlichen in
Die herkömmliche Konstruktion der Abstützvorrichtung 110 erlaubt es nicht, dass die mit der Abstützvorrichtung 110 auf die Kupplungsstange 51 ausgeübte vertikale Abstützkraft an die Einzelanwendung angepasst werden kann. Insbesondere kann mit der herkömmlichen Abstützvorrichtung 115 keine optimale vertikale Abstützung einer Kupplungsstange 51 bewirkt werden, wenn diese beispielsweise über ein in der Gelenkanordnung 50 integrierte Elastomeranordnung bereits eine vertikale Abstützkraft erfährt. Gleiches gilt auch für Kupplungsstangen 51, welche über ein Sphärolager gelenkig mit dem Wagenkastenuntergestell 60 eines Fahrzeuges verbunden sind.The conventional design of the
Um diesen Nachteil zu beheben, wird erfindungsgemäß vorgeschlagen, die von der Abstützvorrichtung in die abzustützende Kupplungsstange einzuleitende vertikale Abstützkraft durch eine geeignete Mechanik von der Federkennlinie des mindestens einen Federelements der Abstützvorrichtung zu entkoppeln, um so einen für den jeweiligen Anwendungsfall günstigen Kraftverlauf erreichen zu können.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.
Mögliche Realisierungen der erfindungsgemäß vorgeschlagenen Kraftübersetzungsmechanik werden nachfolgend unter Bezugnahme auf die beigefügten Zeichnungen näher beschrieben.Possible implementations of the force transmission mechanism proposed according to the invention are described in more detail below with reference to the accompanying drawings.
Im Einzelnen ist der Darstellung in
Mit der als Elastomer-Federgelenk ausgeführten Anlenkung 50 lassen sich nicht nur die im Fahrbetrieb über die Kupplungsstange 51 übertragenen Zug- und Stoßkräfte abdämpfen, sondern es wird auch eine vertikale Abstützung der Kupplungsstange 51 bewirkt, welche jedoch nicht ausreicht, um die Kupplungsstange 51 im ungekuppelten Zustand in der horizontalen Mittenlängsebene zu halten.With the
Zu diesem Zweck kommt bei dem in den
Die Halterung 2 ist mit einem Flanschbereich 9 verbunden bzw. weist einen Flanschbereich 9 auf (vgl.
Um die mit der Abstützvorrichtung 100 auf die abzustützende Kupplungsstange 51 in vertikaler Richtung V ausgeübte Abstützkraft von der Federkennlinie eines Federelements der Abstützvorrichtung 100 zu entkoppeln, kommt bei der exemplarischen Ausführungsform gemäß den
Wie es nachfolgend unter Bezugnahme auf die Darstellungen in den
Im Einzelnen weist die Kraftübersetzungsmechanik 10 bei der in den
Insbesondere ist bei der in den
Die Federelemente 3a, 3b sind als Druckfederpakete ausgebildet und liegen bei der dargestellten Ausführungsform zwischen einem ersten Bolzen 4 und einem Widerlager. Der erste Bolzen 4 liegt auf der horizontalen Achse H2, um welche die Schenkel 17a, 17b der ersten Schere 15 der Doppel-Scherenanordnung relativ zueinander bewegbar sind. Im Einzelnen ist der erste Bolzen 4 mit den beiden Schenkeln 17a, 17b der ersten Schere 15 derart verbunden, dass die Schenkel 17a, 17b um die horizontale Achse H2 relativ zu dem ersten Bolzen 4 drehbar sind. Hierzu kommt somit wieder ein Festlager zum Einsatz. Das Widerlager ist über eine Zugstange 8 mit einem zweiten Bolzen 5 verbunden, wobei dieser zweite Bolzen 5 auf der horizontalen Achse H3 liegt, um welche die Schenkel 18a, 18b der zweiten Schere 16 der Doppel-Scherenanordnung relativ zueinander bewegbar sind. Im Einzelnen sind die Schenkel 18a, 18b der zweiten Schere 16 über ein Festlager mit dem zweiten Bolzen 5 derart verbunden, dass die Schenkel 18a, 18b um die horizontale Achse H3 drehbar sind.The
Wie es insbesondere der teilgeschnitten perspektivischen Darstellung in
Im Einzelnen sind die als Druckfederringpakete ausgeführten Federelemente 3a, 3b zwischen dem entsprechenden Konterelement 6a, 6b und dem Bodenbereich eines topfförmig ausgeführten Federgehäuses 7a, 7b eingespannt. Die jeweiligen Federgehäuse 7a, 7b sind mit dem ersten Bolzen 4 bzw. dem zweiten Bolzen 5 verbunden.In detail, the
Durch das Vorsehen einer derartigen Kraftübersetzungsmechanik 10 wird eine von der Abstützung 1 bei einer Bewegung relativ zu der Halterung 2 zurückgelegte Wegstrecke in einen Federweg übersetzt, um welchen die beiden Federelemente 3a, 3b bei der Bewegung der Abstützung 1 relativ zu der Halterung 2 elastisch verformt werden. Insbesondere wird eine Kraftübersetzung realisiert, bei welcher die Kennlinie der Abstützkraft von den Federkennlinien der Federelemente 3a, 3 unabhängig ist.By providing such a
In
Demnach nimmt beim Ausüben einer externen Kraft in vertikaler Richtung auf die Abstützung 1 die Abstützkraft zunächst zu und fällt dann nach Erreichen eines Scheitelpunktes nahezu linear ab. Demnach ermöglicht es die Kraftübersetzungsmechanik 10, dass zwischen der Kennlinie der Abstützkraft und den Federkennlinien der Federelemente 3a, 3b ein asynchroner (nicht linearer) Zusammenhang besteht, und zwar derart, dass zumindest in einem Arbeitsbereich der Abstützvorrichtung 100 die Abstützkraft abnimmt, je stärker die Federelemente 3a, 3b der Abstützvorrichtung 100 elastisch verformt werden.Accordingly, when exerting an external force in the vertical direction on the
Die erfindungsgemäße Abstützvorrichtung 100 eignet sich demnach insbesondere zum (temporären) Abstützen einer Kupplungsstange 51 beispielsweise einer Kurzkupplung, wenn diese Kupplungsstange mit einer Elastomer-Federanlenkung 50, wie sie beispielsweise in der Druckschrift
Anschließend lässt sich beispielsweise eine Übergangskupplung an der Kupplungsstange 51 montieren, um ein Abschleppen des Fahrzeuges zu ermöglichen. Die erfindungsgemäße Abstützvorrichtung 100 erlaubt dabei eine vertikale Bewegung der Kupplungsstange 51 relativ zu dem Wagenkastenuntergestell während der Fahrt.Subsequently, for example, a transition coupling can be mounted on the
Die erfindungsgemäße Lösung ist nicht auf die zuvor unter Bezugnahme auf die Darstellungen in den
Im Einzelnen liegt bei der in
Um den Arbeitspunkt der Abstützkraft bei der Abstützvorrichtung 100 gemäß der in
Bei einer weiteren, konstruktiv einfachen Umsetzung der erfindungsgemäßen Lösung kommt als Kraftübersetzungsmechanik 10 eine Scherenanordnung bestehend aus einer Einzel-Schere zum Einsatz, wobei diese Einzel-Schere zwei gleich lange Schenkel aufweist, die um eine durch die Mittelpunkte der beiden Schenkel verlaufende gemeinsame horizontale Achse relativ zueinander bewegbar sind. Jeder Schenkel der Einzelschere ist dabei über ein Festlager mit der Halterung einerseits und über ein Loslager mit der Abstützung andererseits verbunden. Ein als Druckfeder oder Druckfederpaket ausgebildetes Federelement greift dabei an einen ersten Schenkel der beiden gleich langen Schenkel der Einzel-Schere einerseits und an dem entsprechenden zweiten Schenkel der beiden gleich langen Schenkel andererseits an.In a further, structurally simple implementation of the solution according to the invention comes as a
- 11
- Abstützungsupport
- 22
- Halterungbracket
- 3a, b, c3a, b, c
- Federelementspring element
- 44
- erster Bolzenfirst bolt
- 55
- zweiter Bolzensecond bolt
- 6a, 6b6a, 6b
- Konterelementcounter element
- 7a, 7b7a, 7b
- Federgehäusespring housing
- 88th
- Zugstangepull bar
- 99
- Flanschbereichflange
- 1010
- KraftübersetzungsmechanikForce transmission mechanism
- 12a, 12b12a, 12b
- Festlagerfixed bearing
- 13a, 13b13a, 13b
- Loslagermovable bearing
- 15, 1615, 16
- Schere einer Doppel-ScherenanordnungScissors of a double scissors arrangement
- 17a, 17b17a, 17b
-
Schenkel der Schere 15Thighs of the
scissors 15 - 18a, 18b18a, 18b
-
Schenkel der Schere 16Thighs of the
scissors 16 - 19a, 19b19a, 19b
- Festlagerfixed bearing
- 20a, 20b20a, 20b
- Loslagermovable bearing
- 21a, 21b21a, 21b
- Widerlagerabutment
- 5050
- Elastomer-FederanlenkungElastomer spring connection
- 5151
- Kupplungsstangecoupling rod
- 5252
- Grundplattebaseplate
- 5353
- vorderes Elastomer-Federelementfront elastomeric spring element
- 5454
- Federtellerspring plate
- 5555
- hinteres Elastomer-Federelementrear elastomer spring element
- 5656
- Federtellerspring plate
- 6060
- WagenkastenuntergestellCar body underframe
- 100100
- AbstützvorrichtungSupport device
- 110110
- Abstützvorrichtung (Stand der Technik)Support device (prior art)
- 111111
- Träger (Stand der Technik)Carrier (prior art)
- 112112
- Abstützung (Stand der Technik)Support (prior art)
- 113113
- Abstützstempel (Stand der Technik)Abstützstempel (prior art)
- 114114
- Halterung (Stand der Technik)Bracket (prior art)
- 115115
- Federelement (Stand der Technik)Spring element (prior art)
- VV
- vertikale Richtungvertical direction
- H2, H3H2, H3
- horizontale Achsehorizontal axis
Claims (15)
- 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. - 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). - 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. - The support device (100) according to claim 3,
wherein a pretensioning of the at least one spring element is adjustable. - 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. - 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. - 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). - 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. - 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). - 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). - 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). - 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). - 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. - 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. - 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.
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP11178426.0A EP2562062B1 (en) | 2011-08-23 | 2011-08-23 | Support device for vertical support of a coupling rod jointed to a vehicle subframe of a rail-bound vehicle |
US13/557,364 US8534475B2 (en) | 2011-08-23 | 2012-07-25 | Supporting device for vertically supporting a coupling rod articulated to the car body underframe of a rail-borne vehicle |
RU2012136030/11A RU2602267C2 (en) | 2011-08-23 | 2012-10-23 | Support device for holding vertical position of coupling rod articulated with car body bottom frame of rail vehicle |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP11178426.0A EP2562062B1 (en) | 2011-08-23 | 2011-08-23 | Support device for vertical support of a coupling rod jointed to a vehicle subframe of a rail-bound vehicle |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2562062A1 EP2562062A1 (en) | 2013-02-27 |
EP2562062B1 true EP2562062B1 (en) | 2017-01-18 |
Family
ID=44785239
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP11178426.0A Not-in-force EP2562062B1 (en) | 2011-08-23 | 2011-08-23 | Support device for vertical support of a coupling rod jointed to a vehicle subframe of a rail-bound vehicle |
Country Status (3)
Country | Link |
---|---|
US (1) | US8534475B2 (en) |
EP (1) | EP2562062B1 (en) |
RU (1) | RU2602267C2 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
RU191553U1 (en) * | 2019-04-08 | 2019-08-12 | Закрытое акционерное общество "Ресурс" | CENTERING DEVICE FOLDING FOR TRAINING RAILWAY VEHICLE |
Families Citing this family (4)
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CN104121316B (en) * | 2014-06-17 | 2017-08-25 | 安庆市昕臆汽车配件有限公司 | A kind of damper |
US9701323B2 (en) | 2015-04-06 | 2017-07-11 | Bedloe Industries Llc | Railcar coupler |
DE102018210385A1 (en) * | 2018-06-26 | 2020-01-02 | Siemens Aktiengesellschaft | Carrying device for transmitting a force acting on a coupling element to a track-bound vehicle |
RU2756118C1 (en) | 2018-07-30 | 2021-09-28 | Сименс Мобилити Гмбх | Coupling support for the middle buffer coupling of a rail vehicle |
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BE372816A (en) * | 1930-11-06 | |||
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DE1530201A1 (en) * | 1966-03-26 | 1970-07-02 | Mini Verkehrswesen | Device for the support and all-round center reset of automatic couplings, especially for central buffer couplings on rail vehicles |
US3417876A (en) * | 1966-08-12 | 1968-12-24 | Pullman Inc | Coupler carrier |
CH437410A (en) * | 1966-09-21 | 1967-06-15 | Ringfeder Gmbh | Device for supporting and centering the coupling head and coupling arm with central buffer couplings |
US4105128A (en) * | 1976-08-16 | 1978-08-08 | Buckeye International, Inc. | Wear surface arrangement for coupler carrier assembly |
US4344541A (en) * | 1977-08-26 | 1982-08-17 | Holland Company | Coupler carrier arrangement for railroad cars |
US4376488A (en) * | 1979-06-29 | 1983-03-15 | Amsted Industries Incorporated | Railway coupler carrier assembly |
US4445618A (en) * | 1981-12-30 | 1984-05-01 | Midland-Ross Corporation | Spring biased rotary railway car coupler carrier |
US4706826A (en) * | 1985-04-22 | 1987-11-17 | Mcconway & Torley Corporation | Striker carrier having an adjustable wear plate for a railway coupler |
DE19947829A1 (en) * | 1999-07-20 | 2001-02-01 | Knorr Bremse Systeme | Automatic coupling for rail vehicles, especially automatic train coupling |
EP1785329B1 (en) | 2005-11-15 | 2008-04-02 | Voith Turbo Scharfenberg GmbH & Co. KG | Joint structure |
US7837046B2 (en) * | 2006-09-15 | 2010-11-23 | Holland, L.P. | Coupler carrier with improved lug structure for railroad cars |
EP2093123B1 (en) * | 2008-02-25 | 2010-09-01 | Voith Patent GmbH | Support device for vertical support of a coupling bar and usage of the support device in a railway vehicle |
-
2011
- 2011-08-23 EP EP11178426.0A patent/EP2562062B1/en not_active Not-in-force
-
2012
- 2012-07-25 US US13/557,364 patent/US8534475B2/en active Active
- 2012-10-23 RU RU2012136030/11A patent/RU2602267C2/en active
Non-Patent Citations (1)
Title |
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None * |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
RU191553U1 (en) * | 2019-04-08 | 2019-08-12 | Закрытое акционерное общество "Ресурс" | CENTERING DEVICE FOLDING FOR TRAINING RAILWAY VEHICLE |
Also Published As
Publication number | Publication date |
---|---|
RU2012136030A (en) | 2014-04-27 |
US8534475B2 (en) | 2013-09-17 |
US20130048589A1 (en) | 2013-02-28 |
EP2562062A1 (en) | 2013-02-27 |
RU2602267C2 (en) | 2016-11-10 |
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