WO2017157738A1

WO2017157738A1 - Coupling system having pneumatic deflection

Info

Publication number: WO2017157738A1
Application number: PCT/EP2017/055443
Authority: WO
Inventors: Ralf Schipmann
Original assignee: Voith Patent Gmbh
Priority date: 2016-03-15
Filing date: 2017-03-08
Publication date: 2017-09-21
Also published as: CN108698619B; CN108698619A; EP3429901A1; EP3429901B1; DE102016104740A1

Abstract

The invention relates to a coupling system for a rail vehicle (1), comprising a bearing block (2), which is provided on the rail vehicle (1), a coupling rod (3), which is connected to the vehicle (1) at the first end of the coupling rod by means of an articulated connection (2a), a coupling head (4), which is provided at the second end of the coupling rod (3) facing away from the rail vehicle (1), and an actuator device (5), which is arranged lateral to the coupling rod (3) and is connected to the rail vehicle (1) by means of a fixed bearing (6). The actuator device (5) is provided on one side with respect to the coupling rod (3) and has a pneumatic reciprocating cylinder (10) such that the coupling rod (3) can be deflected in two opposite directions, in particular incrementally, at the second of the coupling rod having the coupling head (4) and the actuator device (5) can be frictionally and/or interlockingly connected to the coupling rod (3).

Description

COUPLING SYSTEM WITH PN EUMATIC HE LIFTING

description

The invention relates to a coupling system for a rail vehicle, in particular for the pneumatic deflection of a central buffer coupling for rail vehicles according to the preamble of the independent patent claim 1.

A system for the deflection of a coupling device is known for example from DE 10 2014 101 986 AI. The coupling device has a connected to the car body actuator. This Stel lglied is designed to deflect the coupling rod, if necessary, from the center position. By the coupling device of two opposing rail vehicles are deflected accordingly, thus an automatic coupling of two rail vehicles, for example, in tight bends possible.

The actuators or actuators necessary for this purpose are carried out according to the prior art primarily as hydraulic systems in order to enable a quick and precise positioning of the coupling head of a rail vehicle with an arbitrary deflection. However, rail vehicles rarely have hydraulic systems. The necessary system components, such. As hydraulic pumps, accumulators and pressure relief valves, must be additionally integrated into the infrastructure of the rail vehicle to allow lateral deflection of the coupling head. Furthermore, the use of hydraulic fluids such as oil is a major risk factor in case of fire. By contrast, the use of pneumatic system solutions requires no additional risk in the operation of a rail vehicle. The compressibility of gaseous working fluids or fluids in this case causes a rapid but sudden movement initiated with undefined force. The positioning of the coupling head during pre-deflection of the coupling rod is therefore difficult to adjust and inaccurate.

The present invention has for its object to provide a coupling system that allows a simple, cost-effective and low-risk integration into a rail vehicle. Furthermore, a fine-stage (pre-) deflection of the coupling head of a coupling device is to be made possible.

This object is achieved by a coupling system according to independent claim 1. Further preferred embodiments are specified in the dependent claims.

According to independent claim 1, the rail vehicle coupling system according to the invention comprises a bearing block disposed on the rail vehicle, a coupling rod connected at its first end to the vehicle via an articulated connection, a coupling head connected to the second end of the rail Coupling rod is arranged, which faces away from the rail vehicle, and an actuator device, which is arranged laterally of the coupling rod. The actuator device is connected to the rail vehicle. Preferably, the connection between actuator device and rail vehicle is designed as a fixed bearing. Advantageously, the actuator device is thus supported against the rail vehicle or its frame or its chassis in order to allow a relative movement of the coupling rod with the coupling head relative to the rail vehicle.

The actuator device according to the invention is arranged on one side with respect to the coupling rod. In this arrangement, there is the advantage that the pivoting range of the coupling rod during deflection, in particular in the lateral direction, is not limited by the actuator device. For the purposes of the present invention, the deflection of the coupling rod is always understood to mean the rotation of the coupling rod about an axis of rotation, so that the coupling head undergoes an appropriate (pre-) deflection and the connection or coupling of two opposing rail vehicles is made possible. For the deflection of the coupling rod with the coupling head, in particular a so-called central buffer coupling, the rotation of the coupling rod always takes place about an axis of rotation which passes through the articulated connection between the coupling rod and rail vehicle or bearing block. If the coupling head is sufficiently deflectable via the coupling rod, two opposing rail vehicles can be coupled to each other on the basis of the gripping area of the central buffer coupling. The deflection of the coupling device is thus to be understood in particular as a pre-deflection, so that the mutual finding of the opposing coupling devices is made possible.

The actuator device has a pneumatic lifting cylinder, so that the coupling rod is deflectable at its second end with the coupling head in two opposite directions. The use of a pneumatic lifting cylinder has the advantage that the fluid or working fluid, in contrast to hydraulic fluids such as oil, no additional risk, for example in case of fire, represents. Rather, media such as air or other gas can be used, which have further advantageous properties. Among other things, a flammable working fluid can be selected to further reduce the risk in the event of fire.

Furthermore, the infrastructure of rail vehicles on pneumatic systems, so no additional components such. As pressure accumulator, pneumatic pumps to provide a compressed working fluid or pressure relief valves, necessary. Rather, the components already integrated in the rail vehicle can also be used to supply the actuator device with working fluid according to the present invention. Thus, the infrastructure or the number of system components, for. B. compared to a hydraulic device for the deflection of the coupling rod can be reduced.

According to the present invention, the coupling rod is deflectable in two opposite directions by means of the actuator device. Thus, per coupling ment device or per coupling rod a single actuator device sufficient to allow the proper use of a rail vehicle. The number of components for the deflection of the coupling rod with the coupling head is reduced. In addition to a reduced probability of failure, a cost-efficient production and maintenance can thus be ensured.

The deflection of the coupling rod by the pneumatic lifting cylinder is particularly gradual. Advantageously, it is thus possible to subdivide a desired deflection of the coupling rod into a plurality of partial movements. As a result, a pneumatic lifting cylinder can be used, which has a smaller maximum stroke. The positioning accuracy of a pneumatic lifting cylinder can be optimized in this way, since the influence of the compressibility of the gaseous working fluid is reduced. The basic disadvantage of a pneumatic lifting cylinder against z. As a hydraulic lifting cylinder can be reduced in the sequence by the use of smaller lifting cylinder. The stepwise deflection of the coupling rod with the coupling head is sufficiently accurate and fast, so that opposing rail vehicles on the basis of the gripping region of the coupling head are connected to each other.

The actuator device can be frictionally and / or positively connected to the coupling rod according to the present invention. A connection between the actuator device and the coupling rod can be permanent. However, the actuator device according to the present invention need not be continuously connected to the coupling rod.

In particular, this is understood to mean that the actuator device in its entirety does not have to be permanently connected to the coupling rod at all times. As required, individual components of the actuator device can be decoupled from the connection with the coupling rod or can be connected to the coupling rod along the force transmission within the actuator device. Based on a non-positive and / or positive connection, therefore, a power transmission can be produced by the actuator device on the coupling rod. Thus, a deflection of the coupling rod can be achieved if necessary. According to an embodiment of the present invention, the lift cylinder has a cylinder housing provided with a first fluid port and a second fluid port. The first and the second fluid connection can be used as fluid inlet and / or fluid outlet. In particular, the lifting cylinder is designed as a double-acting lifting cylinder. Advantageously, with the lifting cylinder, a movement in both directions along the longitudinal axis of the lifting cylinder, if necessary executable. Thus, any position of the lifting cylinder can be approached in controlled or controlled form with high accuracy.

In a further embodiment, the lifting cylinder has a basic position in which a piston head of a piston of the lifting cylinder is in a central position, so that the piston is movable in both axial directions of the lifting cylinder. Advantageously, the basic position of the lifting cylinder represents the state from which a movement of the piston takes place in order to achieve a deflection of the coupling rod. The center position of the piston crown is correspondingly preferably provided in the longitudinal center of the cylinder housing. From the basic position of the lifting cylinder or the piston is, if necessary, movable in both directions along the longitudinal axis of the lifting cylinder.

According to a further embodiment, the actuator device has a housing in which a carriage is arranged and connected to the lifting cylinder in such a way that the carriage is displaceable in the axial direction of the lifting cylinder when the piston moves relative to the housing. The lifting cylinder is connected at a first side to the housing and the housing in turn connected to the rail vehicle. The actuator device is thus supported against the rail vehicle or its frame or its chassis. The carriage is connected to the piston of the lifting cylinder. Advantageously, a relative movement of the carriage relative to the rail vehicle and the housing of the actuator device by the movement of the piston can be generated. Thus, the carriage is movable in both directions of movement of the piston in the direction of the longitudinal axis of the lifting cylinder. In this case, the carriage slides within the housing of the actuator device, which preferably has a corresponding guide for the carriage. In particular, the housing may partially or completely surround the carriage, so that a guided, relative movement of the carriage in the housing. se in the axial direction of the lifting cylinder is possible. Furthermore, at least one stop can be provided in the housing. Thus, a maximum travel of the carriage relative to the housing or the rail vehicle can be limited independently of the lifting cylinder in at least one direction.

According to a further embodiment, the actuator device has a toothed rack, which is arranged displaceably in the housing of the actuator device. Thus, the rack is guided along the two axial directions of the lifting cylinder based on the housing. Furthermore, as required, teeth or tooth engagement enable an interlocking positive connection and / or force fit, so that a displacement in the axial direction can be carried out. After a first displacement of the rack in the housing of the positive connection and / or adhesion to the teeth or teeth meshes can be solved. The rack remains in its position. When restoring a form fit and / or adhesion, a second and optionally further displacements of the rack in the housing are feasible.

Preferably, the rack engages positively and / or positively in the coupling rod. By the rack is displaceable in the housing of the actuator device, thus a displacement of the coupling rod is made possible by the displacement of the rack.

According to this embodiment, the actuator device is connectable to the coupling rod by a positive connection and / or frictional connection with the rack can be produced within the actuator device. Furthermore, a connection between the coupling rod and the actuator device in the context of the present invention is releasable by a positive and / or non-positive connection with the rack is achieved within the actuator device. Thus, the actuator device is at least partially decoupled from the coupling rod.

In a further embodiment, the actuator device is provided with a rotatably mounted first pawl and a rotatably mounted second pawl in the carriage. Further, a ramp is provided in the housing on which the first pawl and the second pawl are slidable. If a relative movement of the carriage relative to the housing of the actuator device, the pawls are carried along with the carriage and opposite the ramp on which they rest and against which they are pressed by means of a compression spring, moved.

Upon movement of the carriage, a positive connection between the carriage and the rack by means of the first pawl or the second pawl can be produced. Depending on the direction of movement of the carriage, the first pawl or the second pawl slides off the ramp and engages the teeth of the rack. The other latch remains on the ramp, preventing engagement with the rack. With continuous movement of the piston of the lifting cylinder or the carriage, the rack is entrained in this way. A displacement of the rack can be made to any extent until the piston or the carriage reaches the respective stop of the lifting cylinder or the housing. Furthermore, one end of the movement is reached before the other pawl slides off the ramp.

For the purposes of the present invention, the step size per movement sequence of the actuator device is adjustable with reference to the teeth or interventions of the rack. Likewise, the stroke, in particular the maximum stroke of the pneumatic lift cylinder is variable to adapt the step size. It should be noted that a step size per movement according to the present embodiment, the half stroke, from the basic position to the stop of the lifting cylinder corresponds. Furthermore, it should be noted that with increasing stroke or increasing step size, the positioning accuracy of the pneumatic lifting cylinder and thus of the pneumatically deflectable coupling system is reduced.

Another embodiment of the present invention provides the actuator device with a return spring connected to the housing and the carriage such that the actuator device is recoverable to the home position. In the home position, the first pawl and the second pawl are on the ramp. Preferably, the return spring is positioned in the actuator device such that the return spring is in each case partially arranged in a groove of the carriage and in a groove of the housing. In a relative movement of the carriage relative to the housing, the spring is compressed in this manner and stored a restoring force. For the positioning of the return spring, the end Th the return spring preferably provided a centering or positioning.

Advantageously, the actuator device or the carriage is reset together with the piston by the return spring in a basic position when the pneumatic lifting cylinder is relaxed. Further, by the return spring or the return of the actuator device in the basic position, a positive connection and / or adhesion of the carriage with the rack, over the two pawls, automatically released. The rack remains in the provision of the actuator device advantageously in its previously set position.

If the return spring returns the actuator device to its basic position, the first pawl and the second pawl are pulled onto the ramp. In particular, the pawl, which has slid off the ramp during the previous movement of the carriage, is returned to the ramp. Thus, the form-fitting and / or non-positive engagement of the slipped pawl is released into the rack. Consequently, when the actuator device or the piston and the carriage of the actuator device move to the home position, the rack remains at its relative position relative to the housing of the actuator device. A previously achieved displacement of the rack is maintained. Consequently, a previously set deflection of the coupling rod with the coupling head is maintained.

If subsequently a further movement of the piston with the carriage is initiated, one of the pawls slides off the ramp according to the direction of movement and engages in the rack in order to carry it along. After reaching the desired position, the return spring moves the carriage back to the basic position. Another shift of the rack is done. By performing the displacement of the carriage with the pawls in one direction and the subsequent return to the basic position several times in succession, a stepwise displacement of the rack takes place by a desired amount. By the rack is in engagement with the coupling rod of the rail vehicle, a desired deflection of the coupling rod with the coupling head is gradually achieved by the actuator device. In a further embodiment, the housing of the actuator device has a brake unit, so that a relative movement of the rack relative to the housing can be delayed. Advantageously, no free movement of the rack can be done in the housing. In particular, with a slope of the route and a thus justified oblique position of the rail vehicle an undesirable displacement of the rack in the housing can be prevented in this way. Among other things, the brake unit may be provided as a spring-loaded detent unit. The spring-loaded catch unit engages in the rack. Free movement of the rack in the housing is delayed.

According to a further embodiment, the delay of the rack is effected by friction. Such a friction brake may be designed as a manually operated brake or as a self-acting brake or as a continuously acting brake. The frictional force acting on the rack is in this case to be set such that in particular an undesirable free movement of the rack, z. B. by gravity in inclination of the rail vehicle is prevented. There is the advantage that a position of the rack can also be kept under the action of gravity.

According to one embodiment of the present invention, at least a first fluid outlet and a second fluid outlet are provided along the cylinder housing. In this case, the fluid connections can preferably be used as fluid feeds.

In the basic position of the lifting cylinder, a first volume and a second volume are located laterally of the piston crown. Preferably, the fluid outlets are arranged on the cylinder housing such that there is one fluid outlet per volume in the basic position of the lifting cylinder. A working fluid can be diverted on both sides of the piston head from the respective volume of the lifting cylinder via the first and / or second fluid outlet. This has the advantage of being able to use the fluid connections for the supply of fluid, while the fluid outlets for discharging fluid from the cylinder housing can be used.

In general, a fluid outlet is not assigned to any of the two volumes of the lifting cylinder. A fluid outlet makes it possible to establish a fluid connection to one of the volumes as a function of the position of the fluid Piston or the piston crown. The fluid outlets are assigned to the first volume or the second volume depending on the position of the piston bottom within the cylinder housing. If the piston head is exactly at the position of a fluid outlet, this fluid outlet is fluidly closed by the piston crown so that the fluid outlet is not assigned to either of the two volumes. Then, no fluid can flow out of the lift cylinder via this closed fluid outlet.

In particular, the fluid outlets are provided for fluidically discharging gaseous working fluid from a volume of the lifting cylinder. Likewise, it is not excluded that the fluid outlets can be used as fluid connections for introducing fluid into a volume of the lifting cylinder. Likewise, it may be advantageous to use the fluid connections for discharging working fluid from the lifting cylinder, in particular to drive the lifting cylinder in an end position or stop position. Advantageously, all the combination for introducing and discharging fluid into and out of a volume of the lifting cylinder can be represented with the fluid connections and the fluid outlets.

According to this embodiment, the lifting cylinder is connected via the piston rod directly to the coupling rod. For the purposes of the present invention, the actuator device can be positively and / or non-positively connected to the coupling rod. However, according to this embodiment, it is provided that a connection between the coupling rod and the piston rod is continuous. On the basis of the at least two fluid outlets, the movement of the piston can be controlled in such a way that pneumatic lifting cylinders with large lifting distances can be used.

In a further embodiment of the present invention, the fluid outlets are each fluidly connected to a valve, so that an outflow of fluid from the cylinder housing via at least one of the fluid outlets is controllable. Advantageously, the hydrostatic pressure conditions in the two volumes of the lifting cylinder can be adjusted and controlled on the basis of the fluid connections, which are used here as the fluid inlet, and the fluid outlets. A movement of the piston of the lifting cylinder can be generated by different hydrostatic pressure in the volumes of the cylinder housing, on both sides of the piston crown. see pressures are set. This hydrostatic pressure ratio can be adapted by increasing the pressure across the fluid connections or by opening at least one of the valves in order to allow working fluid to flow out of the lifting cylinder via the corresponding fluid outlet.

It is possible to generate a movement of the piston in the cylinder housing, and thus a deflection of the coupling rod, by a high hydrostatic pressure difference in the two volumes of the lifting cylinder. Further, it is possible to generate such movement of the coupling rod by opening at least one fluid outlet at the same pressure in the first and second volumes of the lift cylinder, which allows outflow of working fluid from one of the volumes and associated pressure decrease. Further, it is possible to simultaneously carry out the increase of the hydrostatic pressure in one volume by introducing additional working fluid and discharging working fluid from the other volume. In this way, an optimal travel speed can be achieved with exact positioning of the coupling rod in the course of the deflection.

According to a further embodiment, the fluid outlets over the length of the cylinder housing are preferably arranged at the same distance from each other. Advantageously, in each case at least one fluid outlet is arranged in the basic position of the actuator device on both sides of the piston crown. Thus, a targeted movement of the piston in both axial directions of the lift cylinder is possible.

According to a further embodiment, a movement of the piston can be generated by means of at least one of the valves, a fluid connection via the associated fluid outlet can be produced. If the at least one valve is opened, the working fluid flows out of the assigned volume of the cylinder housing in accordance with the hydrostatic pressure conditions via the associated fluid outlet from the cylinder housing. According to the hydrostatic pressure ratios between the two volumes in the cylinder housing, the piston moves in the direction of the smaller hydrostatic pressure. As soon as the piston bottom reaches the fluid outlet through which working fluid flows out of the cylinder housing and closes this fluid outlet, no further fluid can flow out of the cylinder housing , In the episode it comes to a pressure equalization between the two volumes of the cylinder housing. The piston is braked in an advantageous manner in a damped form. Furthermore, a desired position of the piston can be precisely approached with reference to the fluid outlets. Due to the connection between the piston rod and the coupling rod, a deflection of the coupling rod can be achieved in this way.

The invention is explained in more detail below on the basis of embodiments with reference to the accompanying schematic drawings. Further embodiments of the article according to the invention are therefore not to be excluded in the context of the present invention.

They show schematically:

1 shows a coupling device according to the invention for a rail vehicle;

2a shows a first embodiment of an actuator device according to the invention;

FIG. 2b shows the exploded view of the first exemplary embodiment of an actuator device according to the present invention; FIG.

Fig. 2c: the first embodiment of an actuator device according to the present invention in side view;

3a shows the first embodiment of an actuator device according to the present invention in the sectional view A-A according to FIG. 2c;

3b shows the first embodiment of an actuator device according to the present invention in the sectional view B-B of FIG. 2c.

3c shows the first embodiment of an actuator device according to the present invention in the detail view XX according to FIG. 3a; 4a-c: an exemplary sequence for achieving a deflection of the coupling rod with the first embodiment of an actuator device according to the present invention; and

Fig. 5a-c: an exemplary sequence for achieving a deflection of the coupling rod with a second embodiment of the actuator device according to the present invention.

Fig. 1 shows an exemplary embodiment of the inventive coupling system for a rail vehicle 1. The coupling system has a bearing block 2. On the bearing block 2, a coupling rod 3 is attached with its first end by means of an articulated connection 2a. At the second end of the coupling rod 3, which faces away from the rail vehicle 1, a coupling head 4 is provided for connection to a further rail vehicle or its coupling device.

Laterally of the coupling rod 3, an actuator device 5 is arranged. In particular, the actuator device 5 is positioned on one side with respect to the coupling rod 3. The actuator device 5 is mounted by means of a fixed bearing 6 on the rail vehicle 1 or on its frame or on the chassis. Furthermore, the actuator device 5 engages with the aid of a rack 15 or a piston rod 112b on the coupling rod 3, so that a lateral deflection of the coupling rod 3 with the coupling head 4 is possible. On the basis of the actuator device 5, a lateral deflection of the coupling rod 3 in two directions is possible. The coupling rod 3 rotates about an axis of rotation which passes through the articulated connection 2a of the coupling rod 3 with the bearing block 2.

Fig. 2a illustrates a first exemplary embodiment of the actuator device 5 for a clutch system according to the invention. The actuator device 5, as shown in FIG. 2a a housing 5a. In the housing 5a, the rack 15 is slidably mounted and guided. The rack 15 has a receptacle 20 for connection to the coupling rod 3 (see Fig. 1). Furthermore, the actuator device 5 has a lifting cylinder 10 which is connected on one side to the housing 5a. The lifting cylinder 10 is connected on its other side via a piston 12, which has a piston rod 12b, with a carriage 5b (not shown in FIG. 2a). represents). The lifting cylinder 10 is designed for this purpose on both sides with suitable receiving devices. According to Fig. 2a, the connections between the housing 5a and the lifting cylinder 10 and between the lifting cylinder 10 and piston rod 12b and slide 5b are made and secured by means of a bolt connection. Thus, a translational movement of the piston 12 in the lifting cylinder 10 can be transmitted to the carriage 5b, wherein the lifting cylinder 10 is supported against the housing 5a. The housing 5a is in turn connected to the rail vehicle 1 (not shown in Fig. 2a), so that a power transmission to the rail vehicle 1 and its frame or chassis is carried out.

FIG. 2b shows the first exemplary embodiment of the actuator device 5 according to the invention in an exploded view. The actuator device 5 has the two-part housing 5a and the carriage 5b, which is displaceably mounted and guided in the housing 5a. In the housing 5a, a ramp 17 is provided, which is arranged along the guide for the carriage 5b. Recesses are provided on both sides of the ramp 17 which interrupt the guide surface of the housing 5a for the carriage 5b. The ramp 17 opens with falling flanks in the wells. At the opposite end, the recesses have steep, in particular vertical, end stops. The recesses project into the underlying guide for the rack 15.

Furthermore, the housing 5a has on its upper side a cutout, through which the carriage 5b can protrude, so that the carriage 5b can be connected to the lifting cylinder 10 or its piston rod 12b. At the same time, this section of the housing 5a represents stops for restricting the translational movement of the carriage 5b.

According to Fig. 2b, a groove for partially receiving a return spring 18 is provided in the carriage 5b. Preferably, a corresponding groove is provided in the housing 5a (not shown in FIG. 2b) so that the return spring 18 projects partially into the housing 5a and partially into the carriage 5b. The return spring 18 is further provided on both sides with end caps in order to be able to be positioned safely and centered in the grooves of the housing 5a and the carriage 5b. If, based on the lifting cylinder 10, a relative movement of the carriage 5b relative to the housing 5a is initiated, in particular for the purpose of steering the coupling rod 3, the return spring 18 is compressed. As soon as the pneumatic lifting cylinder 10 is relaxed, the carriage 5b and the piston 12 of the lifting cylinder 10 are moved back to the basic position by relaxing the compressed return spring 18.

Furthermore, the actuator device according to FIG. 2b has a first pawl 16a and a second pawl 16b, which are pressed apart by a compression spring 19. The pawls 16a; 16b are rotatably mounted connected to the carriage 5b. In the basic position of the actuator device 5 are the two pawls 16a; 16b on the ramp 17 of the housing 5a and are pressed by the compression spring 19 against them. In a translational movement of the carriage 5b relative to the housing 5a in one of the two axial directions of the lifting cylinder 10 slides one of the two pawls 16a; 16b from the ramp 17 in the adjacent recesses. The slipped pawl 16a; 16b protrudes into the guide of the housing 5a for the rack 15 after sliding. The rack 15 has teeth or interventions over at least part of its total length. The teeth of the rack 15 are the pawls 16a; 16b and the ramp 17 in the opposite direction.

Fig. 2c shows the first embodiment of the actuator device 5 in a side view. The lifting cylinder 10 is positioned on the top of the housing 5a and is connected thereto. The housing 5a has guides for the carriage 5b and underneath for the rack 15. The return spring 18 protrudes with its diameter partially into the carriage 5b with the groove provided for this purpose and partly into the housing 5a with the groove provided for this purpose.

Fig. 3a shows the first embodiment of the actuator device in the sectional view AA of FIG. 2c. Arrows indicate the directions of movement, in which the Aktorvorrichung 5 movable or the rack 15 is displaced. The lifting cylinder 10 with the piston 12 and the cylinder housing 11 is connected via the piston rod 12b with the carriage 5b. A piston head 12a of the piston 12 divides the cylinder housing 11 into a first volume VI and a second volume V2. Furthermore, the lifting cylinder 10 preferably has two fluid inlets 13a; 13b for the first volume VI and the second volume V2 (not shown in FIG. 3a). The lifting cylinder 10 is thus used as a double-acting lifting cylinder. The actuator device 5 is located according to FIG. 3a in its basic position. tion, wherein the piston head 12 a of the piston 12 is located in the center of the cylinder housing 11. A movement of the piston 12 along the axial directions of the lifting cylinder 10 is possible from this basic position on both sides. Likewise, the carriage 5b is positioned in the center of the recess at the top of the housing 5a, through which the carriage 5a protrudes with its connecting part for connection to the piston 12.

In the housing 5a, the ramp 17 is provided. On the ramp 17 are the two rotatably mounted pawls 16a; 16b arranged opposite each other. The two pawls 16a; 16b are attached to the carriage. The compression spring 19 presses the pawls 16a; 16b apart and against the ramp 17 of the housing 5a. If one of the pawls 16a; 16b slides off of the ramp 17 in one of the respective adjacent recess engages the abgeglittene pawl 16a; 16b into the depression and the rack 15 guided along it or their tooth engagement.

3b illustrates the first embodiment of the actuator device 5 for a coupling system according to the invention in the sectional view B-B of FIG. 2c. According to Fig. 3b, the arrangement of the return spring 18 within the grooves in the housing 5a and in the carriage 5b can be seen. The carriage 5b is displaceable in the provided guide within the housing 5a. Further, Fig. 3b shows the ramp 17 with the laterally arranged recesses. The rack 15 protrudes beyond these recesses, as shown in FIG. 3b, so that when a pawl 16a slides; 16b of the ramp 17 in one of the recesses of the engagement of the respective pawl 16a; 16b takes place in the rack or their teeth.

FIG. 3c shows a detailed view XX according to FIG. 3a of the first exemplary embodiment of an actuator device 5. In particular, the detail view XX represents the first and second pawls 16a; 16b rests on the ramp 17. The compression spring 19 presses the two pawls 16a; 16b apart and against the ramp 17. Furthermore, the ramp 17 on both sides sloping flanks, which open into depressions. Thus, a pawl 16a; 16b, which has previously been slid from the ramp 17, by a movement of the carriage 5b in the opposite direction again slide onto the ramp 17 or be pulled up. FIGS. 4 a to 4 c illustrate a movement sequence of the exemplary actuator device 5 according to FIG. 2 a for a coupling system according to the invention in order to enable the deflection of the coupling rod 3 of a rail vehicle 1. The directions of movement of the carriage 5b and the rack 15 are indicated by arrows in Figs. 4a to 4c indicated.

According to FIG. 4a, a movement of the piston 12 to the right takes place on the basis of corresponding hydrostatic pressure conditions in the lifting cylinder 10, that is to say a higher hydrostatic pressure in the first volume VI and a lower hydrostatic pressure in the second volume V2. The piston rod 12b transmits the movement of the lifting cylinder 10 to the carriage 5b, so that it is moved relative to the housing 5a, and thus also relative to the rail vehicle 1. The ramp 17 is arranged in the housing 5a and also carries out no movement. The pawls 16a; 16b are carried along by the carriage 5b moving to the right and slide over the ramp 17 to the right. At the end of the ramp 17, the second pawl 16b slides from the ramp 17 into the adjacent recess and engages in the teeth or the interventions of the toothed rack 15. The first pawl 16a is partially still on the ramp 17th

The engagement of the second pawl 16b in the rack 15 is a positive and / or frictional connection with the teeth of the rack 15. While the carriage 5b is moved over the piston 12 and the piston rod 12b, the carriage 5b takes the rack 15 on the basis of the engaging second pawl 16b with.

4b shows the status of the exemplary actuator device 5 as soon as the carriage 5b has reached the right stop of the housing 5a. After the right pawl 16b has engaged in the rack 15, the rack 15 has been carried along with the movement of the carriage 5b. As a result, a deflection of the coupling rod 3 is achieved, which is connected via the receptacle 20 with the rack 15 (not shown in Fig. 4a-4c).

As soon as the carriage 5b reaches the stop of the housing 5a, preferably the piston 12 has arrived at the corresponding end of the lifting cylinder 10. By the available stroke of the lifting cylinder 10 application-specifically in Hin- Ranging size is designed, at the same time an optimized positioning accuracy can be ensured. By contrast, an oversized lifting cylinder leads to an inaccuracy in the positioning of the pneumatic lifting cylinder and thus to an unacceptable deflection of the coupling rod. 3

Fig. 4c illustrates the return of the actuator device 5 and the carriage 5b and the piston 12 in the basic position by means of the return spring 18 (not shown in 4a to 4c). For this purpose, the lifting cylinder 10 is relaxed, i. the hydrostatic pressure ratio between the first volume VI and the second volume V2 is dissolved, so that in both volumes VI; V2 the same hydrostatic pressure is present. Based on the relative movement of the carriage 5b relative to the housing 5a, the return spring 18 has been previously biased or compressed. Once an end of the movement of the carriage 5 b is reached, the lifting cylinder 10 can be relieved by a corresponding reduction of the hydrostatic pressure in the first volume VI. With the aid of the prestressed return spring 18, the actuator device 5 is then moved back to the basic position.

For this purpose, the preloaded return spring 18 triggers a relative movement of the carriage 5b relative to the housing 5a, so that the piston head 12a returns to the longitudinal center of the cylinder housing 11. Here, the pawls 16a received in the carriage 5b; 16b pulled back onto the ramp 17, so that the positive and / or non-positive engagement of the second pawl 16b is dissolved in the rack 15. As soon as the piston head 12a is again centered in the cylinder housing 11, the two pawls 16a; 16b arranged on the ramp 17.

By engaging the lifting cylinder 10 in the home position, together with the carriage 5b, the engagement of the two pawls 16a; 16b is released and prevented by means of the ramp 17, the rack 15 remains in the previously set position. Consequently, a previously set deflection of the coupling rod 3 is maintained during the return movement of the actuator device 5 in the basic position.

If the coupling rod 3 is to be deflected further, the process according to FIGS. 4 a to 4 c can be repeated as often as desired until a maximum deflection of the coupling rod 3 or displacement of the rack 15 is provided. is enough. A stop at an arbitrary position of the stroke of the Huzylinder 10 is not provided according to this first embodiment. It is always carried out a complete movement of the lifting cylinder 10 and the piston 12 from the basic position to the stop of the lifting cylinder 10 and the housing 5a. The (preliminary) deflection of the coupling rod 3 with the coupling head 4 (not shown in Fig. 2, 2a to 2c) takes place step by step on the basis of the recurrent retraction of the actuator device 5 or of the carriage 5b into the basic position.

5a shows a further, second exemplary embodiment of the actuator device 5 for a coupling system according to the invention. The illustrated actuator device 5 has the lifting cylinder 110, with the cylinder housing 111 and the piston 112. The piston 112 has the piston head 112a and the piston rod 112b. The piston bottom 112b divides the cylinder housing 111 into the first volume VI and the second volume V2. The piston rod 112b is preferably connected directly to the coupling rod 3 (not shown in Fig. 5a, see Fig. 1). Consequently, a deflection of the piston 112 leads to a direct deflection of the coupling rod 3 in the axial direction of the lifting cylinder 10th

The cylinder housing 111 has two fluid inlets 113a; 113b in the vicinity of the end sides or at the end sides. According to FIG. 5a, four fluid outlets 114a; 114b; 114c; 114d are provided, which are preferably distributed at the same distance from one another along the longitudinal direction of the cylinder housing 111. Furthermore, in the basic position of the actuator device 5, the first volume VI and the second volume V2 are preferably assigned an equal number of fluid outlets. Furthermore, valves are provided at the fluid outlets 114a-114d (not shown in FIG. 5a) such that fluid opening of a fluid outlet 114a-114d causes fluid to flow out of the first volume VI and / or the second volume V2 of the cylinder housing 111 , is controllable.

The Figs. 5a to 5c illustrate a movement of the second embodiment of the actuator device 5 for a coupling system according to the invention in order to achieve a (pre-) deflection of the coupling rod 3 of a rail vehicle 1. FIG. 5 a shows the actuator device 5 or the lifting cylinder 10 in the basic position. The first three fluid outlets 114a-c are fluidly separated while the valve is open at the fourth fluid outlet 114d. In the first volume VI, a greater hydrostatic pressure is applied than in the second volume V2. As a result, the piston 112 moves with the piston head 112a of FIG. 5b to the right. As a result, a corresponding deflection of the coupling rod 3 is achieved via the movement of the piston rod 112b.

In Fig. 5b, the state is shown before the piston head 112a, the opened fourth fluid outlet 114d passes and thereby closes. As soon as the piston head 112a reaches the fourth fluid outlet and closes it in fluid, so that no further fluid can escape from the second volume V2, as the piston 112 moves to the right, the hydrostatic pressure in the second volume V2 increases. Accordingly, a movement of the piston 112 is slowed down as soon as the piston head 112a reaches the fluidly opened, fourth fluid outlet and at least partially closes.

FIG. 5c shows the state of the actuator device 5 according to the second exemplary embodiment as soon as the piston bottom 112a has exceeded the fluidly connected fluid outlet 114d. In this state of the actuator device 5 there is a fluid connection via the fourth fluid outlet 114d to the first volume VI. The second volume V2 is closed in the flow, so that no fluid can flow out of the second volume V2. As soon as the piston bottom 112b has reached and exceeds the opened fourth fluid outlet 114d, a hydrostatic pressure is generated in the second volume V2, which counteracts the hydrostatic pressure in the first volume VI. The hydrostatic pressures of the first and second volumes VI; V2 are the same. As a result, movement of the piston 12 is decelerated until the hydrostatic pressures in the first volume VI and in the second volume V2 are equal.

As a result, the piston head 112a is oriented such that a balance of the hydrostatic pressures in the first volume VI and in the second volume V2 is achieved. In this case, the piston bottom 112a closes the opened fourth fluid port 114d, so that the piston 112 assumes a defined position. The coupling rod 3 is thus deflected targeted. Depending on the Position of the fluid ports 114a-d and the fluid opening or closing of the fluid ports 114a-d is targeted in this way a specific position with the pneuamtischen lifting cylinder approachable. A stepwise deflection of the coupling rod 3 over the entire stroke of the lifting cylinder 110 can also be carried out stepwise by the fluid ports 114a-d are opened and closed successively in a controlled manner accordingly.

Through the fluid connections 113a; 113b the respective volume VI; V2 is subjected to a specific pneumatic pressure, so that the piston head 112a can be further held in a desired position. Furthermore, a fluid outlet 114a-d or a plurality of fluid outlets 114a-d may be fluidly closed simultaneously or serially based on the associated valves, if desired, movement of the piston 112 of the lift cylinder 110 may be controlled. In particular, in this case also pneumatic lifting cylinder can be used with larger strokes because a targeted positioning of the piston 112 takes place on the basis of the fluid outlets 114a-d. In particular, a stepwise deflection of the coupling rod 3 is thus possible, which is directly connected to the piston rod 112b.

reference numeral

VI first volume

V2 second volume

1 rail vehicle

2 bearing block

2a articulated connection to the bearing block

3 coupling rod

4 coupling head

5 actuator device

5a housing

5b sledges

10 lifting cylinders

11 cylinder housing

12 pistons

12a piston crown

12b piston rod

13a first fluid inlet

13b second fluid inlet

14a-d fluid outlet

15 rack

16a first latch

16b second latch

17 ramp

18 return spring

19 compression spring

20 recording

Claims

PO Box 860624 81633 Munich Voith Patent GmbH 8 March 2017 Sankt Pöltener Strasse 43 M / SBK-173-PC 89522 Heidenheim RU / ME COUPLING SYSTEM WITH PNEUMATIC LIFTING Patent claims

A coupling system for a rail vehicle (1), comprising a bearing block (2) which is provided on the rail vehicle (1), with a coupling rod (3) which at its first end via an articulated connection (2a) to the vehicle ( 1), with a coupling head (4) which is provided at the second end of the coupling rod (3), which is remote from the rail vehicle (1), and with an actuator device (5), the side of the coupling rod (3) arranged and connected to the rail vehicle (1), characterized in that

the actuator device (5) is provided on one side with respect to the coupling rod (3) and has a pneumatic lifting cylinder (10; 110) so that the coupling rod (3) can be deflected stepwise in two opposite directions at its second end with the coupling head (4) is and the actuator device (5) non-positively and / or positively connected to the coupling rod (3) is connectable.

2. Coupling system according to claim 1,

wherein the lift cylinder (10; 110) has a cylinder housing (11; 111) provided with a first fluid port (13a; 113a) and a second fluid port (13b; 113b).

3. Coupling system according to one of claims 1 or 2, 2 wherein the lift cylinder (10; 110) has a home position in which a piston head (12a; 112a) of a piston (12; 112) of the lift cylinder (10; 110) is in a central position such that the piston (12; 112) in both axial directions of the lifting cylinder (10; 110) is movable.

4. Coupling system according to one of the preceding claims,

wherein the actuator device (5) has a housing (5a) in which a carriage (5b) is arranged, which is connected to the lifting cylinder (10) such that the carriage (5b) moves relative to the housing when the piston (12) moves (5a) in the axial direction of the lifting cylinder (10) is displaceable.

5. Coupling system according to one of the preceding claims,

wherein the actuator device (5) is provided with a rack (15) which is slidably provided in the housing (5a) of the actuator device (5).

6. Coupling system according to one of the preceding claims,

wherein the actuator device (5) comprises a rotatably mounted first pawl (16a) and a rotatably mounted second pawl (16b) in the carriage (5b) and a ramp (17) in the housing (5a) on which the first pawl (16) 16a) and the second pawl (16b) are displaceable, is provided such that upon movement of the carriage (5b) a positive connection between the carriage (5b) and the rack (15) by means of the first pawl (16a) or the second pawl (16b) can be produced.

7. Coupling system according to one of the preceding claims,

wherein the actuator device (5) has a return spring (18) which is connected to the housing (5a) and the carriage (5b) such that the actuator device (5) can be reset to the basic position in which the first pawl (16a) and the second pawl (16b) rest on the ramp (17).

8. Coupling system according to one of the preceding claims,

wherein the housing (5a) of the actuator device (5) has a brake unit, so that a relative movement of the rack (15) relative to the housing (5a) is delayable.

9. Coupling system according to one of the preceding claims, 3 where the delay is due to friction.

10. Coupling system according to one of claims 1 to 3,

wherein at least a first fluid outlet (114a) and a second fluid outlet (114d) are provided along the cylinder housing (111).

11. Coupling system according to claim 10,

wherein the fluid outlets (114a, 114b, 114c, 114d) are each fluidly connected to a valve so that outflow of fluid from the cylinder housing (111) is controllable via at least one of the fluid outlets (114a, 114b, 114c, 114d).

12. Coupling system according to one of claims 10 or 11,

wherein the fluid outlets (114a, 114b, 114c, 114d) are preferably equidistantly spaced over the length of the cylinder housing.

13. Coupling system according to one of claims 10 to 12,

wherein a particular stepwise movement of the piston (112) in the axial direction of the lifting cylinder (110) is controllable by a fluid via at least one of the fluid outlets (114a, 114b, 114c, 114d), if necessary, from the cylinder housing (111) can be derived.