Device with a traction and buffing device of a coupling system for a railway vehicle

Abstract

A device (10) with a pulling and pushing device of a coupling system for a rail vehicle is provided with an outer casing (12) receiving a coupling flange (13) and having a stop element (24) arranged therein. Furthermore, the device (10) comprises a drawbar (22) mounted in the stop element so as to be displaceable in the axial direction (A), a connecting head (15) connected to the drawbar (22), and, between the connecting head and the stop element (24), preferably a plurality of spring elements (23) arranged in a row on the drawbar (22).The connecting head (15) is displaceably guided over a stroke (h) extending in the elastic region of the spring elements (23). It comprises an absorption means (30) that interacts with an absorption means (33) on the outer casing (12) in such a way that, upon impact with a defined impact force, the connecting head (15) engages with the outer casing (12) after the stroke (h) in an energy-absorbing manner. This allows the device to be provided with a short overall length.

Description

[0001] The invention relates to a device with a pulling and pushing device of a coupling system for a rail vehicle, which is provided with an outer casing accommodating a coupling flange and a stop element arranged therein. Furthermore, a drawbar mounted in the stop element so as to be displaceable in the axial direction, a connecting head connected to the drawbar, and between the connecting head and the stop element, preferably several spring elements arranged in a row on the drawbar, are provided, according to the preamble of claim 1.

[0002] A coupling device for a rail vehicle according to EP 3 205 551 B1 is provided with at least one coupling half with a coupling flange and a tubular section. A coupling part with a hub is held therein, forming a passive safety device. For this purpose, the tubular section is provided on the inside with a diameter extension that accommodates this hub. In the event of an impact with an impact force, this hub of the coupling part is slidably guided within the tubular section, absorbing energy. The tubular end of the tubular section can be fastened to the coupling flange by a detachable connection. In the event of an impact, the hub penetrating the tubular section causes the tubular section to expand in the area of ​​plastic deformation, with the hub sliding against the inside of the tubular section with an approximately uniform frictional force.However, this coupling device does not have an integrated pulling and pushing device with an elastic spring area.

[0003] The invention is based on the object of creating a device of a coupling system for a rail vehicle, which is provided with a compact design in which a pulling and pushing device and a passive energy absorption are integrated, which enables conversion into deformation energy in the event of an impact with a defined impact force.

[0004] The object is achieved according to the invention by the features of claim 1.

[0005] According to the invention, in the device, the connecting head is displaceably guided over a stroke extending in the elastic region of the spring elements and is provided with an absorption means which interacts with an absorption means on the outer casing of the device in such a way that, in the event of an impact with a defined impact force, the connecting head engages with the outer casing in an energy-absorbing manner after the stroke in the elastic region.

[0006] The outer casing is very advantageously arranged around the spring elements. It encompasses the spring elements arranged between the connecting head and the stop element at its narrowed diameter and the subsequent narrowed inner diameter.

[0007] This allows the device to be provided with a short overall length, in which both an elastic area made possible by the spring elements and also this passive energy absorption are integrated, without the need for an additional piece of pipe as in the known coupling device.

[0008] These corresponding absorption means are very advantageously formed by a cone at the connecting head and a diameter constriction formed on the inside of the outer shell facing this cone, whereby the cone engages at this diameter constriction in the event of an impact after this stroke and causes the energy-absorbing plastic diameter expansion of the outer shell when displaced by the impact.

[0009] The stop element of the spring elements is conveniently held by a shearing device on the outer casing in such a way that the shearing device releases automatically upon a defined impact force, and the stop element is pushed through the outer casing by the connecting head, together with the spring elements and the tension rod, and out of it. This defined impact force arises when, for example, two trains collide in an incident and the spring elements can no longer absorb the resulting impact force, causing the shearing device to shear off.

[0010] The invention provides a positioning element extending between the outer casing and the spring elements. On the one hand, the positioning element abuts the shearing element in the axial direction and, on the other hand, is positioned with its opposite end face in such a way that it serves as a stop surface in the axial direction for the connecting head when a certain impact force acts on the connecting head that is less than the defined impact force and does not result in shearing of the shearing element. This positioning element is advantageously tubular and provided with an annular stop surface for the connecting head.

[0011] The invention and further advantages thereof are explained in more detail below using exemplary embodiments with reference to the drawing. It shows: Fig. 1 a longitudinal section of a device according to the invention with a pulling and pushing device of a coupling system; Fig. 2 a perspective side view of the device according to Fig. 1 ; and Fig. 3 a cross-section of the device according to Fig. 1 along line III - III according to Fig. 1 .

[0012] Fig. 1 bis Fig. 3 show a device 10 with a pulling and pushing device 20 of a coupling system (not shown in detail) for a rail vehicle. It is suitable for various vehicles, such as passenger cars, freight cars, or similar transport vehicles, but is particularly advantageous for locomotives where simple, compact coupling systems are practical.

[0013] The device 10 has a hub-shaped, protruding coupling flange 13 on the outside, which can be fastened, for example, in a vehicle body of the rail vehicle (not shown in detail). Instead of the coupling flange, a housing structure enclosing the device could also be provided, which could be clamped in the vehicle body. For assembly purposes, the coupling flange 13 is designed with a two-part or multi-part hub 11 and with a clamping sleeve 14 holding the hub. This clamping sleeve 14 preferably has several, for example eight, bushings 16 on its outer circumference aligned parallel to one another in the axial direction A, into which screws can be inserted, which can be connected on the one hand in the vehicle body and on the other hand to the hub 11 (not shown in detail). In this way, the device 10 can be fastened in the vehicle in a rigid arrangement.

[0014] A tubular or other-shaped outer casing 12 extends from the coupling flange 13 to the rear side 10' of the device. In the assembled state, it is clamped between the bracing sleeve 14 and the hub 11 by a hub-shaped or other-shaped retaining element 12'. Therefore, the hub 11 is constructed in two or more parts so that it can be radially fitted onto the outer casing 12. However, the hub could also be constructed in one piece if the outer casing were dimensioned with a smaller outer diameter than the inner diameter of the hub.

[0015] A connecting head 15 is guided in the bracing sleeve 14 of the coupling flange 13 for reciprocating movement in the axial direction A. In the unloaded initial state, a joint fork 19 with a coupling pin 21 protrudes from the bracing sleeve 14, to which a coupling head, a connecting link, or the like can be connected. This connecting head 15 with the joint fork 19 is connected to the tie rod 22 extending through the outer casing 12. Furthermore, keys 17 are included between the bracing sleeve 14 and the connecting head 15 as anti-twist devices, although these could also be omitted. Furthermore, a foot support 18 for supporting the device 10 is assigned to the underside of the bracing sleeve 14.

[0016] Spring elements 23 are arranged in a row on the pull rod 22 and can be compressed in a reversibly elastic range when subjected to an impact force. The number of spring elements 23 can be varied depending on the requirements for the forces to be absorbed. For example, nine of them can be installed as shown. They are arranged in a row, preferably pre-tensioned, between the connecting head 15 and a stop element 24. The disc-shaped stop element 24, which supports the pull rod 22, is pressed against the spring elements 23 by a driver 26 detachably attached to the pull rod 22 and has a flange 26' that can be fixed by a locking screw 28 as an optional variant of a fastening means. This design of the stop of the spring elements can, of course, be provided differently than shown.

[0017] According to the invention, the connecting head 15 is guided at least partially in the outer casing 12 over a stroke h extending in the elastic region of the spring elements 23, wherein it has an absorption means 30 which interacts with an absorption means 33 of the outer casing 12 in such a way that, in the event of an impact with a defined impact force after the stroke h, the connecting head 15 engages with the outer casing 12 in an energy-absorbing manner and plastically deforms it.

[0018] Such a defined minimum impact force arises when, for example, two trains collide in an unforeseen event and the spring elements can no longer absorb the resulting impact force in the elastic range, which is several times the respective impact force that occurs during a normal train journey.

[0019] The invention is characterized in that the outer jacket, during its diameter constriction and the subsequent narrowed inner diameter 34, surrounds the spring elements 23 arranged between the connecting head 15 and the stop element 24 on their outer sides or that the spring elements 23 are arranged in the outer jacket 12 with the passive absorption means.

[0020] These corresponding absorption means 30, 33 are formed by a cone on the connecting head 15 and a diameter constriction provided on the inside of the outer casing 12 facing said cone. The cone is tapered toward the constriction. The cone is formed on the outside of a longitudinally movable sliding disc 31 assigned to the connecting head 15, and this diameter constriction is formed on the inside of the outer casing 12 with a similar contour. The cones extend relative to one another in such a way that mutual support is achieved in the event of an impact, thus evenly distributing the compressive force from the cone around the diameter constriction.

[0021] The connecting head 15 is guided in the bracing sleeve 14 of the coupling flange 13 and, with its sliding disk 31 in the outer casing 12, is displaceably guided in both directions over the stroke h extending in the elastic range of the spring elements 23. Firstly, when the connecting head 15 is pushed in the thrust direction into a cavity 32 in the outer casing 12, and secondly, when the drawbar is pulled, and with it a positioning element 35 outside the spring elements is displaceable over this stroke h into the cavity 32. When the connecting head 15 and, with it, the drawbar 22, are pulled, the connecting head moves in the bracing sleeve 14 without the sliding disk 31.

[0022] The outer casing could also extend through the bracing sleeve 14 and be secured to the rear thereof with its retaining element 12'. The coupling flange 13 could also extend to the diameter constriction of the outer casing 12, and the latter could be secured to the coupling flange with its retaining element in front of the constriction.

[0023] The outer casing 12 is provided in the area of ​​the stroke h with an inner diameter D1 that is minimally larger than the outer diameter of the cone. Starting from the diameter constriction up to the rear side 10' of the device 10, the outer casing 12 is advantageously provided with the same narrowed inner diameter D2 on its inner side 34, as is also evident from Fig. 3is visible. However, the inner diameter D2 could also, for example, be continuously larger towards the rear or be dimensioned differently. Likewise, the outer diameter of the outer casing 12 is the same size up to its end 12" and is enlarged at the end due to the shear bolts 29. The outer casing could be provided on the outside with an increasing diameter or with a different diameter instead of being cylindrical.

[0024] When an impact force is applied to the connecting head 15 during normal operation, its cone in the outer casing 12 is preferably guided with little play and with it the pull rod 22 in the outer casing is moved backwards, while the spring elements 23 are compressed by the moving connecting head 15 because they are held stationary at the rear by the stop element 24 or the stop ring 27.

[0025] The force flow in the event of an impact force runs from a coupling head (not shown in detail) or from a rod as a connecting link to the joint fork 19 of the connecting head 15 and from there to the elastically compressible spring elements 23, the stop element 24 and from the fixed outer casing 12 holding this stop element 24 back to the coupling flange 13 fastened to the rail vehicle.

[0026] In contrast, in the case of a tensile force, the force flow runs from the coupling head or the connecting link to the joint fork 19 of the connecting head 15 and from there through a tensile force to the drawbar 22 and the driver 26 at the rear of the drawbar and consequently to the elastically compressible spring elements 23 as a compressive force, from these to the sliding disk 31, which strikes the outside with its end face 38 facing the connecting head against the bracing sleeve 14 of the coupling flange 13 and thus the compressive force is absorbed by the rail vehicle.

[0027] For this purpose, the sliding disc 31 is guided longitudinally displaceably on the pull rod 22 because, with this tensile force, the connecting head 15, which is movably guided within the bracing sleeve 14 of the coupling flange 13, is pulled with the pull rod 22 to the left with respect to the image area, i.e. away from the spring elements 23, while the sliding disc 31 strikes with its end face 38 against the bracing sleeve 14 and does not move with the connecting head 15, but rather a distance forms between them in the axial direction A, depending on the strength of the tensile force. In the unloaded initial state, the sliding disc 31 strikes with its end face 38 against the bracing sleeve 14 or elsewhere on the coupling flange 13.

[0028] Upon impact of the cone of the sliding disk 31, which engages this diameter constriction of the outer shell 12 after the stroke h, the impact energy causes the energy-absorbing plastic diameter expansion of the outer shell 12, which can occur from the diameter constriction to the rear side 10'. The sliding disk 31 and the outer shell 12 are advantageously manufactured from a material such that a certain sliding ability is present during expansion, so that the two materials do not weld together.

[0029] The stop element 24 for the spring elements 23 is held in the axial direction A by a shearing element 25 in the outer casing 12. This shearing element 25 consists of a stop ring 27 arranged within the outer casing 12 at its end 12" and preferably a plurality of shearing bolts 29 which are inserted on the circumference of the end 12" of the outer casing 12 and engage radially in the stop ring 27, so that they connect the outer casing to the stop ring.

[0030] In the event of an impact, the shearing device 25 is automatically released at the defined minimum impact force by shearing off the shear pins 29. This causes the stop ring 27 and, with it, the stop element 24 from the connecting head 15, together with the spring elements 23 and the tension rod 22, to be pushed through the outer casing 12 and, if necessary, out of it. This depends on the strength and duration of the impact force. Based on empirical values, the number and diameter of the shear pins 29, as well as the wall thickness and the degree of diameter constriction of the outer casing 12, and thus the resistance to plastic deformation, are determined accordingly. This shearing device could also be configured with just one shear pin and in a different design than shown.

[0031] The sliding disc 31 with the cone as absorption means 30 of the connecting head 15, the spring elements 23, the stop element 24, and the stop ring 27 of the shearing element 25 are surrounded or held by the outer casing 12. The outer casing 12 forms a cavity 32 between the connecting head 15 and the stop element 24, in which the pull rod 22 and the several spring elements 23 arranged in a row on it are arranged.

[0032] Within the scope of the invention, a positioning element 35 is arranged which extends between the outer casing 12 and the spring elements 23. On the one hand, said positioning element abuts the stop ring 27 of the shearing element 25 and, on the other hand, is positioned with its opposite end face such that it serves as an abutment surface 36 in the axial direction A for the connecting head 15 when an impact force acts on it which is less than the impact force and does not lead to shearing of the shearing element 25 or is absorbed by the reversible elasticity of the spring elements 23. This abutment surface 36 of the positioning element 35 is located in front of the diameter constriction of the outer casing 12 so that the cone of the connecting head 15 does not come into contact with this diameter constriction in the event of an impact force less than the impact force, but instead strikes this positioning element 35 if necessary.

[0033] Preferably, this positioning element 35 is tubular and adjoins the stop ring 27 of the shearing element 25 at the rear, so that in the event of an impact by the connecting head 15, it strikes the stop ring 27 and the shearing element 25 is automatically released from the outer casing 12 by the impact force, and the energy absorption takes place through the plastic deformation of the outer casing 12 generated by the absorption means 30, 33. In addition, this positioning element 35 is fixed by one or more pins 37 or the like on the outside of the stop element 24 in the axial direction A. However, it could also be designed without pins.

[0034] This positioning element could, of course, also be constructed from one or more axially extending rods, segments, a cage, or something similar, instead of a tube. A simpler solution could even omit this element. The cone would then come into contact with the outer casing in the event of a larger impact force when the diameter of the outer casing narrows, but the shearing element would not detach, as long as the impact force does not reach the magnitude of an impact force.

[0035] These corresponding absorption means could also be designed differently than shown. For example, the mutual contact surfaces could be shaped differently than conical annular surfaces, such as with rounded, stepped, or differently shaped tapers in cross-section.

[0036] In principle, the outer shell could be extended behind the shearing element to increase the length of the plastic deformation.

Claims

1. Device with a pulling and pushing device of a coupling system for a rail vehicle, which is provided with an outer casing (12) receiving a coupling flange (13) with a stop element (24) arranged therein, a drawbar (22) mounted displaceably in the axial direction (A) in the stop element, a connecting head (15) connected to the drawbar (22) and between the latter and the stop element (24) with preferably several spring elements (23) arranged one after the other on the drawbar (22), characterized in that the connecting head (15) is displaceably guided over a stroke (h) extending in the elastic region of the spring elements (23), wherein it has an absorption means (30) which interacts with an absorption means (33) on the outer casing (12) in such a way that the connecting head (15) engages with the outer casing (12) in an energy-absorbing manner in the event of an impact with a defined impact force after the stroke (h).

2. Device according to claim 1, characterized in that the outer casing (12) surrounds the spring elements (23) arranged in a row between the connecting head (15) and the stop element on their outer sides when its diameter is narrowed and the inner diameter (34) is subsequently narrowed.

3. Device according to claim 1 or 2, characterized in that these corresponding absorption means (30, 33) are formed by a cone on the connecting head (15) and a diameter constriction provided on the inside of the outer casing (12) facing the latter, wherein the cone engages at this diameter constriction (12) in the event of an impact after this stroke (h) and the energy-absorbing diameter expansion of the outer casing (12) is brought about during displacement by the impact energy.

4. Device according to one of claims 1 to 3, characterized in thatthe stop element (24) of the spring elements (23) is held by a shearing member (25) on the outer casing (12) in such a way that the shearing member (25) is automatically released at the defined impact force and the stop element (24) can be pushed by the connecting head (15) together with the spring elements (23) and the pull rod (22) through the outer casing (12) and out of it.

5. Device according to one of claims 1 to 4, characterized in that the cone of the connecting head (15), the spring elements (23), the stop element (24) and the shearing member (25) are surrounded or held by the outer casing (12), wherein the outer casing (12) forms a cavity (32) between the connecting head (15) and the stop element (24), in which cavity the pull rod (22) and preferably a plurality of spring elements (23) arranged one after the other on the latter are arranged.

6. Device according to one of claims 1 to 5, characterized in thata positioning element (35) extending between the outer casing (12) and the spring elements (23) is arranged, which, viewed in the axial direction, on the one hand abuts the stop element (24) or the shearing element (25) and, on the other hand, is positioned with its opposite abutting surface (36) in such a way that it serves as a stop surface in the axial direction (A) for the connecting head (15) when an impact force acts on it which is, however, lower than the impact force and does not lead to shearing off the shearing element (25).

7. Device according to claim 6, characterized in that this abutting surface (36) of the positioning element (35) is located in front of the diameter constriction of the outer casing (15) so that the cone of the connecting head (15) does not come into contact with this diameter constriction in the event of an impact force less than the impact force.

8. Device according to claim 6 or 7, characterized in thatthis positioning element (35) is tubular and abuts the stop ring (27) of the shearing element (25) so that when the connecting head (15) impacts the other impact surface (36), the shearing element is automatically released from the outer casing and the energy of the connecting head is absorbed in the diameter constriction by the absorption means.

9. Device according to one of claims 2 to 8, characterized in that the cone at the connecting head (20) and this diameter constriction on the inside of the outer casing (15) run at the same angle in cross-section, so that an annular mutual support is formed in the event of an impact.

10. Device according to one of claims 1 to 9, characterized in thatthe cone is formed as an absorption means (30) by at least one sliding disc (31) which is guided longitudinally displaceably on the tie rod (22) and is assigned to the connecting head (15), wherein the sliding disc (31) abuts the coupling flange (13) with its end face (38) facing the connecting head (15) in the unloaded state.

11. Device according to one of claims 1 to 10, characterized in that the force flow in the event of an impact force runs from a coupling head or a connecting link to the connecting head (15) and from there to the elastically compressible spring elements (23), to the stop element (24) and from the outer casing (12) holding this stop element back to the coupling flange (13) fastened to the rail vehicle.

12. Device according to one of claims 1 to 11, characterized in thatthe force flow in the case of a tensile force from a coupling head or a connecting link to the connecting head (15) and from there through a tensile force to the drawbar (22) and a driver (26) at the rear of the drawbar and consequently to the elastically compressible spring elements (23) as a compressive force and from there to the sliding disc (31) and the coupling flange (13).

13. Device according to claim 12, characterized in that the sliding disc (31) on the outside with its end face (38) facing the connecting head (15) preferably abuts against a bracing sleeve (14) of the coupling flange (13).

14. Device according to one of claims 1 to 13, characterized in that the connecting head (15) is guided displaceably in the bracing sleeve (14) of the coupling flange (13) and together with its sliding disc (31) in the outer casing (12) over the stroke (h) extending in the elastic region of the spring elements (23).

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