EP3429901B1 - Coupling system having pneumatic deflection - Google Patents
Coupling system having pneumatic deflection Download PDFInfo
- Publication number
- EP3429901B1 EP3429901B1 EP17709656.7A EP17709656A EP3429901B1 EP 3429901 B1 EP3429901 B1 EP 3429901B1 EP 17709656 A EP17709656 A EP 17709656A EP 3429901 B1 EP3429901 B1 EP 3429901B1
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- EP
- European Patent Office
- Prior art keywords
- actuator device
- housing
- coupling
- piston
- pawl
- Prior art date
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- 230000008878 coupling Effects 0.000 title claims description 131
- 238000010168 coupling process Methods 0.000 title claims description 131
- 238000005859 coupling reaction Methods 0.000 title claims description 131
- 239000012530 fluid Substances 0.000 claims description 97
- 230000002706 hydrostatic effect Effects 0.000 description 19
- 230000006835 compression Effects 0.000 description 6
- 238000007906 compression Methods 0.000 description 6
- 238000006073 displacement reaction Methods 0.000 description 6
- 238000007599 discharging Methods 0.000 description 5
- 230000008901 benefit Effects 0.000 description 4
- 230000003111 delayed effect Effects 0.000 description 3
- 230000000717 retained effect Effects 0.000 description 3
- 230000005540 biological transmission Effects 0.000 description 2
- 230000005484 gravity Effects 0.000 description 2
- 238000007373 indentation Methods 0.000 description 2
- 206010019233 Headaches Diseases 0.000 description 1
- 230000009471 action Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 230000010354 integration Effects 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000009931 pascalization Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 230000000284 resting effect Effects 0.000 description 1
Images
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B61—RAILWAYS
- B61G—COUPLINGS; DRAUGHT AND BUFFING APPLIANCES
- B61G7/00—Details or accessories
- B61G7/10—Mounting of the couplings on the vehicle
- B61G7/12—Adjustable coupling bars, e.g. for centralisation purposes
Definitions
- 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 independent claim 1.
- a system for deflecting a coupling device is, for example, from DE 10 2014 101 986 A1 known.
- the coupling device has an actuator connected to the car body. This actuator is designed to deflect the coupling rod from the central position as required. Since the coupling device of two opposite rail vehicles are accordingly steered in advance, an automatic coupling of two rail vehicles is possible even in tight bends, for example.
- the actuators or actuators required for this are primarily designed as hydraulic systems in order to enable the coupling head of a rail vehicle to be positioned quickly and precisely with any deflection.
- rail vehicles only rarely have hydraulic systems.
- the necessary system components, such as hydraulic pumps, pressure accumulators and pressure relief valves, must also be integrated into the infrastructure of the rail vehicle in order to enable the coupling head to be deflected to the side.
- hydraulic fluids such as oil represents a major risk factor in the event of a fire.
- the present invention is based on the object of providing a coupling system which enables simple, cost-effective and low-risk integration into a rail vehicle. Furthermore, a finely stepped (pre-) deflection of the coupling head of a coupling device should be made possible.
- the coupling system according to the invention for a rail vehicle has a bearing block which can be arranged on the rail vehicle, a coupling rod which can be connected to the vehicle at its first end via an articulated connection, a coupling head which is connected to the second end of the Coupling rod is arranged, which faces away from the rail vehicle in the assembled state, and an actuator device which is arranged to the side of the coupling rod.
- the actuator device can be connected to the rail vehicle.
- the connection between the actuator device and the rail vehicle is preferably designed as a fixed bearing. The actuator device is thus advantageously supported against the rail vehicle or its frame or its chassis in order to enable a relative movement of the coupling rod with the coupling head with respect to the rail vehicle.
- the actuator device according to the invention is arranged on one side with respect to the coupling rod. This arrangement has the advantage that the pivoting range of the coupling rod when it is deflected, in particular in a lateral direction, is not restricted by the actuator device.
- the deflection of the coupling rod is always to be understood as the rotation of the coupling rod about an axis of rotation, so that the coupling head experiences an appropriate (pre-) deflection and the connection or coupling of two opposing rail vehicles is made possible.
- the coupling rod is always rotated about an axis of rotation that runs through the articulated connection between the coupling rod and the rail vehicle or bearing block. If the coupling head can be sufficiently deflected via the coupling rod, two rail vehicles facing each other can be coupled to one another using 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 it is possible to find the coupling devices opposing one another.
- the actuator device has a pneumatic lifting cylinder, so that the coupling rod can be deflected at its second end with the coupling head in two opposite directions.
- a pneumatic lifting cylinder has the advantage that the fluid or working fluid, in contrast to hydraulic fluids such as oil, does not pose any additional risk, for example in the event of a fire. Rather, media such as air or other gas can be used which have further advantageous properties.
- a poorly flammable working fluid can be selected in order to further reduce the hazard potential in the event of a fire.
- the infrastructure of rail vehicles has pneumatic systems, so that no additional components, such as pressure accumulators, pneumatic pumps for providing a compressed working fluid or pressure relief valves, are 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. In this way, the infrastructure or the number of system components, e.g. compared to a hydraulic device for deflecting the coupling rod, can be reduced.
- the coupling rod can be deflected in two opposite directions with the aid of the actuator device.
- per coupling device or a single actuator device per coupling rod is sufficient to enable the appropriate use of a rail vehicle.
- the number of components for deflecting the coupling rod with the coupling head is reduced. In addition to a reduced probability of failure, cost-efficient production and maintenance can be guaranteed.
- the deflection of the coupling rod by the pneumatic lifting cylinder takes place, in particular, step by step. It is thus advantageously possible to subdivide a desired deflection of the coupling rod into several 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 fundamental disadvantage of a pneumatic lifting cylinder compared to e.g. a hydraulic lifting cylinder can be reduced by using smaller lifting cylinders.
- the step-by-step deflection of the coupling rod with the coupling head is sufficiently precise and fast so that rail vehicles opposite one another can be connected to one another by means of the gripping area of the coupling head.
- the actuator device can be connected non-positively and / or positively to the coupling rod.
- a connection between the actuator device and the coupling rod can be permanent.
- the actuator device according to the present invention does not have to be continuously connected to the coupling rod.
- the actuator device in its entirety does not have to be permanently connected to the coupling rod at all times.
- individual components of the actuator device can, if necessary, be decoupled from the connection to the coupling rod or can be connected to the coupling rod.
- a force transmission through the actuator device to the coupling rod can consequently be established on the basis of a force-fit and / or form-fit connection. A deflection of the coupling rod can thus be achieved as required.
- the lifting cylinder has a cylinder housing which is provided with a first fluid connection and a second fluid connection.
- the first and the second fluid connection can be used as a fluid inlet and / or fluid outlet.
- the lifting cylinder is designed as a double-acting lifting cylinder. A movement in both directions along the longitudinal axis of the lifting cylinder can advantageously be carried out with the lifting cylinder as required. Any position of the lifting cylinder can thus be approached in a controlled or regulated manner with high accuracy.
- 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 can be moved in both axial directions of the lifting cylinder.
- the basic position of the lifting cylinder advantageously represents the state from which a movement of the piston takes place in order to achieve a deflection of the coupling rod.
- the central position of the piston head is accordingly preferably provided in the longitudinal center of the cylinder housing. If necessary, the lifting cylinder or the piston can be moved in both directions along the longitudinal axis of the lifting cylinder from the basic position.
- the actuator device has a housing in which a slide is arranged and connected to the lifting cylinder in such a way that the slide can be displaced in the axial direction of the lifting cylinder when the piston moves relative to the housing.
- the lifting cylinder is connected on a first side to the housing and the housing is in turn connected to the rail vehicle.
- the actuator device is thus supported against the rail vehicle or its frame or its chassis.
- the slide is connected to the piston of the lifting cylinder.
- a relative movement of the slide with respect to the rail vehicle and the housing of the actuator device can advantageously be generated by the movement of the piston.
- the slide can thus be moved in both directions of movement of the piston in the direction of the longitudinal axis of the lifting cylinder.
- the carriage slides within the housing of the actuator device, which preferably has a corresponding guide for the carriage.
- the housing can partially or completely surround the slide, so that a guided, relative movement of the slide in the housing is possible in the axial direction of the lifting cylinder.
- at least one stop can be provided in the housing.
- a maximum travel path of the slide relative to the housing or the rail vehicle can be limited in at least one direction independently of the lifting cylinder.
- the actuator device has a toothed rack which is arranged displaceably in the housing of the actuator device.
- the rack is guided along the two axial directions of the lifting cylinder by means of the housing.
- a form fit and / or force fit as required is made possible by teeth or the tooth engagements, so that a shift in the axial direction can be carried out.
- the form fit and / or force fit with the teeth or the tooth engagements can be released.
- the rack remains in its position.
- the toothed rack preferably engages with the coupling rod in a force-fitting and / or form-fitting manner. Since the toothed rack can be displaced in the housing of the actuator device, the displacement of the toothed rack enables the coupling rod to be deflected.
- the actuator device can be connected to the coupling rod in that a form fit and / or force fit with the rack can be produced within the actuator device. Furthermore, a connection between the coupling rod and the actuator device can be released in the sense of the present invention by releasing a positive and / or non-positive connection with the rack within the actuator device. The actuator device can thus be at least partially decoupled from the coupling rod.
- the actuator device is provided with a rotatably mounted first pawl and a rotatably mounted second pawl in the slide. Furthermore, a ramp is provided in the housing, on which the first pawl and the second pawl are slidably displaceable. If there is a relative movement of the carriage with respect to the housing of the actuator device, the pawls are carried along with the carriage and with respect to the ramp on which they are and against which they are pressed by means of a compression spring, displaced.
- a positive connection between the carriage and the rack can be established by means of the first pawl or the second pawl.
- the first pawl or the second pawl slides off the ramp and engages the teeth of the rack.
- the other pawl remains on the ramp, which prevents engagement with the rack.
- the rack can be carried along in this way. The rack can be shifted to any extent until the piston or the slide reaches the respective stop of the lifting cylinder or the housing. Furthermore, one end of the movement is reached before the other pawl also slides off the ramp.
- the step size per movement sequence of the actuator device can be set on the basis of the teeth or engagements of the rack.
- the stroke path, in particular the maximum stroke path, of the pneumatic lifting cylinder can also be varied in order to adapt the step size. It must be taken into account here that one step size per movement sequence according to the present embodiment corresponds to half the stroke path from the basic position to the stop of the lifting cylinder. It should also be taken into account that the positioning accuracy of the pneumatic lifting cylinder and thus of the pneumatically deflectable coupling system is reduced with increasing stroke distance or increasing step size.
- Another embodiment of the present invention provides the actuator device with a return spring which is connected to the housing and the slide in such a way that the actuator device can be reset to the basic position.
- the return spring is preferably positioned in the actuator device in such a way that the return spring is partially arranged in a groove of the slide and in a groove of the housing.
- the spring is compressed in this way and a restoring force is stored.
- a centering means or positioning means is preferably provided for the return spring.
- the actuator device or the slide can be returned to a basic position together with the piston by the return spring when the pneumatic lifting cylinder is relaxed. Furthermore, a form fit and / or force fit of the slide with the rack via the two pawls is automatically released by the return spring or the resetting of the actuator device into the basic position. When the actuator device is reset, the toothed rack advantageously remains in its previously set position.
- the housing of the actuator device has a braking unit, so that a relative movement of the toothed rack with respect to the housing can be delayed.
- the rack cannot move freely in the housing. In this way, an undesirable displacement of the rack in the housing can be prevented, particularly when the route is inclined and the rail vehicle is inclined as a result.
- the braking unit can be provided as a spring-loaded latching unit. The spring-loaded locking unit engages in the rack. Free movement of the rack in the housing is delayed.
- the rack is delayed by friction.
- a friction brake can 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 to be set in such a way that, in particular, undesired free movement of the rack, e.g. due to gravity when the rail vehicle is tilted, is prevented.
- a position of the rack can also be held under the action of gravity.
- At least a first fluid outlet and a second fluid outlet are provided along the cylinder housing.
- the fluid connections can preferably be used as fluid inlets.
- first and a second volume to the side of the piston head.
- the fluid outlets are preferably arranged on the cylinder housing in such a way that there is one fluid outlet per volume in the basic position of the lifting cylinder.
- a working fluid can preferably 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 supplying fluid, while the fluid outlets can be used for discharging fluid from the cylinder housing.
- a fluid outlet is not permanently assigned to either of the two volumes of the lifting cylinder.
- a fluid outlet enables a flow connection to be made to one of the volumes depending on the position of the 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 head within the cylinder housing. If the piston head is exactly at the position of a fluid outlet, this fluid outlet is closed in terms of flow by the piston head, so that the fluid outlet is not assigned to either of the two volumes. Then no fluid can flow out of the lifting cylinder via this closed fluid outlet.
- the fluid outlets are provided for discharging gaseous working fluid from a volume of the lifting cylinder.
- the fluid outlets can be used as flow connections for introducing fluid into a volume of the lifting cylinder. It can also be advantageous to use the fluid connections for discharging working fluid from the lifting cylinder, in particular in order to move the lifting cylinder into an end position or stop position.
- all combinations 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.
- the lifting cylinder is connected directly to the coupling rod via the piston rod.
- the actuator device can be connected to the coupling rod in a form-fitting and / or force-fitting manner.
- a connection between the coupling rod and the piston rod is continuous. With the aid of the at least two fluid outlets, the movement of the piston can be controlled in such a way that pneumatic lifting cylinders with long stroke paths can be used.
- the fluid outlets are each fluidly connected to a valve, so that an outflow of fluid from the cylinder housing can be controlled via at least one of the fluid outlets.
- the hydrostatic pressure conditions in the two volumes of the lifting cylinder can be set and controlled on the basis of the fluid connections, which are used here as a fluid inlet, and the fluid outlets.
- a movement of the piston of the lifting cylinder can be generated by different hydrostatisehe in the volumes of the cylinder housing, on both sides of the piston head Pressures can be adjusted.
- This hydrostatic pressure ratio can be adapted by increasing the pressure via 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.
- the fluid outlets are preferably arranged at the same distance from one another over the length of the cylinder housing.
- at least one fluid outlet is advantageously arranged on both sides of the piston head. A targeted movement of the piston in both axial directions of the lifting cylinder is thus possible.
- a movement of the piston can be generated in that a flow connection via the associated fluid outlet can be established using at least one of the valves. 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 lower hydrostatic pressure.As soon as the piston head 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 . Then it comes to equalize the pressure between the two volumes of the cylinder housing.
- the piston can advantageously be braked in a damped manner. Furthermore, a desired position of the piston can be precisely approached using 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.
- Fig. 1 shows an exemplary embodiment of the coupling system according to the invention for a rail vehicle 1.
- the coupling system has a bearing block 2.
- a coupling rod 3 is attached with its first end to the bearing block 2 by means of an articulated connection 2a.
- a coupling head 4 is provided for connection to a further rail vehicle or its coupling device.
- An actuator device 5 is arranged to the side of the coupling rod 3.
- the actuator device 5 is positioned on one side with respect to the coupling rod 3.
- the actuator device 5 is attached to the rail vehicle 1 or to its frame or to its chassis by means of a fixed bearing 6.
- the actuator device 5 engages the coupling rod 3 with the aid of a toothed rack 15 or a piston rod 112b, so that a lateral deflection of the coupling rod 3 with the coupling head 4 is possible.
- a lateral deflection of the coupling rod 3 in two directions is possible with the aid of the actuator device 5.
- the coupling rod 3 rotates about an axis of rotation which runs through the articulated connection 2 a 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 according to Fig. 2a a housing 5a.
- the rack 15 is slidably mounted and guided in the housing 5a.
- the rack 15 has a receptacle 20 for connection to the coupling rod 3 (cf. Fig. 1 ).
- the actuator device 5 has a lifting cylinder 10, which is connected on one side to the housing 5a.
- the lifting cylinder 10 is on its other side via a piston 12, which has a piston rod 12b, with a slide 5b (in Fig. 2a not shown) tied together.
- the lifting cylinder 10 is designed with suitable receiving devices on both sides.
- the connections between housing 5a and lifting cylinder 10 and between lifting cylinder 10 or piston rod 12b and slide 5b are established and secured by means of a bolt connection.
- a translational movement of the piston 12 in the lifting cylinder 10 can thus be transmitted to the slide 5b, the lifting cylinder 10 being supported against the housing 5a.
- the housing 5a can in turn be connected to the rail vehicle 1 (in Fig. 2a not shown), so that power is transmitted to the rail vehicle 1 or its frame or chassis.
- FIG. 2b shows the first 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 slide 5b which is slidably mounted and guided in the housing 5a.
- a ramp 17 is provided which is arranged along the guide for the carriage 5b.
- On both sides of the ramp 17 there are recesses which interrupt the guide surface of the housing 5a for the slide 5b.
- the ramp 17 opens into the depressions with sloping flanks. At the opposite end, the depressions have steep, in particular vertical, end stops. The depressions protrude into the guide below for the rack 15.
- the housing 5a has a cutout on its upper side, through which the slide 5b can protrude, so that the slide 5b can be connected to the lifting cylinder 10 or its piston rod 12b.
- this section of the housing 5a represents stops for restricting the translational movement of the slide 5b.
- a groove for partially receiving a return spring 18 is provided in the slide 5b.
- a corresponding groove is preferably provided in the housing 5a (in Figure 2b not shown), so that the return spring 18 projects partially into the housing 5a and partially into the carriage 5b.
- the return spring 18 is also provided with end caps on both sides in order to be able to be positioned securely and centered in the grooves of the housing 5a and of the slide 5b. If a relative movement of the slide 5b with respect to the housing 5a is initiated on the basis of the lifting cylinder 10, in particular for deflection the coupling rod 3, the return spring 18 is compressed. As soon as the pneumatic lifting cylinder 10 is relaxed, the slide 5b and the piston 12 of the lifting cylinder 10 are moved back into the basic position by the relaxation of the compressed return spring 18.
- the actuator device a first pawl 16a and a second pawl 16b, which are pressed apart by a compression spring 19.
- the pawls 16a; 16b are rotatably connected to the carriage 5b.
- the two pawls 16a; 16b on the ramp 17 of the housing 5a and are pressed against this by the compression spring 19.
- one of the two pawls 16a slides; 16b from the ramp 17 into the adjacent depressions.
- 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 engagements 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.
- Figure 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 to it.
- the housing 5a has guides for the carriage 5b and, underneath, for the rack 15.
- the diameter of the return spring 18 projects partially into the slide 5b with the groove provided for it and partially into the housing 5a with the groove provided for it.
- Fig. 3a shows the first embodiment of the actuator device in the sectional view AA according to Figure 2c .
- Arrows indicate the directions of movement in which the actuator device 5 can be moved or the rack 15 can be moved.
- the lifting cylinder 10 with the piston 12 and the cylinder housing 11 is connected to the slide 5b via the piston rod 12b.
- a piston head 12a of the piston 12 divides the cylinder housing 11 into a first volume V1 and a second volume V2.
- the lifting cylinder 10 preferably has two fluid inlets 13a; 13b for the first volume V1 and the second volume V2 (in Fig. 3a not shown).
- the lifting cylinder 10 can thus be used as a double-acting lifting cylinder.
- the actuator device 5 is located according to Fig.
- the ramp 17 is provided in the housing 5a. On the ramp 17 are the two rotatably mounted pawls 16a; 16b arranged opposite one another. 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 the ramp 17 into one of the adjacent indentations, the pawl 16a that has slipped off engages; 16b into the recess and the toothed rack 15 guided along it or its tooth engagements.
- Figure 3b illustrates the first exemplary embodiment of the actuator device 5 for a clutch system according to the invention in the sectional view BB according to FIG Figure 2c .
- 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 can be displaced in the guide provided within the housing 5a.
- the ramp 17 with the laterally arranged depressions.
- the rack 15 protrudes according to Figure 3b beyond these indentations, so that when a pawl 16a; 16b from the ramp 17 into one of the recesses, the engagement of the respective pawl 16a; 16b takes place in the rack or its tooth engagement.
- FIG. 3c is a detailed view XX according to Fig. 3a of the first exemplary embodiment of an actuator device 5 is shown.
- the detailed view XX shows the first and second pawls 16a; 16b resting on the ramp 17.
- the compression spring 19 presses the two pawls 16a; 16b apart and against the ramp 17.
- the ramp 17 has sloping flanks on both sides which open into depressions. So can a pawl 16a; 16b, which has previously slipped off the ramp 17, slide or be pulled up again onto the ramp 17 by a movement of the slide 5b in the opposite direction.
- FIGS. 4a to 4c represent a movement sequence of the exemplary actuator device 5 according to FIG Fig. 2a represents a coupling system according to the invention in order to enable the coupling rod 3 of a rail vehicle 1 to be deflected.
- the directions of movement of the carriage 5b and the rack 15 are indicated by arrows in FIG Figs. 4a to 4c indicated.
- 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 V1 and a lower hydrostatic pressure in the second volume V2.
- the piston rod 12b transmits the movement of the lifting cylinder 10 to the slide 5b, so that the slide 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 does not perform any 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 off the ramp 17 into the adjacent recess and engages the teeth or the engagement of the rack 15.
- the first pawl 16a is partially still on the ramp 17.
- the engagement of the second pawl 16b in the rack 15 represents a form and / or force fit with the teeth of the rack 15. While the carriage 5b is moved over the piston 12 or the piston rod 12b, the carriage 5b takes the rack 15 based on the engaging second pawl 16b with.
- Figure 4b shows the status of the exemplary actuator device 5 as soon as the slide 5b has reached the right stop of the housing 5a. After the right pawl 16b has engaged in the rack 15, the rack 15 was carried along with the movement of the carriage 5b. This results in a deflection of the coupling rod 3, which is connected to the rack 15 via the receptacle 20 (in Figures 4a-4c Not shown).
- the piston 12 has preferably also reached the corresponding end of the lifting cylinder 10.
- an optimized positioning accuracy can be guaranteed at the same time.
- a lifting cylinder that is too large leads to inaccuracy in the positioning of the pneumatic lifting cylinder and thus to an imprecise deflection of the coupling rod 3.
- Figure 4c illustrates the return of the actuator device 5 or the slide 5b and the piston 12 to the basic position with the aid of the return spring 18 (not shown in FIGS. 4a to 4c).
- the lifting cylinder 10 is relaxed, ie the hydrostatic pressure ratio between the first volume V1 and the second volume V2 is dissolved, so that in both volumes V1; V2 is the same hydrostatic pressure.
- the return spring 18 was previously pretensioned or compressed.
- the lifting cylinder 10 can be relieved by a corresponding reduction in the hydrostatic pressure in the first volume V1.
- the actuator device 5 is then moved back into the basic position.
- the pretensioned return spring 18 triggers a relative movement of the slide 5b with respect to the housing 5a, so that the piston head 12a moves back into the longitudinal center of the cylinder housing 11.
- the pawls 16a; 16b is pulled back onto the ramp 17, so that the positive and / or non-positive engagement of the second pawl 16b in the rack 15 is released.
- the two pawls 16a; 16b arranged on the ramp 17.
- the process according to FIG Figures 4a to 4c can be repeated as often as desired until a maximum intended deflection of the coupling rod 3 or displacement of the rack 15 is reached is. Stopping at any position of the stroke of the cylinder 10 is not provided according to this first embodiment. There is always a complete movement of the lifting cylinder 10 or the piston 12 from the basic position up to the stop of the lifting cylinder 10 or the housing 5a. The (forward) deflection of the coupling rod 3 with the coupling head 4 (in Fig. 2; 2a to 2c not shown) gradually.
- Figure 5a shows a further, second embodiment of the actuator device 5, which is not part of the invention.
- the actuator device 5 shown 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 head 112b divides the cylinder housing 111 into the first volume V1 and the second volume V2.
- the piston rod 112b is preferably connected directly to the coupling rod 3 (in Figure 5a not shown; please refer 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 10.
- the cylinder housing 111 has two fluid inlets 113a; 113b in the vicinity of the end sides or on the end sides. According to Figure 5a are also four fluid outlets 114a; 114b; 114c; 114d are provided, which are preferably distributed equidistantly 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 V1 and the second volume V2 are preferably assigned an equal number of fluid outlets.
- Valves are also provided at each of the fluid outlets 114a-114d (in Figure 5a not shown), so that the flow-wise opening of a fluid outlet 114a-114d in order to allow fluid to flow out of the first volume V1 and / or the second volume V2 of the cylinder housing 111 can be controlled.
- Figs. 5a to 5c represent 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.
- Figure 5a shows the actuator device 5 or the lifting cylinder 10 in the basic position.
- the first three fluid outlets 114a-c are separated in terms of flow, while the valve at the fourth fluid outlet 114d is open.
- a greater hydrostatic pressure is applied in the first volume V1 than in the second volume V2.
- the piston 112 moves with the piston head 112a according to FIG Figure 5b To the right. This results in a corresponding deflection of the coupling rod 3 via the movement of the piston rod 112b.
- Figure 5c shows the state of the actuator device 5 according to the second exemplary embodiment as soon as the piston head 112a has exceeded the fluid outlet 114d, which is connected in terms of flow.
- This state of the actuator device 5 there is a flow connection via the fourth fluid outlet 114d to the first volume V1.
- the second volume V2 is closed in terms of flow so that no fluid can flow out of the second volume V2.
- a hydrostatic pressure is generated in the second volume V2, which tends to oppose the hydrostatic pressure in the first volume V1.
- the hydrostatic pressures of the first and second volumes V1; V2 align.
- a movement of the piston 12 is braked until the hydrostatic pressures in the first volume V1 and in the second volume V2 are the same.
- the piston head 112a aligns itself in such a way that an equilibrium of the hydrostatic pressures is achieved in the first volume V1 and in the second volume V2.
- the piston head 112a closes the opened fourth fluid connection 114d so that the piston 112 assumes a defined position.
- the coupling rod 3 is thus deflected in a targeted manner.
- the position of the fluid connections 114a-d and the flow-related opening or closing of the fluid connections 114a-d can be approached in a targeted manner with the pneumatic lifting cylinder.
- a step-by-step deflection of the coupling rod 3 over the entire stroke of the lifting cylinder 110 can also take place step-by-step, in that the fluid connections 114a-d are appropriately opened and closed one after the other in a controlled manner.
- a fluid outlet 114a-d or a plurality of fluid outlets 114a-d can be opened or closed in terms of flow simultaneously or in series using the associated valves, a movement of the piston 112 of the lifting cylinder 110 can be controlled as required.
- pneumatic lifting cylinders with larger stroke paths can also be used here, since the piston 112 is positioned in a targeted manner on the basis of the fluid outlets 114a-d.
- a gradual deflection of the coupling rod 3, which is directly connected to the piston rod 112b, is thus possible.
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Description
Die Erfindung betrifft ein Kupplungssystem für ein Schienenfahrzeug, insbesondere zur pneumatischen Auslenkung einer Mittelpufferkupplung für Schienenfahrzeuge gemäß dem Oberbegriff des unabhängigen Patentanspruchs 1.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
Ein System zur Auslenkung einer Kupplungsvorrichtung ist beispielsweise aus der
Die hierzu notwendigen Stellglieder bzw. Aktoren werden gemäß dem Stand der Technik vornehmlich als hydraulische Systeme ausgeführt, um eine schnelle und präzise Positionierung des Kupplungskopfes eines Schienenfahrzeuges mit einer beliebigen Auslenkung zu ermöglichen. Jedoch weisen Schienenfahrzeuge nur in seltenen Fällen Hydrauliksysteme auf. Die notwendigen Systemkomponenten, wie z.B. hydraulische Pumpen, Druckspeicher und Überdruckventile, müssen zusätzlich in die Infrastruktur des Schienenfahrzeuges integriert werden, um eine seitliche Auslenkung des Kupplungskopfes zu ermöglichen. Weiterhin stellt der Einsatz von Hydraulikflüssigkeiten wie beispielsweise Öl einen wesentlichen Risikofaktor im Brandfall dar.According to the state of the art, the actuators or actuators required for this are primarily designed as hydraulic systems in order to enable the coupling head of a rail vehicle to be positioned quickly and precisely with any deflection. However, rail vehicles only rarely have hydraulic systems. The necessary system components, such as hydraulic pumps, pressure accumulators and pressure relief valves, must also be integrated into the infrastructure of the rail vehicle in order to enable the coupling head to be deflected to the side. Furthermore, the use of hydraulic fluids such as oil represents a major risk factor in the event of a fire.
Hingegen bedingt der Einsatz von pneumatischen Systemlösungen kein zusätzliches Risiko im Betrieb eines Schienenfahrzeuges. Die Kompressibilität von gasförmigen Arbeitsmedien bzw. Fluiden bedingt hierbei eine schnelle aber schlagartige und mit undefinierter Kraft eingeleitete Bewegung. Die Positionierung des Kupplungskopfes beim Vor-Auslenken der Kupplungsstange ist demzufolge schwierig einzustellen und ungenau.In contrast, the use of pneumatic system solutions does not entail any additional risk in the operation of a rail vehicle. The compressibility of gaseous working media or fluids causes a rapid but sudden movement that is initiated with undefined force. The positioning of the coupling head during the forward deflection of the coupling rod is therefore difficult to adjust and imprecise.
Der vorliegenden Erfindung liegt die Aufgabe zugrunde, ein Kupplungssystem zur Verfügung zu stellen, das eine einfache, kosteneffiziente und risikoarme Integration in ein Schienenfahrzeug ermöglicht. Ferner soll eine feinstufige (Vor-)Auslenkung des Kupplungskopfes einer Kupplungsvorrichtung ermöglicht werden.The present invention is based on the object of providing a coupling system which enables simple, cost-effective and low-risk integration into a rail vehicle. Furthermore, a finely stepped (pre-) deflection of the coupling head of a coupling device should be made possible.
Diese Aufgabe wird durch ein Kupplungssystem gemäß dem unabhängigen Anspruch 1 gelöst. Weitere bevorzugte Ausführungsformen sind in den abhängigen Patentansprüchen angegeben.This object is achieved by a clutch system according to
Gemäß dem unabhängigen Patentanspruch 1 weist das erfindungsgemäße Kupplungssystem für ein Schienenfahrzeug einen Lagerbock auf, der an dem Schienenfahrzeug anordbar ist, eine Kupplungsstange, die an ihrem ersten Ende über eine gelenkige Verbindung mit dem Fahrzeug verbindbar ist, einen Kupplungskopf, der an dem zweiten Ende der Kupplungsstange angeordnet ist, welches im montierten Zustand dem Schienenfahrzeug abgewandt ist, und eine Aktorvorrichtung, die seitlich der Kupplungsstange angeordnet ist. Die Aktorvorrichtung ist mit dem Schienenfahrzeug verbindbar. Vorzugsweise ist die Verbindung zwischen Aktorvorrichtung und Schienenfahrzeug als ein Festlager ausgestaltet. Vorteilhafterweise ist die Aktorvorrichtung somit gegen das Schienenfahrzeug bzw. dessen Rahmen bzw. dessen Fahrgestell abgestützt, um eine Relativbewegung der Kupplungsstange mit dem Kupplungskopf gegenüber dem Schienenfahrzeug zu ermöglichen.According to
Die erfindungsgemäße Aktorvorrichtung ist in Bezug auf die Kupplungsstange einseitig angeordnet. In dieser Anordnung liegt der Vorteil begründet, dass der Schwenkbereich der Kupplungsstange beim Auslenken, insbesondere in seitlicher Richtung, durch die Aktorvorrichtung nicht eingeschränkt wird.The actuator device according to the invention is arranged on one side with respect to the coupling rod. This arrangement has the advantage that the pivoting range of the coupling rod when it is deflected, in particular in a lateral direction, is not restricted by the actuator device.
Im Sinne der vorliegenden Erfindung ist unter der Auslenkung der Kupplungsstange stets die Rotation der Kupplungsstange um eine Drehachse zu verstehen, sodass der Kupplungskopf eine zweckmäßige (Vor-)Auslenkung erfährt und das Verbinden bzw. das Koppeln zweier gegenüberstehender Schienenfahrzeuge ermöglicht wird. Zur Auslenkung der Kupplungsstange mit dem Kupplungskopf, insbesondere einer sogenannten Mittelpufferkupplung, erfolgt die Rotation der Kupplungsstange stets um eine Drehachse, die durch die gelenkige Verbindung zwischen Kupplungsstange und Schienenfahrzeug bzw. Lagerbock verläuft. Sofern der Kupplungskopf über die Kupplungsstange hinreichend auslenkbar ist, können zwei sich gegenüberstehende Schienenfahrzeuge anhand des Greifbereiches der Mittelpufferkupplung miteinander gekoppelt werden. Die Auslenkung der Kupplungsvorrichtung ist somit insbesondere als eine Vor-Auslenkung zu verstehen, sodass das gegenseitige Finden der einander entgegengerichteten Kupplungsvorrichtungen ermöglicht wird.In the context of the present invention, the deflection of the coupling rod is always to be understood as the rotation of the coupling rod about an axis of rotation, so that the coupling head experiences an appropriate (pre-) deflection and the connection or coupling of two opposing rail vehicles is made possible. To deflect the coupling rod with the coupling head, in particular a so-called central buffer coupling, the coupling rod is always rotated about an axis of rotation that runs through the articulated connection between the coupling rod and the rail vehicle or bearing block. If the coupling head can be sufficiently deflected via the coupling rod, two rail vehicles facing each other can be coupled to one another using 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 it is possible to find the coupling devices opposing one another.
Die Aktorvorrichtung weist einen pneumatischen Hubzylinder auf, sodass die Kupplungsstange an ihrem zweiten Ende mit dem Kupplungskopf in zwei entgegengesetzte Richtungen auslenkbar ist. Der Einsatz eines pneumatischen Hubzylinders bedingt den Vorteil, dass das Fluid bzw. Arbeitsfluid, im Gegensatz zu Hydraulikflüssigkeiten wie Öl, kein zusätzliches Risiko, beispielsweise im Brandfall, darstellt. Vielmehr können Medien wie Luft oder andere Gas eingesetzt werden, die weitere vorteilhafte Eigenschaften aufweisen. Unter anderem kann ein schwer entzündliches Arbeitsfluid gewählt werden, um das Gefahrenpotential im Brandfall weiter zu senken.The actuator device has a pneumatic lifting cylinder, so that the coupling rod can be deflected 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, does not pose any additional risk, for example in the event of a fire. Rather, media such as air or other gas can be used which have further advantageous properties. Among other things, a poorly flammable working fluid can be selected in order to further reduce the hazard potential in the event of a fire.
Ferner weist die Infrastruktur von Schienenfahrzeugen pneumatische Systeme auf, sodass keine zusätzlichen Komponenten, wie z.B. Druckspeicher, pneumatische Pumpen zur Bereitstellung eines komprimierten Arbeitsfluids oder Überdruckventile, notwendig werden. Vielmehr sind die bereits im Schienenfahrzeug integrierten Komponenten auch zur Versorgung der Aktorvorrichtung mit Arbeitsfluid gemäß der vorliegenden Erfindung einsetzbar. Somit kann die Infrastruktur bzw. die Anzahl an Systemkomponenten, z.B. gegenüber einer hydraulischen Vorrichtung zur Auslenkung der Kupplungsstange, reduziert werden.Furthermore, the infrastructure of rail vehicles has pneumatic systems, so that no additional components, such as pressure accumulators, pneumatic pumps for providing a compressed working fluid or pressure relief valves, are 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. In this way, the infrastructure or the number of system components, e.g. compared to a hydraulic device for deflecting the coupling rod, can be reduced.
Gemäß der vorliegenden Erfindung ist die Kupplungsstange anhand der Aktorvorrichtung in zwei entgegengesetzte Richtungen auslenkbar. Somit ist pro Kupplungsvorrichtung bzw. pro Kupplungsstange eine einzige Aktorvorrichtung ausreichend, um die zweckmäßige Verwendung eines Schienenfahrzeuges zu ermöglichen. Die Anzahl an Komponenten zur Auslenkung der Kupplungsstange mit dem Kupplungskopf wird reduziert. Neben einer reduzierten Ausfallwahrscheinlichkeit kann somit eine kosteneffiziente Herstellung sowie Instandhaltung gewährleistet werden.According to the present invention, the coupling rod can be deflected in two opposite directions with the aid of the actuator device. Thus is per coupling device or a single actuator device per coupling rod is sufficient to enable the appropriate use of a rail vehicle. The number of components for deflecting the coupling rod with the coupling head is reduced. In addition to a reduced probability of failure, cost-efficient production and maintenance can be guaranteed.
Die Auslenkung der Kupplungsstange durch den pneumatischen Hubzylinder erfolgt insbesondere schrittweise. Vorteilhafterweise ist es somit möglich, eine gewünschte Auslenkung der Kupplungsstange in mehrere Teilbewegungen zu untergliedern. In der Folge ist ein pneumatischer Hubzylinder einsetzbar, der einen kleineren maximalen Hubweg aufweist. Die Positioniergenauigkeit eines pneumatischen Hubzylinders ist auf diese Weise optimierbar, da der Einfluss der Kompressibilität des gasförmigen Arbeitsfluids reduziert wird. Der grundlegende Nachteil eines pneumatischen Hubzylinders gegenüber z.B. einem hydraulischen Hubzylinder ist in der Folge durch den Einsatz kleinerer Hubzylinder verringerbar. Dabei ist die schrittweise Auslenkung der Kupplungsstange mit dem Kupplungskopf hinreichend genau und schnell, sodass einander gegenüberstehende Schienenfahrzeuge anhand des Greifbereiches des Kupplungskopfes miteinander verbindbar sind.The deflection of the coupling rod by the pneumatic lifting cylinder takes place, in particular, step by step. It is thus advantageously possible to subdivide a desired deflection of the coupling rod into several 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 fundamental disadvantage of a pneumatic lifting cylinder compared to e.g. a hydraulic lifting cylinder can be reduced by using smaller lifting cylinders. The step-by-step deflection of the coupling rod with the coupling head is sufficiently precise and fast so that rail vehicles opposite one another can be connected to one another by means of the gripping area of the coupling head.
Die Aktorvorrichtung ist gemäß der vorliegenden Erfindung kraftschlüssig und/oder formschlüssig mit der Kupplungsstange verbindbar. Eine Verbindung zwischen der Aktorvorrichtung und der Kupplungsstange kann dauerhaft vorliegen. Jedoch muss die Aktorvorrichtung gemäß der vorliegenden Erfindung nicht kontinuierlich mit der Kupplungsstange verbunden sein.According to the present invention, the actuator device can be connected non-positively and / or positively to the coupling rod. A connection between the actuator device and the coupling rod can be permanent. However, the actuator device according to the present invention does not have to be continuously connected to the coupling rod.
Insbesondere ist hierunter zu verstehen, dass die Aktorvorrichtung in ihrer Gesamtheit nicht zu jedem Zeitpunkt fest mit der Kupplungsstange verbunden sein muss. Entlang der Kraftübertragung innerhalb der Aktorvorrichtung können einzelne Komponenten der Aktorvorrichtung bedarfsweise von der Verbindung mit der Kupplungsstange entkoppelbar sein bzw. mit der Kupplungsstange verbindbar sein. Anhand einer kraftschlüssigen und/oder formschlüssigen Verbindung ist folglich eine Kraftübertragung durch die Aktorvorrichtung auf die Kupplungsstange herstellbar. So kann eine Auslenkung der Kupplungsstange bedarfsweise erzielt werden.In particular, this is to be understood as meaning that the actuator device in its entirety does not have to be permanently connected to the coupling rod at all times. Along the power transmission within the actuator device, individual components of the actuator device can, if necessary, be decoupled from the connection to the coupling rod or can be connected to the coupling rod. A force transmission through the actuator device to the coupling rod can consequently be established on the basis of a force-fit and / or form-fit connection. A deflection of the coupling rod can thus be achieved as required.
Gemäß einer Ausführungsform der vorliegenden Erfindung weist der Hubzylinder ein Zylindergehäuse auf, das mit einem ersten Fluidanschluss und einem zweiten Fluidanschluss versehen ist. Der erste und der zweite Fluidanschluss sind als Fluidzulauf und/oder Fluidablauf einsetzbar. Insbesondere ist der Hubzylinder als ein doppeltwirkender Hubzylinder ausgestaltet. Vorteilhafterweise ist mit dem Hubzylinder eine Bewegung in beide Richtungen entlang der Längsachse des Hubzylinders bedarfsweise ausführbar. Somit kann eine beliebige Position des Hubzylinders in gesteuerter bzw. geregelter Form mit hoher Genauigkeit angefahren werden.According to one embodiment of the present invention, the lifting cylinder has a cylinder housing which is provided with a first fluid connection and a second fluid connection. The first and the second fluid connection can be used as a fluid inlet and / or fluid outlet. In particular, the lifting cylinder is designed as a double-acting lifting cylinder. A movement in both directions along the longitudinal axis of the lifting cylinder can advantageously be carried out with the lifting cylinder as required. Any position of the lifting cylinder can thus be approached in a controlled or regulated manner with high accuracy.
In einer weiteren Ausführungsform weist der Hubzylinder eine Grundposition auf, bei der sich ein Kolbenboden eines Kolbens des Hubzylinders in einer Mittelposition befindet, sodass der Kolben in beiden axialen Richtungen des Hubzylinders bewegbar ist. Vorteilhafterweise stellt die Grundposition des Hubzylinders den Zustand dar, aus dem eine Bewegung des Kolbens erfolgt, um eine Auslenkung der Kupplungsstange zu erzielen. Die Mittelposition des Kolbenbodens ist entsprechend vorzugsweise in der längsseitigen Mitte des Zylindergehäuses vorgesehen. Aus der Grundposition ist der Hubzylinder bzw. der Kolben bedarfsweise in beide Richtungen entlang der Längsachse des Hubzylinders verfahrbar. Erfindungsgemäß weist die Aktorvorrichtung ein Gehäuse auf, in dem ein Schlitten angeordnet und mit dem Hubzylinder derart verbunden ist, dass der Schlitten bei Bewegung des Kolbens gegenüber dem Gehäuse in axialer Richtung des Hubzylinders verschiebbar ist. Der Hubzylinder ist an einer ersten Seite mit dem Gehäuse und das Gehäuse wiederum mit dem Schienenfahrzeug verbunden. Die Aktorvorrichtung ist somit gegen das Schienenfahrzeug bzw. dessen Rahmen bzw. dessen Fahrgestell abgestützt. Der Schlitten ist mit dem Kolben des Hubzylinders verbunden. Vorteilhafterweise ist eine Relativbewegung des Schlittens gegenüber dem Schienenfahrzeug und dem Gehäuse der Aktorvorrichtung durch die Bewegung des Kolbens erzeugbar. Somit ist der Schlitten in beide Bewegungsrichtungen des Kolbens in Richtung der Längsachse des Hubzylinders bewegbar. Hierbei gleitet der Schlitten innerhalb des Gehäuses der Aktorvorrichtung, welches vorzugsweise eine entsprechende Führung für den Schlitten aufweist. Insbesondere kann das Gehäuse den Schlitten teilweise oder vollständig umgeben, sodass eine geführte, relative Bewegung des Schlittens in dem Gehäuse in axialer Richtung des Hubzylinders möglich ist. Weiterhin kann in dem Gehäuse wenigstens ein Anschlag vorgesehen sein. So ist ein maximaler Verfahrweg des Schlittens gegenüber dem Gehäuse bzw. dem Schienenfahrzeug unabhängig vom Hubzylinder in wenigstens einer Richtung begrenzbar. Erfindungsgemäß weist die Aktorvorrichtung eine Zahnstange auf, die in dem Gehäuse der Aktorvorrichtung verschiebbar angeordnet ist. Somit ist die Zahnstange entlang der beiden axialen Richtungen des Hubzylinders anhand des Gehäuses geführt. Ferner wird durch Zähne bzw. der Zahneingriffe ein bedarfsweiser Formschluss und/oder Kraftschluss ermöglicht, sodass eine Verschiebung in axialer Richtung ausführbar ist. Nach einer ersten Verschiebung der Zahnstange in dem Gehäuse ist der Formschluss und/oder Kraftschluss mit den Zähnen bzw. den Zahneingriffen lösbar. Die Zahnstange verbleibt in ihrer Position. Bei Wiederherstellung eines Formschlusses und/oder Kraftschlusses sind eine zweite und gegebenenfalls weitere Verschiebungen der Zahnstange in dem Gehäuse durchführbar.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 can be moved in both axial directions of the lifting cylinder. The basic position of the lifting cylinder advantageously represents the state from which a movement of the piston takes place in order to achieve a deflection of the coupling rod. The central position of the piston head is accordingly preferably provided in the longitudinal center of the cylinder housing. If necessary, the lifting cylinder or the piston can be moved in both directions along the longitudinal axis of the lifting cylinder from the basic position. According to the invention, the actuator device has a housing in which a slide is arranged and connected to the lifting cylinder in such a way that the slide can be displaced in the axial direction of the lifting cylinder when the piston moves relative to the housing. The lifting cylinder is connected on a first side to the housing and the housing is in turn connected to the rail vehicle. The actuator device is thus supported against the rail vehicle or its frame or its chassis. The slide is connected to the piston of the lifting cylinder. A relative movement of the slide with respect to the rail vehicle and the housing of the actuator device can advantageously be generated by the movement of the piston. The slide can thus be moved in both directions of movement of the piston in the direction of the longitudinal axis of the lifting cylinder. Here, the carriage slides within the housing of the actuator device, which preferably has a corresponding guide for the carriage. In particular, the housing can partially or completely surround the slide, so that a guided, relative movement of the slide in the housing is possible in the axial direction of the lifting cylinder. Furthermore, at least one stop can be provided in the housing. Thus, a maximum travel path of the slide relative to the housing or the rail vehicle can be limited in at least one direction independently of the lifting cylinder. According to the invention, 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 by means of the housing. Furthermore, a form fit and / or force fit as required is made possible by teeth or the tooth engagements, so that a shift in the axial direction can be carried out. After a first displacement of the rack in the housing, the form fit and / or force fit with the teeth or the tooth engagements can be released. The rack remains in its position. When a form fit and / or force fit is restored, a second and, if necessary, further displacements of the toothed rack in the housing can be carried out.
Vorzugsweise greift die Zahnstange kraftschlüssig und/oder formschlüssig in die Kupplungsstange ein. Indem die Zahnstange in dem Gehäuse der Aktorvorrichtung verschiebbar ist, wird über die Verschiebung der Zahnstange somit eine Auslenkung der Kupplungsstange ermöglicht.The toothed rack preferably engages with the coupling rod in a force-fitting and / or form-fitting manner. Since the toothed rack can be displaced in the housing of the actuator device, the displacement of the toothed rack enables the coupling rod to be deflected.
Gemäß dieser Ausführungsform ist die Aktorvorrichtung mit der Kupplungsstange verbindbar, indem innerhalb der Aktorvorrichtung ein Formschluss und/oder Kraftschluss mit der Zahnstange herstellbar ist. Ferner ist eine Verbindung zwischen der Kupplungsstange und der Aktorvorrichtung im Sinne der vorliegenden Erfindung lösbar, indem innerhalb der Aktorvorrichtung eine formschlüssige und/oder kraftschlüssige Verbindung mit der Zahnstange gelöst wird. Somit ist die Aktorvorrichtung wenigstens teilweise von der Kupplungsstange entkoppelbar. Erfindungsgemäß ist die Aktorvorrichtung mit einer drehbar gelagerten ersten Klinke und einer drehbar gelagerten zweiten Klinke in dem Schlitten versehen. Ferner ist eine Rampe in dem Gehäuse vorgesehen, auf der die erste Klinke und die zweite Klinke gleitend verschiebbar sind. Erfolgt eine Relativbewegung des Schlittens gegenüber dem Gehäuse der Aktorvorrichtung, werden die Klinken mit dem Schlitten mitgeführt und gegenüber der Rampe, auf der sie aufliegen und gegen die sie mittels einer Druckfeder gepresst werden, verschoben.According to this embodiment, the actuator device can be connected to the coupling rod in that a form fit and / or force fit with the rack can be produced within the actuator device. Furthermore, a connection between the coupling rod and the actuator device can be released in the sense of the present invention by releasing a positive and / or non-positive connection with the rack within the actuator device. The actuator device can thus be at least partially decoupled from the coupling rod. According to the invention, the actuator device is provided with a rotatably mounted first pawl and a rotatably mounted second pawl in the slide. Furthermore, a ramp is provided in the housing, on which the first pawl and the second pawl are slidably displaceable. If there is a relative movement of the carriage with respect to the housing of the actuator device, the pawls are carried along with the carriage and with respect to the ramp on which they are and against which they are pressed by means of a compression spring, displaced.
Bei Bewegung des Schlittens ist eine formschlüssige Verbindung zwischen dem Schlitten und der Zahnstange mittels der ersten Klinke oder der zweiten Klinke herstellbar. Abhängig von der Bewegungsrichtung des Schlittens gleitet die erste Klinke oder die zweite Klinke von der Rampe ab und greift in die Zähne der Zahnstange ein. Die andere Klinke verbleibt auf der Rampe, wodurch ein Eingriff auf die Zahnstange verhindert wird. Mit fortlaufender Bewegung des Kolbens des Hubzylinders bzw. des Schlittens ist die Zahnstange auf diese Weise mitführbar. Eine Verschiebung der Zahnstange kann in beliebigem Umfang erfolgen, bis der Kolben bzw. der Schlitten den jeweiligen Anschlag des Hubzylinders bzw. des Gehäuses erreicht. Ferner ist ein Ende der Bewegung erreicht, bevor auch die andere Klinke von der Rampe abgleitet.When the carriage moves, a positive connection between the carriage and the rack can be established by means of the first pawl or the second pawl. 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 pawl remains on the ramp, which prevents engagement with the rack. As the piston of the lifting cylinder or the slide continues to move, the rack can be carried along in this way. The rack can be shifted to any extent until the piston or the slide reaches the respective stop of the lifting cylinder or the housing. Furthermore, one end of the movement is reached before the other pawl also slides off the ramp.
Im Sinne der vorliegenden Erfindung ist die Schrittweite pro Bewegungsablauf der Aktorvorrichtung anhand der Zähne bzw. Eingriffe der Zahnstange einstellbar. Ebenso ist der Hubweg, insbesondere der maximale Hubweg, des pneumatischen Hubzylinders variierbar, um die Schrittweite zu adaptieren. Hierbei ist zu berücksichtigen, dass eine Schrittweite pro Bewegungsablauf gemäß der vorliegenden Ausführungsform dem halben Hubweg, aus der Grundposition bis zum Anschlag des Hubzylinders, entspricht. Ferner ist zu berücksichtigen, dass mit zunehmendem Hubweg bzw. zunehmender Schrittweite die Positioniergenauigkeit des pneumatischen Hubzylinders und somit des pneumatisch auslenkbaren Kupplungssystems reduziert wird.In the context of the present invention, the step size per movement sequence of the actuator device can be set on the basis of the teeth or engagements of the rack. The stroke path, in particular the maximum stroke path, of the pneumatic lifting cylinder can also be varied in order to adapt the step size. It must be taken into account here that one step size per movement sequence according to the present embodiment corresponds to half the stroke path from the basic position to the stop of the lifting cylinder. It should also be taken into account that the positioning accuracy of the pneumatic lifting cylinder and thus of the pneumatically deflectable coupling system is reduced with increasing stroke distance or increasing step size.
Eine weitere Ausführungsform der vorliegenden Erfindung sieht die Aktorvorrichtung mit einer Rückholfeder vor, die mit dem Gehäuse und dem Schlitten derart verbunden ist, dass die Aktorvorrichtung in die Grundposition rückstellbar ist. In der Grundposition liegen die erste Klinke und die zweite Klinke auf der Rampe auf. Vorzugsweise ist die Rückholfeder derart in der Aktorvorrichtung positioniert, dass die Rückholfeder jeweils teilweise in einer Nut des Schlittens und in einer Nut des Gehäuses angeordnet ist. Bei einer relativen Bewegung des Schlittens gegenüber dem Gehäuse wird die Feder auf diese Weise komprimiert und eine Rückstellkraft gespeichert. Zur Positionierung der Rückholfeder ist an den Endseiten der Rückholfeder vorzugsweise ein Zentriermittel bzw. Positioniermittel vorgesehen.Another embodiment of the present invention provides the actuator device with a return spring which is connected to the housing and the slide in such a way that the actuator device can be reset to the basic position. In the basic position, the first pawl and the second pawl rest on the ramp. The return spring is preferably positioned in the actuator device in such a way that the return spring is partially arranged in a groove of the slide and in a groove of the housing. When the slide moves relative to the housing, the spring is compressed in this way and a restoring force is stored. To position the return spring is on the end sides a centering means or positioning means is preferably provided for the return spring.
Vorteilhafterweise ist die Aktorvorrichtung bzw. der Schlitten zusammen mit dem Kolben durch die Rückholfeder in eine Grundposition rückstellbar, wenn der pneumatische Hubzylinder entspannt wird. Ferner wird durch die Rückholfeder bzw. das Zurückstellen der Aktorvorrichtung in die Grundposition ein Formschluss und/oder Kraftschluss des Schlittens mit der Zahnstange, über die beiden Klinken, automatisch gelöst. Die Zahnstange verbleibt bei der Rückstellung der Aktorvorrichtung vorteilhafterweise in ihrer zuvor eingestellten Position.Advantageously, the actuator device or the slide can be returned to a basic position together with the piston by the return spring when the pneumatic lifting cylinder is relaxed. Furthermore, a form fit and / or force fit of the slide with the rack via the two pawls is automatically released by the return spring or the resetting of the actuator device into the basic position. When the actuator device is reset, the toothed rack advantageously remains in its previously set position.
Sofern die Rückholfeder die Aktorvorrichtung in ihre Grundposition zurückfährt, werden die erste Klinke und die zweite Klinke auf die Rampe gezogen. Insbesondere wird die Klinke, die bei der vorhergehenden Bewegung des Schlittens von der Rampe abgeglitten ist, wieder auf die Rampe geführt. So wird der formschlüssige und/oder kraftschlüssige Eingriff der abgeglittenen Klinke in die Zahnstange gelöst. Wenn die Aktorvorrichtung bzw. der Kolben und der Schlitten der Aktorvorrichtung in die Grundposition fahren, verbleibt die Zahnstange folglich an ihrer relativen Position gegenüber dem Gehäuse der Aktorvorrichtung. Eine zuvor erzielte Verschiebung der Zahnstange bleibt erhalten. Folglich bleibt auch eine zuvor eingestellte Auslenkung der Kupplungsstange mit dem Kupplungskopf erhalten.If the return spring moves the actuator device back into its basic position, the first pawl and the second pawl are pulled onto the ramp. In particular, the pawl, which slipped off the ramp during the previous movement of the slide, is guided back onto the ramp. In this way, the positive and / or non-positive engagement of the pawl that has slipped into the rack is released. When the actuator device or the piston and the slide of the actuator device move into the basic position, the toothed rack consequently remains in its relative position with respect to the housing of the actuator device. A previously achieved displacement of the rack is retained. Consequently, a previously set deflection of the coupling rod with the coupling head is also retained.
Wird anschließend eine weitere Bewegung des Kolbens mit dem Schlitten initiiert, gleitet eine der Klinken entsprechend der Bewegungsrichtung von der Rampe ab und greift in die Zahnstange ein, um diese mitzuführen. Nach dem Erreichen der gewünschten Position verfährt die Rückholfeder den Schlitten wieder in die Grundposition. Eine weitere Verschiebung der Zahnstange ist erfolgt. Indem die Verschiebung des Schlittens mit den Klinken in eine Richtung und die nachfolgende Rückstellung in die Grundposition mehrfach hintereinander durchgeführt werden, erfolgt eine schrittweise Verschiebung der Zahnstange um ein gewünschtes Maß. Indem die Zahnstange mit der Kupplungsstange des Schienenfahrzeuges in Eingriff steht, ist durch die Aktorvorrichtung schrittweise eine gewünschte Auslenkung der Kupplungsstange mit dem Kupplungskopf erzielbar.If a further movement of the piston with the slide is then initiated, one of the pawls slides off the ramp in accordance with the direction of movement and engages in the rack in order to carry it along. After the desired position has been reached, the return spring moves the slide back to its home position. Another shift of the rack has taken place. By shifting the slide with the pawls in one direction and then resetting it to the basic position several times in succession, the rack is shifted step-by-step by a desired amount. Since the rack is in engagement with the coupling rod of the rail vehicle, the actuator device can gradually achieve a desired deflection of the coupling rod with the coupling head.
In einer weiteren Ausführungsform weist das Gehäuse der Aktorvorrichtung eine Bremseinheit auf, sodass eine relative Bewegung der Zahnstange gegenüber dem Gehäuse verzögerbar ist. Vorteilhafterweise kann keine freie Bewegung der Zahnstange in dem Gehäuse erfolgen. Insbesondere bei einer Neigung der Fahrstrecke und eine dadurch begründete Schräglage des Schienenfahrzeuges ist auf diese Weise einer unerwünschten Verschiebung der Zahnstange in dem Gehäuse vorbeugbar. Unter anderem kann die Bremseinheit als eine federbelastete Rasteinheit vorgesehen sein. Die federbelastete Rasteinheit greift in die Zahnstange ein. Eine freie Bewegung der Zahnstange in dem Gehäuse wird verzögert.In a further embodiment, the housing of the actuator device has a braking unit, so that a relative movement of the toothed rack with respect to the housing can be delayed. Advantageously, the rack cannot move freely in the housing. In this way, an undesirable displacement of the rack in the housing can be prevented, particularly when the route is inclined and the rail vehicle is inclined as a result. Among other things, the braking unit can be provided as a spring-loaded latching unit. The spring-loaded locking unit engages in the rack. Free movement of the rack in the housing is delayed.
Gemäß einer weiteren Ausführungsform erfolgt die Verzögerung der Zahnstange durch Reibung. Eine derartige Reibbremse kann als eine manuell bedienbare Bremse oder als eine selbstwirkende Bremse oder als eine kontinuierlich wirkende Bremse ausgestaltet sein. Die auf die Zahnstange wirkende Reibkraft ist hierbei derart anzusetzen, dass insbesondere eine unerwünschte freie Bewegung der Zahnstange, z.B. durch die Schwerkraft bei Neigung des Schienenfahrzeuges, verhindert wird. Es besteht der Vorteil, dass eine Position der Zahnstange auch unter der Einwirkung von Schwerkraft gehalten werden kann.According to a further embodiment, the rack is delayed by friction. Such a friction brake can 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 to be set in such a way that, in particular, undesired free movement of the rack, e.g. due to gravity when the rail vehicle is tilted, is prevented. There is the advantage that a position of the rack can also be held under the action of gravity.
Gemäß einer nicht beanspruchten Ausführungsform der vorliegenden Erfindung sind entlang des Zylindergehäuses wenigstens ein erster Fluidauslass und ein zweiter Fluidauslass vorgesehen. Die Fluidanschlüsse sind in diesem Fall bevorzugterweise als Fluidzuläufe einsetzbar.According to an embodiment of the present invention that is not claimed, 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 inlets.
In der Grundposition des Hubzylinders liegen seitlich des Kolbenbodens ein erstes und ein zweites Volumen vor. Bevorzugterweise sind die Fluidauslässe an dem Zylindergehäuse derart angeordnet, dass in der Grundposition des Hubzylinders je ein Fluidauslass pro Volumen vorliegt. Ein Arbeitsfluid ist vorzugsweise beidseitig des Kolbenbodens aus dem jeweiligen Volumen des Hubzylinders über den ersten und/oder zweiten Fluidauslass ausleitbar. Dadurch besteht der Vorteil, die Fluidanschlüsse zur Zuführung von Fluid einsetzen zu können, während die Fluidauslässe zum Ausleiten von Fluid aus dem Zylindergehäuse einsetzbar sind.In the basic position of the lifting cylinder, there is a first and a second volume to the side of the piston head. The fluid outlets are preferably arranged on the cylinder housing in such a way that there is one fluid outlet per volume in the basic position of the lifting cylinder. A working fluid can preferably 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 supplying fluid, while the fluid outlets can be used for discharging fluid from the cylinder housing.
Im Allgemeinen ist ein Fluidauslass keinem der beiden Volumina des Hubzylinders fest zugeordnet. Ein Fluidauslass ermöglicht die Herstellung einer strömungsmäßigen Verbindung zu einem der Volumina in Abhängigkeit von der Position des Kolbens bzw. des Kolbenbodens. Die Fluidauslässe sind abhängig von der Position des Kolbenbodens innerhalb des Zylindergehäuses jeweils dem ersten Volumen oder dem zweiten Volumen zugeordnet. Sofern der Kolbenboden exakt an der Position eines Fluidauslasses steht, wird dieser Fluidauslass durch den Kolbenboden strömungsmäßig verschlossen, sodass der Fluidauslass keinem der beiden Volumina zugeordnet ist. Dann kann kein Fluid aus dem Hubzylinder über diesen verschlossenen Fluidauslass ausströmen.In general, a fluid outlet is not permanently assigned to either of the two volumes of the lifting cylinder. A fluid outlet enables a flow connection to be made to one of the volumes depending on the position of the 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 head within the cylinder housing. If the piston head is exactly at the position of a fluid outlet, this fluid outlet is closed in terms of flow by the piston head, so that the fluid outlet is not assigned to either of the two volumes. Then no fluid can flow out of the lifting cylinder via this closed fluid outlet.
Insbesondere sind die Fluidauslässe zum strömungsmäßigen Ausleiten von gasförmigem Arbeitsfluid aus einem Volumen des Hubzylinders vorgesehen. Gleichfalls ist nicht ausgeschlossen, dass die Fluidauslässe als strömungsmäßige Verbindungen zum Einleiten von Fluid in ein Volumen des Hubzylinders einsetzbar sind. Ebenso kann es vorteilhaft sein, die Fluidanschlüsse zum Ausleiten von Arbeitsfluid aus dem Hubzylinder einzusetzen, insbesondere um den Hubzylinder in eine Endposition bzw. Anschlagsposition zu fahren. Vorteilhafterweise sind mit den Fluidanschlüssen und den Fluidauslässen sämtliche Kombination zum Einleiten und Ausleiten von Fluid in und aus einem Volumen des Hubzylinders darstellbar.In particular, the fluid outlets are provided for discharging gaseous working fluid from a volume of the lifting cylinder. Likewise, it is not excluded that the fluid outlets can be used as flow connections for introducing fluid into a volume of the lifting cylinder. It can also be advantageous to use the fluid connections for discharging working fluid from the lifting cylinder, in particular in order to move the lifting cylinder into an end position or stop position. Advantageously, all combinations 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.
Gemäß dieser Ausführungsform ist der Hubzylinder über die Kolbenstange direkt mit der Kupplungsstange verbunden. Im Sinne der vorliegenden Verbindung ist die Aktorvorrichtung mit der Kupplungsstange formschlüssig und/oder kraftschlüssig verbindbar. Jedoch ist gemäß dieser Ausführungsform vorgesehen, dass eine Verbindung zwischen der Kupplungsstange und der Kolbenstange kontinuierlich vorliegt. Anhand der wenigstens zwei Fluidauslässe ist die Bewegung des Kolbens derart steuerbar, dass pneumatische Hubzylinder mit großen Hubwegen einsetzbar sind.According to this embodiment, the lifting cylinder is connected directly to the coupling rod via the piston rod. In the sense of the present connection, the actuator device can be connected to the coupling rod in a form-fitting and / or force-fitting manner. However, according to this embodiment it is provided that a connection between the coupling rod and the piston rod is continuous. With the aid of the at least two fluid outlets, the movement of the piston can be controlled in such a way that pneumatic lifting cylinders with long stroke paths can be used.
In einer weiteren Ausführungsform der vorliegenden Erfindung sind die Fluidauslässe jeweils mit einem Ventil strömungsmäßig verbunden, sodass ein Ausströmen von Fluid aus dem Zylindergehäuse über wenigstens einen der Fluidauslässe steuerbar ist. Vorteilhafterweise sind die hydrostatischen Druckverhältnisse in den zwei Volumina des Hubzylinders anhand der Fluidanschlüsse, die hierbei als Fluidzulauf verwendet werden, und den Fluidauslässen einstell- und steuerbar. Eine Bewegung des Kolbens des Hubzylinders ist erzeugbar, indem in den Volumina des Zylindergehäuses, beidseitig des Kolbenbodens, unterschiedliche hydrostatisehe Drücke eingestellt werden. Dieses hydrostatische Druckverhältnis ist durch eine Druckerhöhung über die Fluidanschlüsse adaptierbar, oder über das Öffnen wenigstens eines der Ventile, um Arbeitsfluid über den entsprechenden Fluidauslass aus dem Hubzylinder ausströmen zu lassen.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 can be controlled via at least one of the fluid outlets. Advantageously, the hydrostatic pressure conditions in the two volumes of the lifting cylinder can be set and controlled on the basis of the fluid connections, which are used here as a fluid inlet, and the fluid outlets. A movement of the piston of the lifting cylinder can be generated by different hydrostatisehe in the volumes of the cylinder housing, on both sides of the piston head Pressures can be adjusted. This hydrostatic pressure ratio can be adapted by increasing the pressure via 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.
Es ist möglich, eine Bewegung des Kolbens in dem Zylindergehäuse, und somit eine Auslenkung der Kupplungsstange, durch eine hohe hydrostatische Druckdifferenz in den beiden Volumina des Hubzylinders zu erzeugen. Ferner ist es möglich, eine solche Bewegung der Kupplungsstange zu erzeugen, indem bei gleichem Druck in dem ersten und zweiten Volumen des Hubzylinders wenigstens ein Fluidauslass geöffnet wird, der ein Ausströmen von Arbeitsfluid aus einem der Volumina und eine damit verbundene Druckabnahme ermöglicht. Ferner ist es möglich, die Erhöhung des hydrostatischen Drucks in einem Volumen durch das Einleiten zusätzlichen Arbeitsfluids und das Auslassen von Arbeitsfluid aus dem anderen Volumen gleichzeitig auszuführen. Auf diese Weise kann eine optimale Verfahrgeschwindigkeit bei exakter Positionierung der Kupplungsstange im Zuge der Auslenkung erreicht werden.It is possible to generate a movement of the piston in the cylinder housing, and thus a deflection of the coupling rod, by means of a high hydrostatic pressure difference in the two volumes of the lifting cylinder. Furthermore, it is possible to generate such a movement of the coupling rod by opening at least one fluid outlet at the same pressure in the first and second volume of the lifting cylinder, which allows working fluid to flow out of one of the volumes and an associated pressure decrease. Furthermore, it is possible to carry out the increase in the hydrostatic pressure in one volume by introducing additional working fluid and discharging working fluid from the other volume at the same time. In this way, an optimal travel speed can be achieved with exact positioning of the coupling rod in the course of the deflection.
Nach einer weiteren Ausführungsform sind die Fluidauslässe über die Länge des Zylindergehäuses vorzugsweise in gleichem Abstand zueinander angeordnet. Vorteilhafterweise ist somit in der Grundposition der Aktorvorrichtung beidseitig des Kolbenbodens jeweils wenigstens ein Fluidauslass angeordnet. Somit ist eine gezielte Bewegung des Kolbens in beide axialen Richtungen des Hubzylinders möglich.According to a further embodiment, the fluid outlets are preferably arranged at the same distance from one another over the length of the cylinder housing. In the basic position of the actuator device, at least one fluid outlet is advantageously arranged on both sides of the piston head. A targeted movement of the piston in both axial directions of the lifting cylinder is thus possible.
Gemäß einer weiteren Ausführungsform ist eine Bewegung des Kolbens erzeugbar, indem anhand wenigstens eines der Ventile eine strömungsmäßige Verbindung über den zugehörigen Fluidauslass herstellbar ist. Sofern das wenigstens eine Ventil geöffnet wird, strömt aus dem zugeordneten Volumen des Zylindergehäuses das Arbeitsfluid den hydrostatischen Druckverhältnissen entsprechend über den zugehörigen Fluidauslass aus dem Zylindergehäuse aus. Gemäß den hydrostatischen Druckverhältnissen zwischen den beiden Volumina in dem Zylindergehäuse bewegt sich der Kolben in Richtung des kleineren hydrostatischen Drucks. Sobald der Kolbenboden den Fluidauslass, über den Arbeitsfluid aus dem Zylindergehäuse ausströmt, erreicht und diesen Fluidauslass verschließt, kann kein weiteres Fluid aus dem Zylindergehäuse ausströmen. In der Folge kommt es zu einem Druckausgleich zwischen den beiden Volumina des Zylindergehäuses. Der Kolben ist auf vorteilhafter Weise in gedämpfter Form abbremsbar. Ferner ist eine gewünschte Position des Kolbens anhand der Fluidauslässe präzise anfahrbar. Aufgrund der Verbindung zwischen der Kolbenstange und der Kupplungsstange ist auf diese Weise eine Auslenkung der Kupplungsstange erzielbar.According to a further embodiment, a movement of the piston can be generated in that a flow connection via the associated fluid outlet can be established using at least one of the valves. 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 lower hydrostatic pressure.As soon as the piston head 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 . Then it comes to equalize the pressure between the two volumes of the cylinder housing. The piston can advantageously be braked in a damped manner. Furthermore, a desired position of the piston can be precisely approached using 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.
Die Erfindung wird im Folgenden anhand von Ausführungsbeispielen unter Bezug auf die beigefügten schematischen Zeichnungen näher erläutert. Weitere Ausführungsformen des erfindungsgemäßen Gegenstandes sollen im Sinne der vorliegenden Erfindung hierdurch nicht ausgeschlossen sein.The invention is explained in more detail below on the basis of exemplary embodiments with reference to the accompanying schematic drawings. Further embodiments of the subject matter according to the invention are not intended to be excluded by this in the context of the present invention.
Es zeigen schematisch:
- Fig. 1:
- eine erfindungsgemäße Kupplungsvorrichtung für ein Schienenfahrzeug;
- Fig. 2a:
- ein erstes Ausführungsbeispiel einer erfindungsgemäßen Aktorvorrichtung;
- Fig. 2b:
- das erste Ausführungsbeispiel einer Aktorvorrichtung gemäß der vorliegenden Erfindung in der Explosionsdarstellung;
- Fig. 2c:
- das erste Ausführungsbeispiel einer Aktorvorrichtung gemäß der vorliegenden Erfindung in der Seitenansicht;
- Fig. 3a:
- das erste Ausführungsbeispiel einer Aktorvorrichtung gemäß der vorliegenden Erfindung in der Schnittansicht A-A gemäß
Fig. 2c ; - Fig. 3b:
- das erste Ausführungsbeispiel einer Aktorvorrichtung gemäß der vorliegenden Erfindung in der Schnittansicht B-B gemäß
Fig. 2c ; - Fig. 3c:
- das erste Ausführungsbeispiel einer Aktorvorrichtung gemäß der vorliegenden Erfindung in der Detailansicht X-X gemäß
Fig. 3a ; - Fig. 4a-c:
- ein beispielhafter Ablauf zur Erzielung einer Auslenkung der Kupplungsstange mit dem ersten Ausführungsbeispiel einer Aktorvorrichtung gemäß der vorliegenden Erfindung; und
- Fig. 5a-c:
- ein beispielhafter Ablauf zur Erzielung einer Auslenkung der Kupplungsstange mit einem zweiten Ausführungsbeispiel der Aktorvorrichtung, welches nicht Teil der Erfindung ist.
- Fig. 1:
- a coupling device according to the invention for a rail vehicle;
- Fig. 2a:
- a first embodiment of an actuator device according to the invention;
- Fig. 2b:
- the first embodiment of an actuator device according to the present invention in the exploded view;
- Fig. 2c:
- the first embodiment of an actuator device according to the present invention in the side view;
- Fig. 3a:
- the first embodiment of an actuator device according to the present invention in the sectional view AA according to
Figure 2c ; - Fig. 3b:
- the first embodiment of an actuator device according to the present invention in the sectional view BB according to
Figure 2c ; - Fig. 3c:
- the first embodiment of an actuator device according to the present invention in the detailed view XX according to
Fig. 3a ; - Fig. 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, which is not part of the invention.
Seitlich der Kupplungsstange 3 ist eine Aktorvorrichtung 5 angeordnet. Insbesondere ist die Aktorvorrichtung 5 in Bezug auf die Kupplungsstange 3 einseitig positioniert. Die Aktorvorrichtung 5 ist mittels eines Festlagers 6 an dem Schienenfahrzeug 1 oder an dessen Rahmen oder an dessen Fahrgestell angebracht. Ferner greift die Aktorvorrichtung 5 anhand einer Zahnstange 15 bzw. einer Kolbenstange 112b auf die Kupplungsstange 3 ein, sodass eine seitliche Auslenkung der Kupplungsstange 3 mit dem Kupplungskopf 4 möglich ist. Anhand der Aktorvorrichtung 5 ist eine seitliche Auslenkung der Kupplungsstange 3 in zwei Richtungen möglich. Die Kupplungsstange 3 rotiert dabei um eine Drehachse, die durch die gelenkige Verbindung 2a der Kupplungsstange 3 mit dem Lagerbock 2 verläuft.An
Weiterhin weist das Gehäuse 5a an seiner Oberseite einen Ausschnitt auf, durch den der Schlitten 5b hindurchragen kann, sodass der Schlitten 5b mit dem Hubzylinder 10 bzw. dessen Kolbenstange 12b verbindbar ist. Gleichzeitig stellt dieser Ausschnitt des Gehäuses 5a Anschläge zur Beschränkung der translatorischen Bewegung des Schlittens 5b dar.Furthermore, the
Gemäß
Ferner weist die Aktorvorrichtung gemäß
In dem Gehäuse 5a ist die Rampe 17 vorgesehen. Auf der Rampe 17 sind die zwei drehbar gelagerte Klinken 16a; 16b sich gegenüberstehend angeordnet. Die beiden Klinken 16a; 16b sind an dem Schlitten befestigt. Die Druckfeder 19 presst die Klinken 16a; 16b auseinander und gegen die Rampe 17 des Gehäuses 5a. Sofern eine der Klinken 16a; 16b von der Rampe 17 in eine der jeweils danebenliegende Vertiefung abgleitet, greift die abgeglittene Klinke 16a; 16b in die Vertiefung sowie die daran entlang geführte Zahnstange 15 bzw. deren Zahneingriffe ein.The
In
Die
Gemäß
Der Eingriff der zweiten Klinke 16b in die Zahnstange 15 stellt einen Form- und/oder Kraftschluss mit den Zähnen der Zahnstange 15 dar. Während der Schlitten 5b über den Kolben 12 bzw. die Kolbenstange 12b bewegt wird, nimmt der Schlitten 5b die Zahnstange 15 anhand der eingreifenden zweiten Klinke 16b mit.The engagement of the
Sobald der Schlitten 5b den Anschlag des Gehäuses 5a erreicht, ist vorzugsweise auch der Kolben 12 an dem entsprechenden Ende des Hubzylinders 10 angelangt. Indem der verfügbare Hubweg des Hubzylinders 10 anwendungsspezifisch in hinreichender Größe ausgestaltet wird, kann gleichzeitig eine optimierte Positioniergenauigkeit gewährleistet werden. Hingegen führt ein zu groß dimensionierter Hubzylinder zu einer Ungenauigkeit bei der Positionierung des pneumatischen Hubzylinders und somit zu einer ungenauren Auslenkung der Kupplungsstange 3.As soon as the
Die vorgespannte Rückholfeder 18 löst hierzu eine Relativbewegung des Schlittens 5b gegenüber dem Gehäuse 5a aus, sodass der Kolbenboden 12a wieder in die längsseitige Mitte des Zylindergehäuses 11 zurückfährt. Hierbei werden die in dem Schlitten 5b aufgenommenen Klinken 16a; 16b wieder auf die Rampe 17 gezogen, sodass der formschlüssige und/oder kraftschlüssige Eingriff der zweiten Klinke 16b in die Zahnstange 15 aufgelöst wird. Sobald der Kolbenboden 12a wieder mittig in dem Zylindergehäuse 11 steht, sind die beiden Klinken 16a; 16b auf der Rampe 17 angeordnet.To this end, the
Indem beim Zurückfahren des Hubzylinders 10 in die Grundposition, zusammen mit dem Schlitten 5b, der Eingriff der beiden Klinken 16a; 16b gelöst und anhand der Rampe 17 verhindert wird, verbleibt die Zahnstange 15 in der zuvor eingestellten Position. Folglich bleibt eine zuvor eingestellte Auslenkung der Kupplungsstange 3 während des Zurückfahrens der Aktorvorrichtung 5 in die Grundposition erhalten.In that when the lifting
Sofern die Kupplungsstange 3 weiter ausgelenkt werden soll, kann der Prozess gemäß
Das Zylindergehäuse 111 weist zwei Fluidzuläufe 113a; 113b in der Nähe der Endseiten bzw. an den Endseiten auf. Gemäß
Die
In
In der Folge richtet sich der Kolbenboden 112a derart aus, dass ein Gleichgewicht der hydrostatischen Drücke in dem ersten Volumen V1 und in dem zweiten Volumen V2 erreicht ist. Dabei verschließt der Kolbenboden 112a den geöffneten vierten Fluidanschluss 114d, sodass der Kolben 112 eine definierte Position einnimmt. Die Kupplungsstange 3 wird somit gezielt ausgelenkt. In Abhängigkeit von der Position der Fluidanschlüsse 114a-d sowie dem strömungsmäßigen Öffnen oder Schließen der Fluidanschlüsse 114a-d ist auf diese Weise eine bestimmte Position mit dem pneuamtischen Hubzylinder gezielt anfahrbar. Eine schrittweise Auslenkung der Kupplungsstange 3 über den gesamten Hubweg des Hubzylindes 110 kann gleichfalls schrittweise erfolgen, indem die Fluidanschlüsse 114a-d nacheinander in gesteuerter Form entsprechend geöffnet und geschlossen werden.As a result, the
Indem über die Fluidanschlüsse 113a; 113b das jeweilige Volumen V1; V2 mit einem spezifischen pneumatischen Druck beaufschlagt wird, sodass der Kolbenboden 112a ferner in einer gewünschten Position gehalten werden kann. Ferner kann ein Fluidauslass 114a-d oder können mehrere Fluidauslässe 114a-d anhand der zugeordneten Ventile gleichzeitig oder seriell strömungsmäßig geöffnet bzw. strömungsmäßig geschlossen werden, kann eine bedarfsweise Bewegung des Kolbens 112 des Hubzylinders 110 gesteuert werden. Insbesondere sind hierbei auch pneumatische Hubzylinder mit größeren Hubwegen einsetzbar, da eine gezielte Positionierung des Kolbens 112 anhand der Fluidauslässe 114a-d erfolgt. Insbesondere ist somit eine schrittweise Auslenkung der Kupplungsstange 3 möglich, die direkt mit der Kolbenstange 112b in Verbindung steht.By via the
- V1V1
- erstes Volumenfirst volume
- V2V2
- zweites Volumensecond volume
- 11
- SchienenfahrzeugRail vehicle
- 22
- LagerbockBearing block
- 2a2a
- Gelenkige Verbindung an dem LagerbockArticulated connection on the bearing block
- 33
- KupplungsstangeCoupling rod
- 44th
- KupplungskopfCoupling head
- 55
- AktorvorrichtungActuator device
- 5a5a
- Gehäusecasing
- 5b5b
- Schlittensleds
- 1010
- HubzylinderLifting cylinder
- 1111
- ZylindergehäuseCylinder housing
- 1212th
- KolbenPistons
- 12a12a
- KolbenbodenPiston crown
- 12b12b
- KolbenstangePiston rod
- 13a13a
- erster Fluidzulauffirst fluid inlet
- 13b13b
- zweiter Fluidzulaufsecond fluid inlet
- 14a-d14a-d
- FluidauslassFluid outlet
- 1515th
- ZahnstangeRack
- 16a16a
- erste Klinkefirst latch
- 16b16b
- zweite Klinkesecond latch
- 1717th
- Ramperamp
- 1818th
- RückholfederReturn spring
- 1919th
- DruckfederCompression spring
- 2020th
- Aufnahmerecording
Claims (6)
- A coupling system for a rail vehicle (1), comprising a bearing block (2) arrangeable on the rail vehicle (1), a coupling rod (3) connectable at its first end to the vehicle (1) via an articulated connection (2a), a coupling head (4) provided at the second end of the coupling rod (3) facing away from the rail vehicle (1) in the mounted state, and an actuator device (5) arranged laterally to the coupling rod (3) and connectable to the rail vehicle (1),
wherein the actuator device (5) is provided on one side in relation to the coupling rod (3) and comprises a pneumatic lift cylinder (10; 110) such that the coupling rod (3) is deflectable in two opposite directions, in particular incrementally, at its second end comprising the coupling head (4) and the actuator device (5) can be frictionally and/or positively connected to the coupling rod (3),
characterized in that
the actuator device (5) exhibits a housing (5a) in which a carriage (5b) is arranged which is connected to the lift cylinder (10) such that the carriage (5b) can be displaced in the axial direction of the lift cylinder (10) upon the piston (12) moving in relation to the housing (5a), wherein the actuator device (5) is provided with a gear rack (15) displaceably provided in the housing (5a) of the actuator device (5), and wherein the actuator device (5) is provided with a rotatably mounted first pawl (16a) and a rotatably mounted second pawl (16b) in the carriage (5b) as well as with a ramp (17) in the housing (5a) on which the first pawl (16a) and the second pawl (16b) can move such that a positive connection can be established between the carriage (5b) and the gear rack (15) by way of the first pawl (16a) or the second pawl (16b) upon movement of the carriage (5b). - The coupling system according to claim 1,
wherein the lift cylinder (10; 110) exhibits a cylinder housing (11; 111) provided with a first fluid connection (13a; 113a) and a second fluid connection (13b; 113b). - The coupling system according to one of claims 1 or 2,
wherein the lift cylinder (10; 110) has an initial 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) is movable in both axial directions of the lift cylinder (10; 110). - The coupling system according to one of the preceding claims,
wherein the actuator device (5) comprises a return spring (18) which is connected to the housing (5a) and to the carriage (5b) such that the actuator device (5) can be reset into the initial position in which the first pawl (16a) and the second pawl (16b) bear on the ramp (17). - The coupling system according to one of the preceding claims,
wherein the housing (5a) of the actuator device (5) comprises a braking unit so that a relative movement of the gear rack (15) in relation to the housing (5a) can be decelerated. - The coupling system according to claim 5,
wherein the deceleration is effected by friction.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102016104740.6A DE102016104740A1 (en) | 2016-03-15 | 2016-03-15 | Coupling system with pneumatic deflection |
PCT/EP2017/055443 WO2017157738A1 (en) | 2016-03-15 | 2017-03-08 | Coupling system having pneumatic deflection |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3429901A1 EP3429901A1 (en) | 2019-01-23 |
EP3429901B1 true EP3429901B1 (en) | 2021-08-25 |
Family
ID=58264523
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP17709656.7A Active EP3429901B1 (en) | 2016-03-15 | 2017-03-08 | Coupling system having pneumatic deflection |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP3429901B1 (en) |
CN (1) | CN108698619B (en) |
DE (1) | DE102016104740A1 (en) |
WO (1) | WO2017157738A1 (en) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP4178844A1 (en) | 2020-07-09 | 2023-05-17 | Dellner Couplers AB | Device for deflection of a coupler of a train vehicle, coupler of a train, car of a multi-car vehicle and method for coupling a first car of a multi-car vehicle to a second car of a multi-car vehicle |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1719686B1 (en) * | 2005-05-06 | 2007-08-29 | Voith Turbo Scharfenberg GmbH & Co. KG | Separable central buffer coupling with centering device |
SE531773C2 (en) * | 2007-11-29 | 2009-08-04 | Voith Turbo Safeset Ab | Torque transmitting shaft, such as a so-called cardan shaft |
KR20150132243A (en) * | 2013-03-22 | 2015-11-25 | 웹텍 홀딩 코포레이션 | Automated coupler positioning device |
DE102014101986A1 (en) | 2014-02-17 | 2015-08-20 | Voith Patent Gmbh | Coupling device for a car body with a vehicle main frame guided via a drive system |
-
2016
- 2016-03-15 DE DE102016104740.6A patent/DE102016104740A1/en not_active Withdrawn
-
2017
- 2017-03-08 CN CN201780015409.2A patent/CN108698619B/en active Active
- 2017-03-08 EP EP17709656.7A patent/EP3429901B1/en active Active
- 2017-03-08 WO PCT/EP2017/055443 patent/WO2017157738A1/en active Application Filing
Also Published As
Publication number | Publication date |
---|---|
CN108698619B (en) | 2020-09-01 |
CN108698619A (en) | 2018-10-23 |
DE102016104740A1 (en) | 2017-09-21 |
WO2017157738A1 (en) | 2017-09-21 |
EP3429901A1 (en) | 2019-01-23 |
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