DRAWING AND BUFFING DEVICE FOR A DRAW COUPLING AND DRAW COUPLING

Description

[0001] The present invention relates to a pulling and buffing device for a train coupling, in particular a central buffer coupling, and to a train coupling with such a pulling and buffing device.

[0002] A tension and shock device is disclosed, for example, in US 3 031 089 A. This comprises a spring device with a hydraulic displacement damper and with at least one compression spring, wherein according to a first embodiment the hydraulic damper absorbs pressure surges and the compression spring cushions tension surges. According to an alternative embodiment, a second compression spring is provided in the force flow parallel to the hydraulic damper and parallel to the first compression spring, which cushions pressure surges and tension surges. According to a third embodiment, two compression springs are arranged parallel to one another in the force flow, which cushion tension surges, combined with a hydraulic damper that dampens pressure surges. The hydraulic damper comprises an internal return spring, which returns a piston rod of the damper after a pressure surge. The hydraulic damper dampens exclusively pressure surges.

[0003] A disadvantage of the pull and buffer device according to US 3 031 089 A is that it requires considerable axial space and pressure surges are essentially only dampened by the hydraulic damper because the compression spring, which may be arranged in parallel, has a comparatively small spring stroke. Since the damping effect of the hydraulic damper is mass and speed dependent, there is hardly any damping in the first and third embodiments at low speeds. The pull and buffer device will always buffer the full stroke in the compression direction under quasi-static load, which is associated with corresponding mechanical stresses. Furthermore, there are hard metallic stops during a load change, which lead to noise and wear. Furthermore, various stop surfaces arranged one behind the other at a distance must be aligned with one another to ensure proper function.The installation of the drawbar and buffer system is therefore complex. A failure of the hydraulic damper quickly leads to a complete failure of the drawbar and buffer system.

[0004] EP 2305531 A1 discloses an embodiment according to the preamble of claim 1 with parallel arranged spring device and hydraulic damping device, in which the spring devices are effective in both compression and tension directions.

[0005] A traction coupling in which springs are combined with a friction damper is known, for example, from WO 2007 / 103087 A1.

[0006] US 3 556 311 A discloses the combination of rubber buffers with an air damper.

[0007] US 3 854 596 A discloses the combination of a hydraulic damper and elastomer buffers.

[0008] DE 20 2004 014 532 U1 discloses a spring mechanism installation box with a spring mechanism which is connected on the one hand in an articulated manner to a coupling arm and on the other hand to an installation box which is screwed to a stop plate of the vehicle with screws, wherein compressive forces are transmitted to the pressure stops of the vehicle via a tension-pressure piece, a spring, a rear plate and a housing and tensile forces are transmitted to tension stops via a hinge pin, the housing, the rear plate, the spring and the tension-pressure piece.

[0009] WO 2013 / 040119 A1 discloses the combination of an elastomer part with friction damping for a traction and impact device of a traction coupling. A pressure plate is provided at each end of a stack of elastomer elements, so that compressive forces are transmitted across the entire elastomer stack in both the tensile and compressive directions. The spring travel is therefore identical in both axial directions, and the traction and impact device must be supplemented with spacers or similar when installed in different environments.

[0010] EP 1 225 114 B1 discloses a pulling and buffering device for a central buffer coupling, in which a coupling arm or coupling shaft is supported by a joint on a joint pin. Under tensile load, the coupling shaft transmits the tensile force via the joint pin, an upper chord, a lower chord, an end plate, a tension-side play cushion, a stop plate, and a spring system to a pressure plate, which is supported against vehicle-side tension stops. During compressive load, the coupling shaft transmits the compressive force, via a joint play cushion, without play to the joint pin, which is supported against the pressure plate. The pressure plate compresses the spring system and transmits the compressive forces via the stop plate against the vehicle-side pressure stops.

[0011] WO 2016 / 026708 A1 discloses a pulling and pushing device for a train coupling with a reversible and an irreversible energy-absorbing device. The energy-absorbing device with irreversible energy absorption is connected in series with the reversible energy-absorbing device, whereby the energy-absorbing device with irreversible energy absorption is irreversibly deformed or destroyed if a predefined maximum pulling / pushing force is exceeded.

[0012] EP 1 732 798 B1 discloses a heavy-duty long-stroke friction clutch drawbar assembly for absorbing both trailer and train loads applied to a central sleeper member of a rail vehicle during train formation and track operation of the train formation, comprising a friction clutch mechanism having various pairs of plate members and a wedge member for absorbing thermal energy generated during closure of the friction clutch drawbar assembly.

[0013] US 3 150 782 A discloses a traction and impact device for a traction coupling, in which a hydraulic damper is connected in parallel to a plurality of compression springs in order to cushion traction and impact forces simultaneously with the compression springs and the damper.

[0014] US 3,186,563 A discloses a traction and impact device for a traction coupling, in which a hydraulic damper is arranged parallel to two compression springs, one acting only in the traction direction and the other only in the compression direction. US 3,368,698 A discloses a traction and impact device for a traction coupling, in which a hydraulic damper is arranged parallel to a plurality of compression springs in the force flow, further comprising an additional return spring that engages the damper housing to return the traction and impact device to its initial position.

[0015] US 3,447,693 A discloses a traction and impact device with a hydraulic damper and springs, wherein the hydraulic damper is arranged within a friction damping device parallel to a plurality of compression springs. A compression spring is arranged between a cup-shaped ram and a bottom of the housing forming the damping chamber to urge the ram into its fully extended position.

[0016] The present invention is based on the object of providing a traction and buffer device for a traction coupling that allows for a compact design in favor of a shallow installation depth, preferably dispenses with an internal damper spring return, and particularly preferably has different spring forces and spring strokes in the traction and buffer devices in order to avoid a load change with a zero crossing in one spring. The traction and buffer device should be robustly designed and still exhibit sufficient spring properties in the traction and buffer directions even in the event of a hydraulic damper failure.

[0017] The object of the invention is achieved by a pulling and buffering device for a train coupling, in particular a central buffer coupling, with the features of claim 1. The dependent claims describe advantageous and particularly expedient embodiments of the invention and specify a train coupling according to the invention.

[0018] A pulling and buffering device according to the invention for a train coupling, wherein the train coupling is designed in particular as a central buffer coupling, has a first connection for a coupling shaft, wherein the first connection is designed to transmit tensile forces and compressive forces. Furthermore, a second connection is provided for fastening the pulling and buffering device to a vehicle structure, wherein the second connection is also designed to transmit tensile forces and compressive forces. The second connection is positioned away from the first connection in an axial direction.

[0019] Furthermore, a spring device is provided that transmits tensile and compressive forces between the first connection and the second connection. The spring device comprises a hydraulic damper, which is positioned in the axial direction, in particular, between the first connection and the second connection and / or advantageously forms one of the two connections. The hydraulic damper has a piston displaceable in the axial direction and a piston rod connected to this piston and extending in the axial direction.

[0020] According to the invention, the spring device further comprises two individual compression springs positioned side by side on the piston rod. The two compression springs, although more than two compression springs may be provided, are arranged in the compression direction of the spring device, i.e., in the direction of compressive forces acting on the spring device, parallel to the hydraulic damper and in series with one another in the force flow. Furthermore, the two individual compression springs are supported against one another in the axial direction. Preferably, a plate, referred to here as an intermediate plate, can be arranged between the two compression springs, via which the two springs are supported against one another in the compression direction.

[0021] By arranging the two compression springs on the piston rod of the hydraulic damper and connecting them in parallel with the hydraulic damper to absorb or dampen pressure surges, a very compact design of the tension and shock device in the axial direction can be achieved. Furthermore, the tension and shock device provides a large spring stroke even if the hydraulic damper fails, ensuring reliable cushioning of pressure surges. The arrangement of two compression springs arranged one behind the other on the piston rod provides sufficient damping of pressure surges even under quasi-static compressive forces.

[0022] A further advantage of the arrangement of the two individual compression springs on the piston rod of the hydraulic damper is the stroke limitation and thus overload protection of the two individual compression springs by blocking them when the maximum stroke of the compression springs is reached. According to a preferred embodiment of the invention, the hydraulic damper is designed as a displacement damper and can, for example, displace a damping fluid via at least one throttle point when the piston rod is compressed, thereby exerting a corresponding braking effect on the piston rod. For example, the piston can have at least one such throttle point. Additionally or alternatively, a throttle point can also be provided in another component of the damper.

[0023] The hydraulic damper preferably has two damping chambers which are fluidically connected to one another via the at least one throttle point and which are separated from one another by the piston. As a result, when the piston rod is retracted and the piston is displaced, the volume of the first damping chamber can be reduced and the volume of the second damping chamber can be increased, with the fluid simultaneously flowing from the first damping chamber via the at least one throttle point into the second damping chamber. Measures can be provided which essentially prevent damping when the piston rod is extended and thus when the first damping chamber is enlarged and the second damping chamber is reduced, for example by providing an additional fluid-conducting connection to a compensation chamber on the second damping chamber, so that the fluid can be at least partially displaced into the compensation chamber when the piston rod is extended.In such a case, the hydraulic damper only acts when compressive forces are applied to the spring device, whereas it is essentially ineffective with regard to damping when tensile forces are applied to the spring device.

[0024] The hydraulic damper preferably has a damper housing from which the piston rod protrudes and into which the piston rod can be more or less inserted, wherein the two compression springs are positioned outside the damper housing in the axial direction next to it. Advantageously, only the insertion of the piston rod is damped. In principle, however, only a damped extension of the piston rod would be possible, or damping during the retraction and extension of the piston rod. The damper housing itself can be free of compression springs and / or other spring elements, so that a return of the piston or piston rod is preferably brought about by at least one of the two individual compression springs on the piston rod.

[0025] In order to reduce vibration behavior during load changes, the two compression springs can be integrated into the spring device in such a way that a first compression spring of the two individual compression springs is compressed by tensile forces and compressive forces on the spring device, whereas the second of the two individual compression springs is only compressed by compressive forces on the spring device and does not contribute to spring damping in the case of tensile forces and / or is not arranged in the force flow.

[0026] According to a preferred embodiment, an intermediate plate is arranged between the two compression springs. This intermediate plate is connected to the first connection in a tension-resistant manner and has opposing contact surfaces for the two compression springs. This ensures that both springs act jointly in the compression direction on the spring device, and only one compression spring acts when the spring device is subjected to tensile stress.

[0027] Particularly preferably, a housing is provided which accommodates the two compression springs and in particular also the intermediate plate. The housing can, for example, have an upper flange and a lower flange which are suitably connected to one another, for example via side plates, in particular each in the form of a sheet metal plate. The housing forms the first connection, in particular in the form of a receptacle for a coupling shaft bolt, and accommodates a first pressure plate which is displaceable in the axial direction, wherein the first pressure plate comprises a first contact surface for the first of the two compression springs and in particular for the piston rod in order to transmit a pressure force via this first contact surface. In particular, the first pressure plate is guided in the housing by means of a linear guide.

[0028] The intermediate plate can be arranged in a fixed position in the housing in order to be able to transmit tensile forces to the intermediate plate via the housing.

[0029] A train coupling according to the invention, in particular a central buffer coupling, has a coupling shaft that can be pivoted about a vertical axis, as well as a pulling and buffing device of the type shown here. The first connection is formed by a receptacle for the coupling shaft bolt or by the coupling shaft bolt itself, with which the coupling shaft is pivotably connected to the pulling and buffing device. Preferably, the coupling shaft has an at least substantially flat contact surface at its free end, and a second contact surface of the first pressure plate rests freely against the contact surface of the coupling shaft when the first pressure plate is subjected to a compressive force by the spring device.

[0030] The contact of the first pressure plate with the contact surface of the clutch shaft is preferably tiltable, so that the first pressure plate is rotatable relative to the clutch shaft. For example, the clutch shaft is rotatable about the clutch shaft bolt relative to the first pressure plate. Because two at least substantially flat contact surfaces of the first pressure plate and the clutch shaft abut one another in the pressure direction, preloaded by the spring device, the two at least substantially flat contact surfaces tilt relative to one another when the clutch shaft is deflected from its central position, resulting in a restoring moment that acts to return the clutch shaft to its central position, i.e., to the fully axially aligned position.The pressurised but free contact of the two at least substantially flat surfaces and the possibility of tilting the two at least substantially flat surfaces relative to each other thus represents a centre reset integrated into the pulling and pushing device.

[0031] The traction and buffer device according to the invention can preferably be applied to a vehicle undercarriage with only one stop each in the traction and compression directions. The installation of the traction and buffer device between the two stops is preferably free of play. After installation of the traction and buffer device in the traction coupling and between the stops in the vehicle undercarriage, the two compression springs can be preloaded to ensure free of play.

[0032] The pulling and pushing device according to the invention can be free of tie rods, i.e. screw connections that extend in the axial direction and that are loaded by the tensile forces or compressive forces transmitted by the pulling and pushing device.

[0033] The inventive pull and push device allows for large spring strokes, for example, of more than 100 mm, 130 mm, or 150 mm or more, even with small compressive forces. This allows for high energy absorption in the pull and push device at low acceleration.

[0034] The invention will be described below by way of example using embodiments and the figures.

[0035] They show: Figure 1 shows a train coupling according to the invention with a pulling and buffing device according to the invention in a schematic three-dimensional view; Figure 2 shows the train coupling from the Figure 1in a side view; Figure 3 the train coupling from the Figure 1 in a plan view; Figure 4 shows a further embodiment of a traction coupling with a traction and buffer device according to the invention; Figure 5 shows an embodiment of a hydraulic damper.

[0036] In the Figure 1 An embodiment of a pulling and pushing device according to the invention in the form of a long-stroke spring mechanism in a pulling coupling is shown. The pulling coupling comprises a coupling shaft 3, which in its central position extends along an axial direction of the pulling and pushing device and is pivotable about a vertical axis 15 that runs centrally through the coupling shaft bolt 14, and the pulling and pushing device, which has a first connection 1 for transmitting tensile and compressive forces, wherein the first connection 1 is formed by a receptacle 13 for the coupling shaft bolt 14 in a housing 12 or the coupling shaft bolt 14 itself.

[0037] The housing 12 of the pulling and buffing device comprises an upper chord 18 and a lower chord 19, which are connected to each other via side parts, here in the form of a sheet metal plate 20 screwed to the upper chord 18 and lower chord 19. This allows for a weight-optimized housing 12 to be achieved, which can be manufactured using sheet metal parts.

[0038] The housing 12 has a linear guide 11 for a first pressure plate 7, which is displaceable in the linear guide 11 along the axial direction in the housing 12. The first pressure plate 7 comprises an axially directed contact surface, referred to herein as the second contact surface 7.2. With this second contact surface 7.2, which is at least substantially flat, the first pressure plate 7 rests freely and tiltably against a likewise substantially flat contact surface 3.1 of the coupling shaft 3.

[0039] A first contact surface 7.1 of the first pressure plate 7 is directed in the axial direction away from the clutch shaft 3 and is pressurized by the piston rod 6.2 of a hydraulic damper 6 and the first compression spring 5.1. On the axial side facing away from the first pressure plate 7, the first compression spring 5.1 bears against an intermediate plate 8, which is fixedly mounted in the housing 12. On the side facing away from the first compression spring 5.1, a second compression spring 5.2 bears against the intermediate plate 8 and is supported in the axial direction on the damper housing 6.6.

[0040] The first compression spring 5.1 and the second compression spring 5.2 both enclose the piston rod 6.2 of the hydraulic damper 6 and, together with the hydraulic damper 6, form a spring device 4.

[0041] For example, the first compression spring 5.1 and the second compression spring 5.2 are designed as polymer springs. The hydraulic damper 6 is preferably a displacement damper.

[0042] The two compression springs 5.1 and 5.2 act parallel to the hydraulic damper 6 when the traction and impact device is subjected to a compressive force. The contact surface 3.1 of the coupling shaft 3 presses on the second contact surface 7.2 of the first pressure plate 7, which in turn presses via the first contact surface 7.1 on the first compression spring 5.1, which in turn presses via the intermediate plate 8 on the second compression spring 5.2, which in turn presses on the damper housing 6.6, which is supported on a vehicle stop 9 via a central force introduction plate 10, which is in particular spherical. The vehicle stop 9 is provided in particular in the vehicle underframe. At the same time, the first pressure plate 7 presses on the piston rod 6.2 of the hydraulic damper 6, so that the piston rod 6.2 is pushed into the damper housing 6.6.

[0043] The damper housing 6.6 forms a second connection 2 of the pulling and pushing device.

[0044] When subjected to tensile stress, i.e., when a tensile force is applied to the drawbar and pusher device, the coupling shaft 3 pulls on the housing 12 via the coupling shaft bolt 14 and thus on the intermediate plate 8, which exerts a compressive force on the first compression spring 5.1 in the direction of the first pressure plate 7, thereby pressing the first pressure plate 7 against axial vehicle stops 17 in the vehicle undercarriage of the vehicle that has the coupling shaft 3. The vehicle interface 16 is shown in dashed lines in the figures.

[0045] This means that only the first compression spring 5.1 acts in the pulling direction, whereas the second compression spring 5.2 is ineffective, as is the hydraulic damper 6.

[0046] The damper housing 6.6 is supported on the housing 12 in a tensile manner via a recess 21 or a comparable shoulder on the damper, so that the hydraulic damper 6 is also supported by the housing 12 in the tensile direction (left in the Figures 2 and 3) is subjected to a force equal to the preload from spring 5.5 and prevents the spring 5.2 from being released from the installed position.

[0047] Because compression springs 5.1, 5.2 and hydraulic damper 6 act in parallel in the compression direction, quasi-static movements and slow movements in the compression direction can be absorbed by compression springs 5.1, 5.2. At higher speeds in the compression direction, hydraulic damper 6 absorbs the clutch shock thanks to its preferred characteristic curve, featuring a sharply increasing force curve at the beginning of the stroke and a constant force level, along with the progressively increasing energy absorption of compression springs 5.1, 5.2. The combination of damper 6 and compression springs 5.1, 5.2, particularly polymer compression springs, allows for a significant reduction in compressive forces and accelerations. In the retraction direction, however, only the first compression spring 5.1 acts, thus avoiding vibrations caused by load changes.

[0048] The coupling shaft 3 has sufficient axial play in its pin receptacle, for example by providing an elongated hole, so that it can penetrate sufficiently into the housing 12 to compress the compression springs 5.1, 5.2 via the first pressure plate 7 and to insert the piston rod 6.2 of the damper 6. The coupling shaft pin 14 is not loaded in the compression direction.

[0049] In the Figure 4 an embodiment is shown which, except for the design of the housing 12, is identical to the embodiment according to the Figures 1 to 3 In contrast, the housing 12 is composed of a cast or forged upper chord 18 and lower chord 19, which are directly bolted together.

[0050] In the Figure 5 an embodiment of a hydraulic damper is shown, as it is used in the spring device 4 according to the Figures 1 to 3or in other designs according to the invention. The first compression spring 5.1, the second compression spring 5.2 and the intermediate plate 8 are displaceably arranged on the piston rod 6.2. At the free end facing away from the damper housing 6.6, the first pressure plate 7 (not shown here) engages from the Figures 1 to 4 At the end of the piston rod 6.2, which is positioned within the damper housing 6.6, a piston 6.1 is connected, which separates a first damping chamber 6.4 from a second damping chamber 6.5. Since the piston rod 6.2 is shown fully extended from the damper housing 6.6, the volume of the second damping chamber 6.5 approaches zero in this state, whereas the volume of the first damping chamber 6.4 is at its maximum.

[0051] A throttle point 6.3 is provided in the piston 6.1, here in the form of a bore, via which the first damping chamber 6.4 is fluidly connected to the second damping chamber 6.5, so that when the piston 6.1 is moved to reduce the volume of the first damping chamber 6.4, the fluid from the first damping chamber 6.4 must escape via the throttle point 6.3 into the second damping chamber 6.5.

[0052] Furthermore, a compensation chamber 6.8 is provided in the damper housing 6.6, which is connected to the second damping chamber 6.5 via a fluid-conducting connection 6.7. As a result, when the piston rod 6.2 extends from the damper housing 6, fluid can escape from the second damping chamber 6.5 via the fluid-conducting connection 6.7 into the compensation chamber 6.8, thus avoiding or at least substantially reducing damping.

[0053] The damping fluid is preferably oil. List of reference symbols

[0054] 1First connection 2Second connection 3Coupling shaft 3.1Contact surface 4Spring device 5.1First compression spring 5.2Second compression spring 6Hydraulic damper 6.1Piston 6.2Piston rod 6.3Throttle point 6.4Damping chamber 6.5Damping chamber 6.6Damper housing 6.7Fluid-conducting connection 6.8Compensation chamber 7First pressure plate 7.1First contact surface 7.2Second contact surface 8Intermediate plate 9Vehicle stop 10Central force introduction plate 11Linear guide 12Housing 13Receptacle 14Coupling shaft bolt 15Vertical axis 16Vehicle interface 17Vehicle stop 18Upper flange 19Lower flange 20Sheet metal plate 21Recess

Claims

1. Pulling and pushing device for a train coupling, in particular central-buffer coupling, having a first connection (1), transmitting tensile and compressive forces, for a coupling shaft (3); having a second connection (2), transmitting tensile and compressive forces, for fastening the pulling and pushing device to a vehicle structure, the second connection (2) being positioned in an axial direction away from the first connection (1); having a spring device (4), which transmits tensile forces and compressive forces between the first connection (1) and the second connection (2), the spring device (4) comprising a hydraulic damper (6) which has a piston (6.1), which is displaceable in the axial direction, and a piston rod (6.2), which is connected to said piston and extends in the axial direction; the spring device (4) furthermore comprising two individual compression springs (5.1, 5.2) which are positioned next to each other on the piston rod (6.2) and, in the compression direction of the spring device (4), are arranged in series with each other in the force flux parallel to the hydraulic damper (6) so as to support each other, characterized in that a first compression spring (5) of the two individual compression springs (5.1, 5.2) is arranged in such a way that it is compressed by tensile forces and compressive forces on the spring device (4), and a second compression spring (5.2) of the two individual compression springs (5.1, 5.2) is arranged in such a way that it is compressed only by compressive forces on the spring device (4), and in that a housing (12) accommodating the two compression springs (5.1, 5.2) is provided, the housing forming the first connection (1) and receiving and guiding a first pressure plate (7), which is displaceable in the axial direction, the first pressure plate (7) comprising a first contact surface (7.1) for a first compression spring (5.1) of the two individual compression springs (5.1, 5.2) in order to transmit a compressive force.

2. Pulling and pushing device according to Claim 1, characterized in that the hydraulic damper (6) is in the form of a displacement damper.

3. Pulling and pushing device according to Claim 2, characterized in that the damper (6) comprises two damping chambers (6.4, 6.5) which are fluid-conductively connected to each other via at least one throttle point (6.3) and are separated from each other by the piston (6.1).

4. Pulling and pushing device according to Claim 3, characterized in that the damper (6) has a damper housing (6.6), from which the piston rod (6.2) protrudes and into which the piston rod (6.2) is slidable to a greater or lesser extent, wherein the two individual compression springs (5.1, 5.2) are positioned outside the damper housing (6.6) next thereto in the axial direction.

5. Pulling and pushing device according to Claim 4, characterized in that the damper housing (6.6) is free of compression springs and / or other spring elements.

6. Pulling and pushing device according to either of Claims 4 and 5, characterized in that at least one of the two compression springs (5.1, 5.2), in particular a first compression spring (5.1) of the two individual compression springs (5.1, 5.2), exerts a restoring force for extending the piston rod (6.2) out of the damper housing (6.6).

7. Pulling and pushing device according to any one of Claims 1 to 6, characterized in that the hydraulic damper (6) is effective only when compressive forces are applied to the spring device (4).

8. Pulling and pushing device according to any one of Claims 1 to 7, characterized in that an intermediate plate (8) is arranged between the two compression springs (5.1, 5.2), said intermediate plate being connected in a tension-resistant manner to the first connection (1) and having contact surfaces, which face away from each other, for the two compression springs (5.1, 5.2).

9. Pulling and pushing device according to any one of Claims 1 to 8, characterized in that the housing (12) accommodating the two compression springs (5.1, 5.2) and the intermediate plate (8) is provided with an upper flange (18) and a lower flange (19), which forms the first connection (1) in the form of a receptacle (13) for a coupling shaft pin (14) and guides the first pressure plate (7) in a linear guide (11), the first pressure plate (7) comprising a first contact surface (7.1) for a first compression spring (5.1) of the two individual compression springs (5.1, 5.2) and for the piston rod (6.1).

10. Pulling and pushing device according to Claims 8 and 9, characterized in that the intermediate plate (8) is fixed in position in the housing (12).

11. Train coupling, in particular central-buffer coupling, having a coupling shaft (3), which is pivotable about a vertical axis (15), and having a pulling and pushing device according to any one of Claims 1 to 10, wherein the first connection (1) is formed by a receptacle (13) for a coupling shaft pin (14) or the coupling shaft pin (14), with which the coupling shaft (3) is pivotably connected to the pulling and pushing device.

12. Train coupling according to Claim 11, having a pulling and pushing device according to either of Claims 9 and 10, characterized in that the free end of the coupling shaft (3) has an at least substantially flat contact surface (3.1), wherein a second contact surface (7.2) of the first pressure plate (7) lies freely against the contact surface (3.1) of the coupling shaft (3) by being acted upon by the spring device (4) with a compressive force.