WO2017157738A1 - Système d'accouplement à désaxement pneumatique - Google Patents

Système d'accouplement à désaxement pneumatique Download PDF

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Publication number
WO2017157738A1
WO2017157738A1 PCT/EP2017/055443 EP2017055443W WO2017157738A1 WO 2017157738 A1 WO2017157738 A1 WO 2017157738A1 EP 2017055443 W EP2017055443 W EP 2017055443W WO 2017157738 A1 WO2017157738 A1 WO 2017157738A1
Authority
WO
WIPO (PCT)
Prior art keywords
housing
actuator device
coupling
piston
carriage
Prior art date
Application number
PCT/EP2017/055443
Other languages
German (de)
English (en)
Inventor
Ralf Schipmann
Original Assignee
Voith Patent Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Voith Patent Gmbh filed Critical Voith Patent Gmbh
Priority to CN201780015409.2A priority Critical patent/CN108698619B/zh
Priority to EP17709656.7A priority patent/EP3429901B1/fr
Publication of WO2017157738A1 publication Critical patent/WO2017157738A1/fr

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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 the independent patent claim 1.
  • a system for the deflection of a coupling device is known for example from DE 10 2014 101 986 AI.
  • the coupling device has a connected to the car body actuator. This Stel lglied is designed to deflect the coupling rod, if necessary, from the center position. By the coupling device of two opposing rail vehicles are deflected accordingly, thus an automatic coupling of two rail vehicles, for example, in tight bends possible.
  • the actuators or actuators necessary for this purpose are carried out according to the prior art primarily as hydraulic systems in order to enable a quick and precise positioning of the coupling head of a rail vehicle with an arbitrary deflection.
  • rail vehicles rarely have hydraulic systems.
  • the necessary system components such as hydraulic pumps, accumulators and pressure relief valves, must be additionally integrated into the infrastructure of the rail vehicle to allow lateral deflection of the coupling head.
  • hydraulic fluids such as oil is a major risk factor in case of fire.
  • pneumatic system solutions requires no additional risk in the operation of a rail vehicle.
  • the compressibility of gaseous working fluids or fluids in this case causes a rapid but sudden movement initiated with undefined force. The positioning of the coupling head during pre-deflection of the coupling rod is therefore difficult to adjust and inaccurate.
  • the present invention has for its object to provide a coupling system that allows a simple, cost-effective and low-risk integration into a rail vehicle. Furthermore, a fine-stage (pre-) deflection of the coupling head of a coupling device is to be made possible.
  • the rail vehicle coupling system comprises a bearing block disposed on the rail vehicle, a coupling rod connected at its first end to the vehicle via an articulated connection, a coupling head connected to the second end of the rail Coupling rod is arranged, which faces away from the rail vehicle, and an actuator device, which is arranged laterally of the coupling rod.
  • the actuator device is connected to the rail vehicle.
  • the connection between actuator device and rail vehicle is designed as a fixed bearing.
  • the actuator device is thus supported against the rail vehicle or its frame or its chassis in order to allow a relative movement of the coupling rod with the coupling head relative to the rail vehicle.
  • the actuator device according to the invention is arranged on one side with respect to the coupling rod.
  • the pivoting range of the coupling rod during deflection in particular in the lateral direction, is not limited by the actuator device.
  • the deflection of the coupling rod is always understood to mean the rotation of the coupling rod about an axis of rotation, so that the coupling head undergoes an appropriate (pre-) deflection and the connection or coupling of two opposing rail vehicles is made possible.
  • the rotation of the coupling rod always takes place about an axis of rotation which passes through the articulated connection between the coupling rod and rail vehicle or bearing block. If the coupling head is sufficiently deflectable via the coupling rod, two opposing rail vehicles can be coupled to each other on the basis of the gripping area of the central buffer coupling.
  • the deflection of the coupling device is thus to be understood in particular as a pre-deflection, so that the mutual finding of the opposing coupling devices is made possible.
  • the actuator device has a pneumatic lifting cylinder, so that the coupling rod is deflectable at its second end with the coupling head in two opposite directions.
  • a pneumatic lifting cylinder has the advantage that the fluid or working fluid, in contrast to hydraulic fluids such as oil, no additional risk, for example in case of fire, represents. Rather, media such as air or other gas can be used, which have further advantageous properties.
  • a flammable working fluid can be selected to further reduce the risk in the event of fire.
  • the infrastructure of rail vehicles on pneumatic systems so no additional components such.
  • pressure accumulator pneumatic pumps to provide a compressed working fluid or pressure relief valves, necessary.
  • 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.
  • the infrastructure or the number of system components, for. B. compared to a hydraulic device for the deflection of the coupling rod can be reduced.
  • the coupling rod is deflectable in two opposite directions by means of the actuator device.
  • the actuator device per coupling ment device or per coupling rod a single actuator device sufficient to allow the proper use of a rail vehicle.
  • the number of components for the deflection of the coupling rod with the coupling head is reduced. In addition to a reduced probability of failure, a cost-efficient production and maintenance can thus be ensured.
  • the deflection of the coupling rod by the pneumatic lifting cylinder is particularly gradual.
  • a pneumatic lifting cylinder can be used, which has a smaller maximum stroke.
  • the positioning accuracy of a pneumatic lifting cylinder can be optimized in this way, since the influence of the compressibility of the gaseous working fluid is reduced.
  • the basic disadvantage of a pneumatic lifting cylinder against z As a hydraulic lifting cylinder can be reduced in the sequence by the use of smaller lifting cylinder.
  • the stepwise deflection of the coupling rod with the coupling head is sufficiently accurate and fast, so that opposing rail vehicles on the basis of the gripping region of the coupling head are connected to each other.
  • the actuator device can be frictionally and / or positively connected to the coupling rod according to the present invention.
  • a connection between the actuator device and the coupling rod can be permanent.
  • the actuator device according to the present invention need not 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 be decoupled from the connection with the coupling rod or can be connected to the coupling rod along the force transmission within the actuator device. Based on a non-positive and / or positive connection, therefore, a power transmission can be produced by the actuator device on the coupling rod. Thus, a deflection of the coupling rod can be achieved if necessary.
  • the lift cylinder has a cylinder housing provided with a first fluid port and a second fluid port. The first and the second fluid connection can be used as fluid inlet and / or fluid outlet.
  • the lifting cylinder is designed as a double-acting lifting cylinder.
  • a movement in both directions along the longitudinal axis of the lifting cylinder if necessary executable.
  • any position of the lifting cylinder can be approached in controlled or controlled form 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 is movable in both axial directions of the lifting cylinder.
  • the basic position of the lifting cylinder represents the state from which a movement of the piston takes place in order to achieve a deflection of the coupling rod.
  • the center position of the piston crown is correspondingly preferably provided in the longitudinal center of the cylinder housing. From the basic position of the lifting cylinder or the piston is, if necessary, movable in both directions along the longitudinal axis of the lifting cylinder.
  • the actuator device has a housing in which a carriage is arranged and connected to the lifting cylinder in such a way that the carriage is displaceable in the axial direction of the lifting cylinder when the piston moves relative to the housing.
  • the lifting cylinder is connected at a first side to the housing and the housing in turn connected to the rail vehicle.
  • the actuator device is thus supported against the rail vehicle or its frame or its chassis.
  • the carriage is connected to the piston of the lifting cylinder.
  • a relative movement of the carriage relative to the rail vehicle and the housing of the actuator device by the movement of the piston can be generated.
  • the carriage is movable 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 may partially or completely surround the carriage, so that a guided, relative movement of the carriage in the housing. se in the axial direction of the lifting cylinder is possible.
  • at least one stop can be provided in the housing.
  • 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 based on the housing.
  • teeth or tooth engagement enable an interlocking positive connection and / or force fit, so that a displacement in the axial direction can be carried out.
  • the rack engages positively and / or positively in the coupling rod.
  • the rack is displaceable in the housing of the actuator device, thus a displacement of the coupling rod is made possible by the displacement of the rack.
  • the actuator device is connectable to the coupling rod by a positive connection and / or frictional connection with the rack can be produced within the actuator device. Furthermore, a connection between the coupling rod and the actuator device in the context of the present invention is releasable by a positive and / or non-positive connection with the rack is achieved within the actuator device. Thus, the actuator device is at least partially decoupled from the coupling rod.
  • the actuator device is provided with a rotatably mounted first pawl and a rotatably mounted second pawl in the carriage. Further, a ramp is provided in the housing on which the first pawl and the second pawl are slidable. If a relative movement of the carriage relative to the housing of the actuator device, the pawls are carried along with the carriage and opposite the ramp on which they rest and against which they are pressed by means of a compression spring, moved.
  • the step size per movement sequence of the actuator device is adjustable with reference to the teeth or interventions of the rack.
  • the stroke, in particular the maximum stroke of the pneumatic lift cylinder is variable to adapt the step size.
  • a step size per movement according to the present embodiment the half stroke, from the basic position to the stop of the lifting cylinder corresponds.
  • the positioning accuracy of the pneumatic lifting cylinder and thus of the pneumatically deflectable coupling system is reduced.
  • the actuator device with a return spring connected to the housing and the carriage such that the actuator device is recoverable to the home position.
  • the first pawl and the second pawl are on the ramp.
  • the return spring is positioned in the actuator device such that the return spring is in each case partially arranged in a groove of the carriage and in a groove of the housing. In a relative movement of the carriage relative to the housing, the spring is compressed in this manner and stored a restoring force.
  • the end Th the return spring preferably provided a centering or positioning.
  • the actuator device or the carriage is reset together with the piston by the return spring in a basic position when the pneumatic lifting cylinder is relaxed. Further, by the return spring or the return of the actuator device in the basic position, a positive connection and / or adhesion of the carriage with the rack, over the two pawls, automatically released.
  • the rack remains in the provision of the actuator device advantageously in its previously set position.
  • the return spring returns the actuator device to its basic position
  • the first pawl and the second pawl are pulled onto the ramp.
  • the pawl which has slid off the ramp during the previous movement of the carriage, is returned to the ramp.
  • the form-fitting and / or non-positive engagement of the slipped pawl is released into the rack. Consequently, when the actuator device or the piston and the carriage of the actuator device move to the home position, the rack remains at its relative position relative to the housing of the actuator device. A previously achieved displacement of the rack is maintained. Consequently, a previously set deflection of the coupling rod with the coupling head is maintained.
  • the housing of the actuator device has a brake unit, so that a relative movement of the rack relative to the housing can be delayed.
  • the brake unit may be provided as a spring-loaded detent unit.
  • the spring-loaded catch unit engages in the rack. Free movement of the rack in the housing is delayed.
  • the delay of the rack is effected by friction.
  • a friction brake may be designed as a manually operated brake or as a self-acting brake or as a continuously acting brake.
  • the frictional force acting on the rack is in this case to be set such that in particular an undesirable free movement of the rack, z. B. by gravity in inclination of the rail vehicle is prevented.
  • a position of the rack can also be kept 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 feeds.
  • a first volume and a second volume are located laterally of the piston crown.
  • the fluid outlets are arranged on the cylinder housing such that there is one fluid outlet per volume in the basic position of the lifting cylinder.
  • a working fluid can be diverted on both sides of the piston head from the respective volume of the lifting cylinder via the first and / or second fluid outlet. This has the advantage of being able to use the fluid connections for the supply of fluid, while the fluid outlets for discharging fluid from the cylinder housing can be used.
  • a fluid outlet is not assigned to any of the two volumes of the lifting cylinder.
  • a fluid outlet makes it possible to establish a fluid connection to one of the volumes as a function of the position of the fluid Piston or the piston crown.
  • the fluid outlets are assigned to the first volume or the second volume depending on the position of the piston bottom within the cylinder housing. If the piston head is exactly at the position of a fluid outlet, this fluid outlet is fluidly closed by the piston crown so that the fluid outlet is not assigned to either of the two volumes. Then, no fluid can flow out of the lift cylinder via this closed fluid outlet.
  • the fluid outlets are provided for fluidically discharging gaseous working fluid from a volume of the lifting cylinder.
  • the fluid outlets can be used as fluid connections for introducing fluid into a volume of the lifting cylinder.
  • all the combination for introducing and discharging fluid into and out of a volume of the lifting cylinder can be represented with the fluid connections and the fluid outlets.
  • the lifting cylinder is connected via the piston rod directly to the coupling rod.
  • the actuator device can be positively and / or non-positively connected to the coupling rod.
  • a connection between the coupling rod and the piston rod is continuous.
  • the movement of the piston can be controlled in such a way that pneumatic lifting cylinders with large lifting distances can be used.
  • the fluid outlets are each fluidly connected to a valve, so that an outflow of fluid from the cylinder housing via at least one of the fluid outlets is controllable.
  • the hydrostatic pressure conditions in the two volumes of the lifting cylinder can be adjusted and controlled on the basis of the fluid connections, which are used here as the fluid inlet, and the fluid outlets.
  • a movement of the piston of the lifting cylinder can be generated by different hydrostatic pressure in the volumes of the cylinder housing, on both sides of the piston crown. see pressures are set.
  • This hydrostatic pressure ratio can be adapted by increasing the pressure across the fluid connections or by opening at least one of the valves in order to allow working fluid to flow out of the lifting cylinder via the corresponding fluid outlet.
  • the fluid outlets over the length of the cylinder housing are preferably arranged at the same distance from each other.
  • at least one fluid outlet is arranged in the basic position of the actuator device on both sides of the piston crown.
  • a movement of the piston can be generated by means of at least one of the valves, a fluid connection via the associated fluid outlet can be produced. If the at least one valve is opened, the working fluid flows out of the assigned volume of the cylinder housing in accordance with the hydrostatic pressure conditions via the associated fluid outlet from the cylinder housing. According to the hydrostatic pressure ratios between the two volumes in the cylinder housing, the piston moves in the direction of the smaller hydrostatic pressure. As soon as the piston bottom reaches the fluid outlet through which working fluid flows out of the cylinder housing and closes this fluid outlet, no further fluid can flow out of the cylinder housing , In the episode it comes to a pressure equalization between the two volumes of the cylinder housing.
  • the piston is braked in an advantageous manner in a damped form. Furthermore, a desired position of the piston can be precisely approached with reference to the fluid outlets. Due to the connection between the piston rod and the coupling rod, a deflection of the coupling rod can be achieved in this way.
  • FIG. 1 shows a coupling device according to the invention for a rail vehicle
  • FIG. 2a shows a first embodiment of an actuator device according to the invention
  • FIG. 2b shows the exploded view of the first exemplary embodiment of an actuator device according to the present invention
  • Fig. 2c the first embodiment of an actuator device according to the present invention in side view
  • FIG. 3a shows the first embodiment of an actuator device according to the present invention in the sectional view A-A according to FIG. 2c;
  • FIG. 3b shows the first embodiment of an actuator device according to the present invention in the sectional view B-B of FIG. 2c.
  • 3c shows the first embodiment of an actuator device according to the present invention in the detail view XX according to FIG. 3a; 4a-c: an exemplary sequence for achieving a deflection of the coupling rod with the first embodiment of an actuator device according to the present invention; and
  • Fig. 5a-c an exemplary sequence for achieving a deflection of the coupling rod with a second embodiment of the actuator device according to the present invention.
  • Fig. 1 shows an exemplary embodiment of the inventive coupling system for a rail vehicle 1.
  • the coupling system has a bearing block 2.
  • a coupling rod 3 is attached with its first end 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.
  • the actuator device 5 is positioned on one side with respect to the coupling rod 3.
  • the actuator device 5 is mounted by means of a fixed bearing 6 on the rail vehicle 1 or on its frame or on the chassis.
  • the actuator device 5 engages with the aid of a rack 15 or a piston rod 112b on the coupling rod 3, so that a lateral deflection of the coupling rod 3 with the coupling head 4 is possible.
  • a lateral deflection of the coupling rod 3 in two directions is possible.
  • the coupling rod 3 rotates about an axis of rotation which passes through the articulated connection 2a of the coupling rod 3 with the bearing block 2.
  • Fig. 2a illustrates a first exemplary embodiment of the actuator device 5 for a clutch system according to the invention.
  • the actuator device 5 as shown in FIG. 2a a housing 5a.
  • the rack 15 is slidably mounted and guided.
  • the rack 15 has a receptacle 20 for connection to the coupling rod 3 (see Fig. 1).
  • the actuator device 5 has a lifting cylinder 10 which is connected on one side to the housing 5a.
  • the lifting cylinder 10 is connected on its other side via a piston 12, which has a piston rod 12b, with a carriage 5b (not shown in FIG. 2a). represents).
  • the lifting cylinder 10 is designed for this purpose on both sides with suitable receiving devices. According to Fig.
  • the connections between the housing 5a and the lifting cylinder 10 and between the lifting cylinder 10 and piston rod 12b and slide 5b are made and secured by means of a bolt connection.
  • a translational movement of the piston 12 in the lifting cylinder 10 can be transmitted to the carriage 5b, wherein the lifting cylinder 10 is supported against the housing 5a.
  • the housing 5a is in turn connected to the rail vehicle 1 (not shown in Fig. 2a), so that a power transmission to the rail vehicle 1 and its frame or chassis is carried out.
  • FIG. 2b shows the first exemplary embodiment of the actuator device 5 according to the invention in an exploded view.
  • the actuator device 5 has the two-part housing 5a and the carriage 5b, which is displaceably mounted and guided in the housing 5a.
  • a ramp 17 is provided, which is arranged along the guide for the carriage 5b.
  • Recesses are provided on both sides of the ramp 17 which interrupt the guide surface of the housing 5a for the carriage 5b.
  • the ramp 17 opens with falling flanks in the wells.
  • the recesses have steep, in particular vertical, end stops. The recesses project into the underlying guide for the rack 15.
  • the housing 5a has on its upper side a cutout, through which the carriage 5b can protrude, so that the carriage 5b can be connected to the lifting cylinder 10 or its piston rod 12b. At the same time, this section of the housing 5a represents stops for restricting the translational movement of the carriage 5b.
  • a groove for partially receiving a return spring 18 is provided in the carriage 5b.
  • a corresponding groove is provided in the housing 5a (not shown in FIG. 2b) so that the return spring 18 projects partially into the housing 5a and partially into the carriage 5b.
  • the return spring 18 is further provided on both sides with end caps in order to be able to be positioned safely and centered in the grooves of the housing 5a and the carriage 5b. If, based on the lifting cylinder 10, a relative movement of the carriage 5b relative to the housing 5a is initiated, in particular for the purpose of steering the coupling rod 3, the return spring 18 is compressed. As soon as the pneumatic lifting cylinder 10 is relaxed, the carriage 5b and the piston 12 of the lifting cylinder 10 are moved back to the basic position by relaxing the compressed return spring 18.
  • the actuator device has a first pawl 16a and a second pawl 16b, which are pressed apart by a compression spring 19.
  • the pawls 16a; 16b are rotatably mounted connected to the carriage 5b.
  • In the basic position of the actuator device 5 are the two pawls 16a; 16b on the ramp 17 of the housing 5a and are pressed by the compression spring 19 against them.
  • In a translational movement of the carriage 5b relative to the housing 5a in one of the two axial directions of the lifting cylinder 10 slides one of the two pawls 16a; 16b from the ramp 17 in the adjacent recesses.
  • the slipped pawl 16a; 16b protrudes into the guide of the housing 5a for the rack 15 after sliding.
  • the rack 15 has teeth or interventions over at least part of its total length.
  • the teeth of the rack 15 are the pawls 16a; 16b and the ramp 17 in the opposite direction.
  • Fig. 2c shows the first embodiment of the actuator device 5 in a side view.
  • the lifting cylinder 10 is positioned on the top of the housing 5a and is connected thereto.
  • the housing 5a has guides for the carriage 5b and underneath for the rack 15.
  • the return spring 18 protrudes with its diameter partially into the carriage 5b with the groove provided for this purpose and partly into the housing 5a with the groove provided for this purpose.
  • Fig. 3a shows the first embodiment of the actuator device in the sectional view AA of FIG. 2c.
  • Arrows indicate the directions of movement, in which the Aktorvorrichung 5 movable or the rack 15 is displaced.
  • the lifting cylinder 10 with the piston 12 and the cylinder housing 11 is connected via the piston rod 12b with the carriage 5b.
  • a piston head 12a of the piston 12 divides the cylinder housing 11 into a first volume VI and a second volume V2.
  • the lifting cylinder 10 preferably has two fluid inlets 13a; 13b for the first volume VI and the second volume V2 (not shown in FIG. 3a).
  • the lifting cylinder 10 is thus used as a double-acting lifting cylinder.
  • the actuator device 5 is located according to FIG. 3a in its basic position.
  • the ramp 17 is provided. On the ramp 17 are the two rotatably mounted pawls 16a; 16b arranged opposite each other. The two pawls 16a; 16b are attached to the carriage.
  • the compression spring 19 presses the pawls 16a; 16b apart and against the ramp 17 of the housing 5a. If one of the pawls 16a; 16b slides off of the ramp 17 in one of the respective adjacent recess engages the quitglittene pawl 16a; 16b into the depression and the rack 15 guided along it or their tooth engagement.
  • FIG. 3b illustrates the first embodiment of the actuator device 5 for a coupling system according to the invention in the sectional view B-B of FIG. 2c.
  • Fig. 3b the arrangement of the return spring 18 within the grooves in the housing 5a and in the carriage 5b can be seen.
  • the carriage 5b is displaceable in the provided guide within the housing 5a.
  • Fig. 3b shows the ramp 17 with the laterally arranged recesses.
  • the rack 15 protrudes beyond these recesses, as shown in FIG. 3b, so that when a pawl 16a slides; 16b of the ramp 17 in one of the recesses of the engagement of the respective pawl 16a; 16b takes place in the rack or their teeth.
  • FIG. 3c shows a detailed view XX according to FIG. 3a of the first exemplary embodiment of an actuator device 5.
  • the detail view XX represents the first and second pawls 16a; 16b rests on the ramp 17.
  • the compression spring 19 presses the two pawls 16a; 16b apart and against the ramp 17.
  • the ramp 17 on both sides sloping flanks, which open into depressions.
  • a pawl 16a; 16b which has previously been slid from the ramp 17, by a movement of the carriage 5b in the opposite direction again slide onto the ramp 17 or be pulled up.
  • FIGS. 4 a to 4 c illustrate a movement sequence of the exemplary actuator device 5 according to FIG.
  • a movement of the piston 12 to the right takes place on the basis of corresponding hydrostatic pressure conditions in the lifting cylinder 10, that is to say a higher hydrostatic pressure in the first volume VI and a lower hydrostatic pressure in the second volume V2.
  • the piston rod 12b transmits the movement of the lifting cylinder 10 to the carriage 5b, so that it is moved relative to the housing 5a, and thus also relative to the rail vehicle 1.
  • the ramp 17 is arranged in the housing 5a and also carries out no movement.
  • the pawls 16a; 16b are carried along by the carriage 5b moving to the right and slide over the ramp 17 to the right. At the end of the ramp 17, the second pawl 16b slides from the ramp 17 into the adjacent recess and engages in the teeth or the interventions of the toothed rack 15.
  • the first pawl 16a is partially still on the ramp 17th
  • the engagement of the second pawl 16b in the rack 15 is a positive and / or frictional connection with the teeth of the rack 15. While the carriage 5b is moved over the piston 12 and the piston rod 12b, the carriage 5b takes the rack 15 on the basis of the engaging second pawl 16b with.
  • FIG. 4b shows the status of the exemplary actuator device 5 as soon as the carriage 5b has reached the right stop of the housing 5a. After the right pawl 16b has engaged in the rack 15, the rack 15 has been carried along with the movement of the carriage 5b. As a result, a deflection of the coupling rod 3 is achieved, which is connected via the receptacle 20 with the rack 15 (not shown in Fig. 4a-4c).
  • Fig. 4c illustrates the return of the actuator device 5 and the carriage 5b and the piston 12 in the basic position by means of the return spring 18 (not shown in 4a to 4c).
  • the lifting cylinder 10 is relaxed, i. the hydrostatic pressure ratio between the first volume VI and the second volume V2 is dissolved, so that in both volumes VI; V2 the same hydrostatic pressure is present.
  • the return spring 18 Based on the relative movement of the carriage 5b relative to the housing 5a, the return spring 18 has been previously biased or compressed.
  • the lifting cylinder 10 can be relieved by a corresponding reduction of the hydrostatic pressure in the first volume VI.
  • the actuator device 5 is then moved back to the basic position.
  • the preloaded return spring 18 triggers a relative movement of the carriage 5b relative to the housing 5a, so that the piston head 12a returns to the longitudinal center of the cylinder housing 11.
  • the pawls 16a received in the carriage 5b; 16b pulled back onto the ramp 17, so that the positive and / or non-positive engagement of the second pawl 16b is dissolved in the rack 15.
  • the process according to FIGS. 4 a to 4 c can be repeated as often as desired until a maximum deflection of the coupling rod 3 or displacement of the rack 15 is provided. is enough.
  • a stop at an arbitrary position of the stroke of the Huzylinder 10 is not provided according to this first embodiment. It is always carried out a complete movement of the lifting cylinder 10 and the piston 12 from the basic position to the stop of the lifting cylinder 10 and the housing 5a.
  • the (preliminary) deflection of the coupling rod 3 with the coupling head 4 takes place step by step on the basis of the recurrent retraction of the actuator device 5 or of the carriage 5b into the basic position.
  • the illustrated actuator device 5 has the lifting cylinder 110, with the cylinder housing 111 and the piston 112.
  • the piston 112 has the piston head 112a and the piston rod 112b.
  • the piston bottom 112b divides the cylinder housing 111 into the first volume VI and the second volume V2.
  • the piston rod 112b is preferably connected directly to the coupling rod 3 (not shown in Fig. 5a, see Fig. 1). Consequently, a deflection of the piston 112 leads to a direct deflection of the coupling rod 3 in the axial direction of the lifting cylinder 10th
  • the cylinder housing 111 has two fluid inlets 113a; 113b in the vicinity of the end sides or at the end sides. According to FIG. 5a, four fluid outlets 114a; 114b; 114c; 114d are provided, which are preferably distributed at the same distance from one another along the longitudinal direction of the cylinder housing 111. Furthermore, in the basic position of the actuator device 5, the first volume VI and the second volume V2 are preferably assigned an equal number of fluid outlets. Furthermore, valves are provided at the fluid outlets 114a-114d (not shown in FIG. 5a) such that fluid opening of a fluid outlet 114a-114d causes fluid to flow out of the first volume VI and / or the second volume V2 of the cylinder housing 111 , is controllable.
  • FIG. 5 a shows the actuator device 5 or the lifting cylinder 10 in the basic position.
  • the first three fluid outlets 114a-c are fluidly separated while the valve is open at the fourth fluid outlet 114d.
  • a greater hydrostatic pressure is applied than in the second volume V2.
  • the piston 112 moves with the piston head 112a of FIG. 5b to the right.
  • a corresponding deflection of the coupling rod 3 is achieved via the movement of the piston rod 112b.
  • Fig. 5b the state is shown before the piston head 112a, the opened fourth fluid outlet 114d passes and thereby closes.
  • the piston head 112a reaches the fourth fluid outlet and closes it in fluid, so that no further fluid can escape from the second volume V2
  • the hydrostatic pressure in the second volume V2 increases. Accordingly, a movement of the piston 112 is slowed down as soon as the piston head 112a reaches the fluidly opened, fourth fluid outlet and at least partially closes.
  • FIG. 5c shows the state of the actuator device 5 according to the second exemplary embodiment as soon as the piston bottom 112a has exceeded the fluidly connected fluid outlet 114d.
  • this state of the actuator device 5 there is a fluid connection via the fourth fluid outlet 114d to the first volume VI.
  • the second volume V2 is closed in the flow, so that no fluid can flow out of the second volume V2.
  • a hydrostatic pressure is generated in the second volume V2, which counteracts the hydrostatic pressure in the first volume VI.
  • the hydrostatic pressures of the first and second volumes VI; V2 are the same.
  • movement of the piston 12 is decelerated until the hydrostatic pressures in the first volume VI and in the second volume V2 are equal.
  • the piston head 112a is oriented such that a balance of the hydrostatic pressures in the first volume VI and in the second volume V2 is achieved.
  • the piston bottom 112a closes the opened fourth fluid port 114d, so that the piston 112 assumes a defined position.
  • the coupling rod 3 is thus deflected targeted.
  • a stepwise deflection of the coupling rod 3 over the entire stroke of the lifting cylinder 110 can also be carried out stepwise by the fluid ports 114a-d are opened and closed successively in a controlled manner accordingly.
  • a fluid outlet 114a-d or a plurality of fluid outlets 114a-d may be fluidly closed simultaneously or serially based on the associated valves, if desired, movement of the piston 112 of the lift cylinder 110 may be controlled.
  • pneumatic lifting cylinder can be used with larger strokes because a targeted positioning of the piston 112 takes place on the basis of the fluid outlets 114a-d.
  • a stepwise deflection of the coupling rod 3 is thus possible, which is directly connected to the piston rod 112b.

Abstract

L'invention concerne un système d'accouplement pour un véhicule ferroviaire (1), comportant un support de palier (2) monté sur le véhicule ferroviaire (1), une barre d'attelage (3) reliée, à sa première extrémité, au véhicule (1) par l'intermédiaire d'une liaison articulée (2a), une tête d'accouplement (4) située à la seconde extrémité de la barre d'attelage (3), laquelle seconde extrémité est opposée au véhicule ferroviaire (1) ainsi d'un dispositif d'actionnement (5) qui est monté latéralement à la barre d'attelage (3) et est relié au véhicule ferroviaire (1) au moyen d'un palier fixe (6). Le dispositif d'actionnement (5) est prévu d'un seul côté par rapport à la barre d'attelage (3) et présente un vérin de levage (10) pneumatique, de sorte que la barre d'attelage (3) peut être dérivée, en particulier progressivement, à sa seconde extrémité, conjointement avec la tête d'attelage dans deux positions opposées et que le dispositif d'actionnement (5) peut être relié à force et/ou par complémentarité de forme avec la barre d'attelage (3).
PCT/EP2017/055443 2016-03-15 2017-03-08 Système d'accouplement à désaxement pneumatique WO2017157738A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201780015409.2A CN108698619B (zh) 2016-03-15 2017-03-08 具有气动式偏转的联接器系统
EP17709656.7A EP3429901B1 (fr) 2016-03-15 2017-03-08 Système d'accouplement à désaxement pneumatique

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016104740.6A DE102016104740A1 (de) 2016-03-15 2016-03-15 Kupplungssystem mit pneumatischer Auslenkung
DE102016104740.6 2016-03-15

Publications (1)

Publication Number Publication Date
WO2017157738A1 true WO2017157738A1 (fr) 2017-09-21

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PCT/EP2017/055443 WO2017157738A1 (fr) 2016-03-15 2017-03-08 Système d'accouplement à désaxement pneumatique

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EP (1) EP3429901B1 (fr)
CN (1) CN108698619B (fr)
DE (1) DE102016104740A1 (fr)
WO (1) WO2017157738A1 (fr)

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Publication number Priority date Publication date Assignee Title
WO2022008108A1 (fr) 2020-07-09 2022-01-13 Dellner Couplers Ab Dispositif de déviation d'un attelage d'un véhicule ferroviaire, attelage d'un train, wagon d'un véhicule à plusieurs wagons et procédé permettant de coupler un premier wagon d'un véhicule à plusieurs wagons à un second wagon d'un véhicule à plusieurs wagons

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20140284297A1 (en) * 2013-03-22 2014-09-25 Wabtec Holding Corp. Automated Coupler Positioning Device
DE102014101986A1 (de) 2014-02-17 2015-08-20 Voith Patent Gmbh Kupplungsvorrichtung für einen Wagenkasten mit einem über ein Laufwerksystem geführten Fahrzeughauptrahmen

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EP1719686B1 (fr) * 2005-05-06 2007-08-29 Voith Turbo Scharfenberg GmbH & Co. KG Attelage séparable à tampon central avec dispositif de recentrage
SE531773C2 (sv) * 2007-11-29 2009-08-04 Voith Turbo Safeset Ab Vridmomentsöverförande axel, såsom en så kallad kardanaxel

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20140284297A1 (en) * 2013-03-22 2014-09-25 Wabtec Holding Corp. Automated Coupler Positioning Device
DE102014101986A1 (de) 2014-02-17 2015-08-20 Voith Patent Gmbh Kupplungsvorrichtung für einen Wagenkasten mit einem über ein Laufwerksystem geführten Fahrzeughauptrahmen

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2022008108A1 (fr) 2020-07-09 2022-01-13 Dellner Couplers Ab Dispositif de déviation d'un attelage d'un véhicule ferroviaire, attelage d'un train, wagon d'un véhicule à plusieurs wagons et procédé permettant de coupler un premier wagon d'un véhicule à plusieurs wagons à un second wagon d'un véhicule à plusieurs wagons

Also Published As

Publication number Publication date
DE102016104740A1 (de) 2017-09-21
CN108698619A (zh) 2018-10-23
CN108698619B (zh) 2020-09-01
EP3429901A1 (fr) 2019-01-23
EP3429901B1 (fr) 2021-08-25

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