EP3623252B1 - Cylindre d'actionnement pour un frein sur rail et frein sur rail doté d'un cylindre d'actionnement - Google Patents

Cylindre d'actionnement pour un frein sur rail et frein sur rail doté d'un cylindre d'actionnement Download PDF

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Publication number
EP3623252B1
EP3623252B1 EP18194730.0A EP18194730A EP3623252B1 EP 3623252 B1 EP3623252 B1 EP 3623252B1 EP 18194730 A EP18194730 A EP 18194730A EP 3623252 B1 EP3623252 B1 EP 3623252B1
Authority
EP
European Patent Office
Prior art keywords
actuating cylinder
piston rod
piston
traction means
traction
Prior art date
Legal status (The legal status 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 status listed.)
Active
Application number
EP18194730.0A
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German (de)
English (en)
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EP3623252A1 (fr
EP3623252C0 (fr
Inventor
Sebastian A. MONTUA
Sandra CHRIST
Christopher NATHAUS
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Faiveley Transport Witten GmbH
Original Assignee
Faiveley Transport Witten 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
Priority to HUE18194730A priority Critical patent/HUE063004T2/hu
Priority to PL18194730.0T priority patent/PL3623252T3/pl
Priority to EP18194730.0A priority patent/EP3623252B1/fr
Priority to HRP20230819TT priority patent/HRP20230819T1/hr
Priority to ES18194730T priority patent/ES2952201T3/es
Application filed by Faiveley Transport Witten GmbH filed Critical Faiveley Transport Witten GmbH
Priority to RS20230597A priority patent/RS64468B1/sr
Publication of EP3623252A1 publication Critical patent/EP3623252A1/fr
Application granted granted Critical
Publication of EP3623252C0 publication Critical patent/EP3623252C0/fr
Publication of EP3623252B1 publication Critical patent/EP3623252B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B61—RAILWAYS
    • B61H—BRAKES OR OTHER RETARDING DEVICES SPECIALLY ADAPTED FOR RAIL VEHICLES; ARRANGEMENT OR DISPOSITION THEREOF IN RAIL VEHICLES
    • B61H7/00—Brakes with braking members co-operating with the track
    • B61H7/02—Scotch-blocks, skids, or like track-engaging shoes
    • B61H7/04—Scotch-blocks, skids, or like track-engaging shoes attached to railway vehicles

Definitions

  • the present invention relates to an actuating cylinder according to the preamble of claim 1 for a rail brake, in particular a magnetic rail brake, comprising a cylinder housing, a piston guided in the cylinder housing and a piston rod connected to the piston, the piston rod being hollow and having an interior space, with Interior of the piston rod, a traction means is arranged movably guided in an axial direction of the piston rod, wherein the traction means has a holding section at a first end arranged in the interior space, which is designed to prevent the traction means from sliding out of the piston rod.
  • the present invention relates to a rail brake according to claim 13, in particular a magnetic rail brake, comprising a sliding shoe and an actuating cylinder.
  • a rail brake is a brake for a rail vehicle. It includes an iron drag shoe, which is lowered onto a rail to brake the rail vehicle. Friction is created between the rail and the contact shoe moving forward with the rail vehicle, which converts the kinetic energy of the movement into heat until the kinetic energy is consumed.
  • a most commonly used embodiment of a rail brake is a magnetic rail brake.
  • the magnetic rail brake also includes an electromagnet, which is usually arranged in the contact shoe. When current flows through the electromagnet, the contact shoe is pulled onto the rail.
  • Actuating cylinders are usually provided for lowering or raising the contact shoe of the rail brake, on which the contact shoe of the rail brake is suspended.
  • the actuating cylinder When the actuating cylinder is actuated, the rail brake or the contact shoe of the rail brake becomes so wide lowered until, in the case of a magnetic rail brake, the magnetic forces generated by the electromagnets are sufficient to pull the shoe against the rail.
  • the actuating cylinder is attached to the rail vehicle, for example to a bogie.
  • the connection between the actuating cylinder and the contact shoe or a tie rod of the contact shoe is a rigid connection.
  • the contact pad or the tie rod of the contact pad is connected directly to the piston rod of the actuating cylinder. Due to movements of the rail vehicle or due to unevenness of the surface of the rail as well as the retraction and extension of the piston in the actuating cylinder, the magnetic track brake moves relative to the rail vehicle and the actuating cylinder. In order to minimize the relative movements and the resulting material fatigue, rubber-elastic mountings of the actuating cylinder on the rail vehicle are known in the prior art.
  • the piston is designed as a hollow cylinder that is open on one side and is formed without cutting from thin sheet steel or a section of steel wire.
  • the piston also includes a piston head and a wall with a groove in one piece thereon, wherein the piston head can be acted upon hydraulically with braking pressure starting from the interior of the pot, so that an outwardly directed contact surface of the piston head can be pressed against a friction lining, and the piston for the purpose of cooperation with a drive nut a parking brake actuation device additionally has a clutch cone.
  • the GB 2 074 260A discloses an actuating cylinder for a disc brake.
  • the actuating cylinder includes a housing and a hollow, stepped piston disposed in a cylinder bore of the housing.
  • a sleeve is arranged in the hollow piston, which sleeve has a projection formed on the sleeve is positively guided on the stepped piston.
  • a pull rod is actuated via the sleeve.
  • a transverse component of a brake application force can be transmitted to the housing of the actuating cylinder by means of the sleeve arranged in the piston.
  • the braking system includes a piston-cylinder arrangement which is arranged between the vehicle and the brake.
  • the piston and cylinder assembly includes means for raising the brake and supply means for introducing or removing hydraulic fluid into or out of the cylinder.
  • the CH 508 511 B discloses a lifting cylinder piston unit with a cylinder flanged to a base body, a piston and a piston tube for a magnetic track brake, with a bolt which can be pushed into the interior of the piston tube connecting the magnet to the piston.
  • the object of the present invention is to provide an actuating cylinder for a rail brake in which the load or pendulum movement occurring due to relative movements of a contact shoe to be suspended from the actuating cylinder is minimized and for which the necessary free space in a bogie of a rail vehicle for fastening the actuating cylinder is minimized . Furthermore, the present invention is based on the object of providing a rail brake with an actuating cylinder, with which the aforementioned advantages are obtained.
  • an actuating cylinder for a rail brake in particular a magnetic rail brake, according to claim 1 is provided.
  • top”, “bottom”, “side”, “upper end” and “bottom end” always refer to an orientation of the actuating cylinder which corresponds to the orientation of the actuating cylinder when it is arranged on the rail vehicle.
  • terms like “above”, “below”, etc. are such refers to an actuating cylinder which is aligned in such a way that the piston and the piston rod connected to it perform a vertical movement when the actuating cylinder is actuated and that the holding section of the traction means is arranged in the vertical direction above the connection section of the traction means.
  • terms such as “up”, “down” and related terms are appropriate to transfer or adapt.
  • the piston rod is hollow and has an interior space.
  • the interior can be designed as an inner bore of the piston rod.
  • the piston rod is designed to be open on a first side, so that the traction means arranged in the interior is arranged with a first end in the interior of the piston rod and with a second end outside of the interior of the piston rod.
  • the piston rod also has an elongate extension in an axial direction, with the interior space, in particular the inner bore, extending along the axial direction.
  • the pulling means is arranged at least partially, namely with the first end, in the inner space and can be moved back and forth in the piston rod in the axial direction.
  • a holding section is provided, which secures the traction means in the piston rod in the manner of a captive device, so that the traction means is prevented from completely sliding out of the piston rod.
  • the traction means has a connecting section which is designed for connecting or suspending a rail brake, in particular a magnetic rail brake, or a contact shoe of a rail brake.
  • the connection section provided for connection to a rail brake is designed to be movable, in particular deflectable, relative to the holding section.
  • a mobility of the connection section in relation to the holding section means that the connection section can be moved at least in a plane perpendicular to the axial direction of the piston rod in relation to the holding section of the piston rod arranged in the piston rod Can be moved traction means.
  • the movement of the connection section can take place as a change in the orientation of the holding section compared to the orientation of the connection section.
  • the orientation of the area arranged in the interior of the piston rod, or of the first end of the traction means is not changed during a movement or deflection of the area protruding from the interior of the piston rod, or of the second end of the traction means.
  • the connection section preferably only the area protruding from the interior of the piston rod, or the second end of the traction means, experiences a change in alignment.
  • the region of the traction means, more particularly the first end of the traction means, which is arranged in the interior of the piston rod can only be moved in the axial direction and more particularly not or only minimally moved or deflected in a plane perpendicular to the axial direction.
  • connection section can be pivoted, deflected or moved laterally relative to the holding section, in particular perpendicular to the axial direction of the piston rod.
  • a rail brake in particular a magnetic rail brake
  • relative movements of the rail brake, in particular of a contact shoe of the rail brake are possible due to the mobility or deflectability of the connection section in relation to the actuating cylinder, so that pendulum movements, material fatigue and loads on the Actuating cylinder or its suspension can be reduced to a bogie of a rail vehicle.
  • the actuating cylinder When the actuating cylinder is arranged on the rail vehicle, it is preferably attached to a bogie of the rail vehicle.
  • the cylinder housing of the actuating cylinder is fastened to the bogie in a lower area in such a way that an upper area of the actuating cylinder is essentially free-standing.
  • the piston and the piston rod connected to the piston execute a movement in a vertical or perpendicular direction when the actuating cylinder is actuated. If the piston and the piston rod are lowered down, this is also the case in the interior of the Piston rod arranged traction means with lowered.
  • the traction means protrudes downwards out of the hollow piston rod; in particular, the connection section is arranged essentially below the holding section.
  • a tie rod or a sliding shoe of the rail brake can be attached to the connection section, with the holding section arranged in the interior of the hollow piston rod preventing the traction means from sliding out and thus the contact shoe arranged on the connection section of the traction means from falling down.
  • connection section Due to the movability of the connection section in relation to the holding section and thus in relation to the actuating cylinder, pendulum movements of the actuating cylinder and high loads on the connection of the actuating cylinder to the bogie are reduced.
  • the traction means comprises a flexible traction rope, with the holding section being arranged at an upper end of the traction rope and the connection section at a lower end of the traction rope, or that the traction means comprise a rigid and/or inflexible rod, with the traction means being a Has a universal joint or a ball joint, via which the connection section is deflectably connected to the rod and relative to the rod.
  • the traction means thus comprises a traction cable and a holding section and a connection section.
  • the holding section is arranged at an upper end of the traction cable, so that the traction means has a holding section at a first end arranged in the interior of the piston rod.
  • the connection section is arranged and located at the lower end of the traction cable thus located at the second end of the traction means and is arranged outside of the interior of the piston rod.
  • the flexibility of the traction cable allows a sliding shoe of the rail brake arranged on the connection section to perform movements relative to the axial direction of the actuating cylinder, in particular in an approximately horizontal plane.
  • the area of the traction means designed as a traction cable which is arranged outside the interior of the piston rod, can be moved, or deflected, or pivoted relative to the holding section arranged in the interior of the piston rod.
  • an embodiment with a universal joint or ball joint is particularly advantageous.
  • the area of the traction means, in particular the upper end of the traction means, which is arranged in the interior of the hollow piston rod is then designed as a substantially rigid and inflexible rod.
  • the connection section is also designed as a rigid rod. The connection section is connected to the rod via the joint and can be moved, in particular deflected or pivoted, with respect to the rod and thus also with respect to the holding section arranged at the first end of the traction means.
  • the universal joint or ball joint is preferably not arranged in the interior of the piston rod.
  • the inner space preferably has a lower area and an upper area, with a diameter of the lower area of the inner space being smaller than a diameter of the upper area of the inner space, and with more preferably a diameter of the holding section being greater than the diameter of the lower area of the inner space of the piston rod is.
  • the interior of the piston rod is divided into an upper and a lower area, particularly viewed in the axial direction, with the upper area being arranged in the vertical direction above the lower area when the actuating cylinder is arranged on the rail vehicle. If the interior is designed as an inner bore, then the interior has two essentially cylindrical shapes trained areas of the bore, which have different diameters. The sections of the inner bore in the upper area and in the lower area of the inner space are aligned coaxially with one another. Viewed in the axial direction of the piston rod from bottom to top, the interior of the piston rod thus widens at the transition from the lower area to the upper area.
  • a diameter of the holding section is preferably larger than the diameter of the lower area of the interior space, but more preferably at the same time smaller than the diameter of the upper area of the interior space.
  • a piston rod and a traction device are provided which have sufficient stability for holding or suspending a contact shoe of a rail brake.
  • the piston rod can have a smaller outer diameter than the piston rods for actuating cylinders known from the prior art, since the loads on the piston rod are reduced due to the mobility of the connection section relative to the holding section.
  • the traction mechanism is arranged in the piston rod such that it can rotate, preferably about the axial direction.
  • the rotatability of the traction device in the hollow piston rod can be ensured in particular by the traction device, in particular the holding section, having a substantially circular cross-section and being arranged in an inner bore of the piston rod with a likewise substantially circular cross-section.
  • the traction mechanism can rotate in the piston rod, complex relative movements of a contact shoe or a tie rod of a contact shoe of a rail brake relative to the actuating cylinder can also be compensated for, since the traction mechanism can always assume a position by rotating in the piston rod in which the mobility or deflectability of the connection section is opposite the holding section can optimally compensate for the relative movements of the grinding shoe.
  • the holding section is a flange and/or a rotary part, in particular a sleeve, with the holding section having a lower contact surface and with the interior of the piston rod having a contact surface at a transition between the lower area and the upper area has the contact surface.
  • the contact surface is more preferably formed opposite and facing the contact surface of the piston rod.
  • the contact surface is located on an underside of the holding section when the actuating cylinder is arranged on the rail vehicle.
  • the contact surface of the piston rod is formed at the transition between the lower area and the upper area and can be formed in a stepped manner.
  • the contact surface and the contact surface can be aligned essentially horizontally, ie in a plane perpendicular to the axial direction of the piston rod.
  • the bearing surface and the contact surface can be essentially conical and complementary to one another. More preferably, the contact surface and the contact surface can be brought into planar contact with one another.
  • the holding section can either be an integral part of the traction means and can be designed, for example, as a flange formed out of the traction means.
  • the holding section it is also possible for the holding section to be arranged and fastened in the form of a rotating part at the upper end of the traction means.
  • the holding section is designed as a sleeve, this can be placed on an upper end of the traction means and connected to it, so that the holding section becomes part of the traction means.
  • the holding section designed as a rotary part can also have a flange.
  • connection section is a sleeve, in particular a press-in sleeve.
  • connection section By configuring the connection section as a sleeve, it can be connected to the traction mechanism in a simple manner.
  • connection section can also be an integral part of the traction mechanism.
  • the actuating cylinder is a pneumatic cylinder and/or a single-acting cylinder.
  • Pneumatic cylinders in particular, are particularly suitable as actuating cylinders for a rail brake, since pneumatic systems are widespread in rail vehicles and the actuating cylinder can therefore be easily integrated into existing braking systems.
  • the actuating cylinder is designed such that the piston rod connected to the piston is moved out of the cylinder housing when the piston is actuated, in particular when pressure is applied, from a starting position in an extending movement in the direction of an end position.
  • actuation means supplying energy to the actuation cylinder, as a result of which the piston in the cylinder housing is moved.
  • the energy supplied is particularly preferably in the form of pressurization of the piston, in particular when the actuating cylinder is in the form of a pneumatic cylinder. If no energy is supplied, the piston is in an initial position.
  • the actuating cylinder is designed in such a way that the piston, when it is arranged on the rail vehicle, is moved downwards when the actuating cylinder is actuated, and thus also the piston rod connected to the piston.
  • the traction mechanism moves from a first position, in which the contact surface is particularly preferably in contact with the contact surface, to a second position, in which more preferably the contact surface is not in contact with the contact surface, in particular counter to the extension movement of the piston, can be moved into the piston rod.
  • the traction mechanism can be moved in the axial direction in the piston rod in any position between the starting position and the end position of the piston rod, limited only by the loss prevention device provided by the holding section.
  • the traction device In the first position of the traction device, in which the contact surface is in contact with the contact surface, the traction device is moved out of the piston rod as far as possible, i.e. the largest possible area of the traction device above the connection section protrudes downwards from the piston rod.
  • the traction mechanism in the piston rod can be moved upwards in the axial direction and take at least a second position in which the contact surface is not in contact with the bearing surface.
  • the traction mechanism can slide upwards into the piston rod if, for example, the contact shoe slides over a bump in the rail and the due to the bump reduced distance between actuating cylinder and rail can be compensated. Less vibrations are thus transmitted to the piston rod or to the actuating cylinder, so that the loads on the actuating cylinder or pendulum movements of the actuating cylinder are minimized.
  • At least one, preferably at least two, particularly preferably four, spring elements, in particular compression coil springs, are provided, with the spring elements being particularly preferably designed to prestress the piston into the initial position.
  • the spring elements are particularly preferably arranged below the piston, so that they press the piston in the actuating cylinder upwards into the starting position.
  • the spring elements are also designed in such a way that the forces exerted by the spring elements are sufficient to carry the piston, the piston rod, the traction means and a contact shoe of a rail brake attached thereto. Comparatively little energy must therefore be supplied to lower the rail brake, or the piston only needs to be subjected to a comparatively low pressure, which only has to be sufficient to overcome the spring forces.
  • the weight of the contact shoe, together with the energy supplied, in particular with the application of pressure has the effect that the contact shoe of the rail brake is lowered when the actuating cylinder is actuated or when pressure is applied.
  • the rail brake is also designed as a magnetic rail brake, the piston does not have to be actively extended over the entire distance to the rail.
  • the course of force of the spring elements can be optimized by appropriate arrangement of the spring elements and tuning of the spring constants, and at the same time a trouble-free linear extension movement of the piston or the piston rod can be ensured.
  • Another advantage is that at least two spring elements are provided, with the spring elements being arranged one behind the other in the axial direction, and with a compensating plate being arranged between the spring elements in the axial direction.
  • a first spring element is thus arranged in the upper area of the actuating cylinder or the cylinder housing and a second spring element is arranged in the lower area of the actuating cylinder or the cylinder housing.
  • the piston presses on the two spring elements from above.
  • a compensating plate is arranged approximately in the middle between the spring elements.
  • At least two spring elements are provided, with a second spring element, in particular a second compression coil spring, being arranged within a first spring element, in particular a first compression coil spring.
  • the second spring element or the second helical compression spring preferably has a different winding direction than the first spring element or the first helical compression spring. That is, if the outer compression coil spring has a right-hand coil, the inner compression coil spring has a left-hand coil.
  • two pairs of compression coil springs can be provided, with a second compression coil spring being arranged inside a first compression coil spring.
  • the two pairs of compression coil springs arranged one inside the other can then be arranged one behind the other in the axial direction, preferably separated by a compensating plate, in the cylinder housing.
  • the interior of the piston rod has, in the lower section, a section that widens conically towards an outside of the piston rod.
  • the section is arranged in the lower area of the interior of the piston rod at the transition between the interior and the exterior of the piston rod.
  • the conically widening section allows movements of the lower area of the traction device protruding from the piston rod to be made possible without strong pressure loads and stresses occurring in the traction device or in the piston rod if an area of the traction device comes into contact with a edge of the piston rod.
  • the movements of the connection section can absorb bending in the traction cable without excessively high pressure peaks and pressure loads occurring.
  • connection section has a thread.
  • the thread can be designed in particular to attach a grinding shoe or a tie rod of a grinding shoe to the connection section.
  • the traction means has a metallic material, in particular a steel, and/or that the traction means has a plastic.
  • the metallic material and/or the plastic can be designed in such a way that the traction means has sufficient stability to hold a grinding shoe suspended on the connection section.
  • the traction means comprises a traction cable
  • the traction cable is in particular made of a metallic material, in particular steel, with the metallic material or the steel having sufficient flexibility.
  • the traction cable is a steel cable, more preferably a wire cable.
  • a wire rope has sufficient stability against tensions in the longitudinal direction to hold a rail brake suspended from the wire rope or the connection section of the wire rope or a sliding shoe suspended from the connection section of the wire rope.
  • wire ropes are flexible, which allows the rail brake or the contact shoe to move relative to the actuating cylinder.
  • a further solution to the problem on which the invention is based is the provision of a rail brake, in particular a magnetic rail brake, according to claim 13 comprising a sliding shoe and an actuating cylinder as described above, the connection section of the traction device being connected directly or indirectly to the sliding shoe, so that the sliding shoe is attached to the traction device is suspended in such a way that the grinding shoe can be moved, in particular deflected, relative to the actuating cylinder at least in a horizontal direction.
  • connection section of the traction means which in turn is designed to be movable or deflectable relative to the holding section of the traction means.
  • the connecting section can be connected to the grinding shoe directly or indirectly. This means that the connection section of the traction device is connected either directly to the grinding shoe or to a tie rod arranged between the grinding shoe and the connection section.
  • connection section is connected to the grinding shoe by means of a thread and a threaded nut that are seconded to the connection section.
  • connection section or the thread arranged on the connection section can be introduced into a bore of the grinding shoe and/or the tie rod.
  • a threaded nut is screwed on on the opposite side, as a result of which the grinding shoe is held and suspended on the connection section and thus also on the actuating cylinder.
  • the actuating cylinder of the rail brake can also be configured in accordance with the embodiments described above.
  • FIG. 1 shows a known rail brake 200 with an actuating cylinder 201 and a sliding shoe 202.
  • the actuating cylinder 201 has a cylinder housing 203 and is connected via a bracket 204 to a bogie of a rail vehicle, not shown.
  • a piston rod 205 protrudes downward from the cylinder housing 203 .
  • a tie rod 207 of the rail brake 200 is connected to a connection section 206 of the piston rod 205 by means of a screw connection 208 .
  • the piston rod 205 from the cylinder housing 203 in an extension movement in the drawing 1 moved out down.
  • the grinding shoe 202 is thus moved via the tie rod 207 to an in 1 not shown lowered rail. Rubber elements 209 are provided for shock absorption.
  • FIG. 2 shows an actuating cylinder 100 for a rail brake, in particular for a magnetic rail brake, comprising a cylinder housing 10, a piston 11 guided in the cylinder housing 10 and a piston rod 12 connected to the piston 11.
  • the piston rod 12 is hollow and has an interior space 13.
  • a traction mechanism 14 is arranged in the interior space 13 so that it can move in an axial direction 15 .
  • the traction means 14 has a holding section 17 at a first end 16 which prevents the traction means 14 from sliding out of the piston rod 12 .
  • a diameter 20 in an upper area 21 of the interior 13 of the piston rod 12 is larger than a diameter 22 in a lower area 23 of the interior 13 of the piston rod 12.
  • the holding section is designed as a rotary part 24, in particular as a sleeve 25.
  • a diameter 26 of the holding section 17 in the area of a flange 27 is larger than the diameter 22 of the lower area 23 and smaller than the diameter 20 of the upper area 21 of the interior 13 of the piston rod 12
  • Interior 13 of the piston rod 12 is arranged in such a way that the traction means 14 is prevented from sliding out of the piston rod 12 .
  • the traction means 14 can be moved within the interior space 13 of the piston rod 12 in the axial direction 15, with the movement in the drawing of FIG 2 is limited downwards by the interaction of the retaining portion 17 with the reduced diameter 22 in the lower region 23 of the hollow piston rod 12.
  • the traction means 14 has a flexible traction cable 28 . Due to the flexibility of the traction cable 28 , the connection section 19 can be moved or deflected relative to the holding section 17 at least in a horizontal direction 29 perpendicular to the axial direction 15 . A tie rod that can be fastened to the connection section 19 or a contact shoe of a rail brake can thus also move at least in the horizontal direction 29 relative to the holding section 17 and the actuating cylinder 100 or the cylinder housing 10 .
  • each spring element 31 designed as compression coil springs 30 is arranged, which push the piston 11 in the 2 shown starting position A upwards.
  • Two spring elements 31 in each case form a first pair of spring elements 31a and a second pair of spring elements 31b, which are arranged one behind the other in the axial direction 15 .
  • a compensating plate 32 is arranged between the pairs of spring elements 31a, 31b and is likewise movable in the cylinder housing 10 in the axial direction 15 .
  • Each spring element pair 31a, 31b comprises a second compression coil spring 30b arranged inside a first compression coil spring 30a, the coiling direction of the second compression coil spring 30b being opposite to the coiling direction of the first compression coil spring 30a.
  • Compressed air is introduced through a compressed air line 33 into a pressure chamber 34 above the piston 11, so that the piston 11 can be subjected to compressed air.
  • the piston 11 in the 2 pressed down against the spring force of the spring elements 31.
  • the piston rod 12, which is firmly connected to the piston 11, is thereby moved downwards out of the cylinder housing 10. Due to the weight of the traction device 14 and a grinding shoe that may be arranged on the connection section 19 of the traction device 14 , the traction device 14 or the grinding shoe suspended thereon is also lowered by the actuation of the actuating cylinder 100 .
  • the spring constants of the compression coil springs 30, 30a, 30b are selected in such a way that they hold the piston 11, the piston rod 12, the traction mechanism 14 and a grinding shoe suspended thereon in the starting position A, so that only a relatively low pressure is generated in the pressure chamber 34 must be used to lower the sanding pad onto a rail.
  • connection section 19 has two threads 35 for connecting a grinding shoe or a tie rod.
  • a tie rod arranged between the threads 35 can then be held by means of threaded nuts 36 .
  • the piston rod 12 has an interior 13, with a diameter 20 in an upper area 21 being larger than a diameter 22 in a lower area 23 of the piston rod 12. Due to the different diameter 20, 22 arises between the upper area 21 and the lower area 23 has a step 37 with a contact surface 38 which is aligned essentially perpendicular to the axial direction 15 of the piston rod 12 . In the lower area 23, the piston rod 21 also has a section 39 that widens conically.
  • the traction cable 28 has a holding section 17 which is designed as a rotary part 24 or as a sleeve 25 and also includes a flange 27 .
  • the connection section 19 is arranged on the traction cable 28 , which is designed as a press-in sleeve 40 .
  • the traction cable 28 is a flexible wire cable 41 so that the connection section 19 can be deflected or moved in a horizontal direction 29 perpendicular to the axial direction 15 .
  • the flange 27 of the holding section 17 has a contact surface 42 on an underside, which is aligned in a plane perpendicular to the axial direction 15 .
  • FIG 5 shows a traction means 14 designed as a traction cable 28, which is arranged with a holding section 17 in the interior 13 of the piston rod 12.
  • the contact surface 42 of the holding section 17 is in direct contact with the contact surface 38 in the transition between the lower area 23 and the upper area 21 of the interior 13 of the piston rod 12.
  • the traction cable 28 can be moved in the axial direction 15 in the interior 13 of the piston rod 12 arranged.
  • the contact between contact surface 38 and contact surface 42 prevents the traction cable 28 from sliding out of the interior 13.
  • the connection section 19 is deflected in the horizontal direction 29, the traction cable 28 can be supported on the conical section 39 in the lower area 23 of the piston rod 12.
  • FIG. 6 shows the traction cable 28 in a second position C in the piston rod 12.
  • the traction cable 28 has been displaced in the axial direction 15 in the piston rod 12, so that the contact surface 42 is no longer in contact with the contact surface 38.
  • the traction means 14 is designed as a rigid, inflexible rod 43, with a first end 16 of the rigid rod 43 also having a holding section 17 arranged.
  • the traction mechanism 14 also has a universal joint 44 embodied Joint 45 via which the connection section 19 is connected to the rigid rod 43 in an articulated manner and in a manner that allows it to be deflected or pivoted in the horizontal direction 29 .
  • the traction means 14 can be moved within the cavity 13 of the piston rod 12 in the axial direction 15 and is prevented from sliding out of the piston rod 12 by the holding section 17 or the contact surface 42 of the flange 27 and the contact surface 38 of the piston rod 12.
  • the traction means 14 has a rigid rod 43 and a holding section 17 at a first end 16.
  • the holding section 17 comprises a flange 27 with a contact surface 42.
  • the connection section 19 is connected to the rigid rod 43 in a deflectable manner via a universal joint 44.
  • the connection section 19 also has a thread 35 .
  • the traction mechanism 14 can be moved out of the position in the 2 , 5 and 7 shown first position B, in which the contact surface 42 of the traction means 14 is in contact with the contact surface 38 of the piston rod 12, against the extension movement 46 of the piston rod 12 in a second position C according to 6 , in which the contact surface 42 is not in contact with the contact surface 38, are moved into the piston rod 12 in the axial direction 15 upwards.
  • This movement of the traction means 14 in the piston rod 12 counter to the extension movement 46 allows varying distances between the rail and the actuating cylinder 100 to be compensated for.
  • connection section 19 due to the mobility or deflectability of the connection section 19 in the horizontal direction 29 It is possible to compensate for relative movements due to the friction between the grinding shoe and the rail. As soon as the pressure chamber 34 is vented, the spring elements 31 ensure that the piston 11, the piston rod 12, the traction means 14 arranged therein and the grinding shoe suspended on the connection section 19 of the traction means 14 are moved upwards again.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Braking Arrangements (AREA)

Claims (13)

  1. Cylindre d'actionnement (100) pour un frein sur rail, en particulier un frein sur rail magnétique, comprenant un boîtier de cylindre (10), un piston (11) guidé dans le boîtier de cylindre (10) et une tige de piston (12) reliée au piston (11), sachant que la tige de piston (12) est constituée creuse et comporte un espace intérieur (13), sachant que dans l'espace intérieur (13) de la tige de piston (12) est disposé un moyen de traction (14) guidé de façon mobile dans une direction axiale (15) de la tige de piston (12), sachant que le moyen de traction (14) comporte une section de maintien (17) à une première extrémité (16) disposée dans l'espace intérieur (13), laquelle est constituée pour éviter un glissement de sortie du moyen de traction (14) hors de la tige de piston (12), sachant que le moyen de traction (14) comporte à une deuxième extrémité (18) ressortant de l'espace intérieur (13) une section de liaison (19) adaptée pour une liaison à un frein sur rail et sachant que la section de liaison (19) est mobile et peut être en particulier orientée par rapport à la section de maintien (17), caractérisé en ce que le moyen de traction (14) comprend un câble de traction flexible (28), sachant que la section de maintien (17) est disposée à une extrémité supérieure (16) du câble de traction (28) et la section de liaison (19) à une extrémité inférieure (18) du câble de traction (28) ou en ce que le moyen de traction (14) comprend une tige (43) rigide et/ou non flexible, sachant que le moyen de traction (14) comporte un joint universel (44) ou un joint à rotule par le biais duquel la section de liaison (19) est reliée à la tige (43) et pouvant être orientée par rapport à la tige (43).
  2. Cylindre d'actionnement (100) selon la revendication 1, caractérisé en ce que l'espace intérieur (13) comporte une zone inférieure (23) et une zone supérieure (21), sachant qu'un diamètre (22) de la zone inférieure (23) de l'espace intérieur (13) est plus petit qu'un diamètre (20) de la zone supérieure (21) de l'espace intérieur (13) et en ce que de préférence un diamètre (26) de la section de maintien (17) est plus grand que le diamètre (22) de la zone inférieure (23) de l'espace intérieur (13).
  3. Cylindre d'actionnement (100) selon la revendication 1 ou 2, caractérisé en ce que le moyen de traction (14) est disposé de préférence, pouvant tourner dans la tige de piston (12) autour de la direction axiale (15).
  4. Cylindre d'actionnement (100) selon l'une quelconque des revendications précitées, caractérisé en ce que la section de maintien (17) est une bride (27) et/ou une pièce rotative (24) en particulier un manchon (25), sachant que la section de maintien (17) comporte une surface de contact inférieure (42) et sachant que l'espace intérieur (13) de la tige de piston (12) comporte à un endroit de transition entre la zone inférieure (23) et la zone supérieure (21) une surface d'appui (38) pour la surface de contact (42) et/ou en ce que la section de liaison (19) est un manchon, en particulier un manchon d'enfoncement (40).
  5. Cylindre d'actionnement (100) selon l'une quelconque des revendications précitées, caractérisée en ce que le cylindre d'actionnement est constitué de telle manière que la tige de piston (12) reliée au piston (11) lors d'un actionnement, en particulier lors d'une sollicitation par pression, du piston (11) est sortie d'une position initiale (A) dans un mouvement de sortie (46) en direction d'une position extrême hors du boîtier de cylindre (10).
  6. Cylindre d'actionnement (100) selon l'une quelconque des revendications précitées, caractérisé en ce que le moyen de traction (14) peut être déplacé vers l'intérieur dans la tige de piston (12) d'une première position (B), dans laquelle de préférence la surface de contact (42) est en appui avec la surface d'appui (38), dans une deuxième position (C), dans laquelle la surface de contact (42) ne se trouve de préférence pas en appui avec la surface d'appui (38), en particulier à l'opposé du mouvement de sortie (46) du piston (11).
  7. Cylindre d'actionnement (100) selon l'une quelconque des revendications précitées, caractérisé en ce qu'au moins un, de préférence au moins deux, en particulier de préférence quatre, éléments à ressort (31), en particulier des ressorts hélicoïdaux de pression (30, 30a, 30b) sont prévus, sachant que les éléments à ressort (31) sont en particulier constitués de préférence pour précontraindre le piston (11) dans la position initiale (A).
  8. Cylindre d'actionnement (100) selon la revendication 7, caractérisé en ce qu'au moins deux éléments à ressort (31) sont prévus, sachant que les éléments à ressort (31) sont disposés l'un derrière l'autre dans la direction axiale (15) et sachant qu'une plaque de compensation (32) est disposée dans la direction axiale (15) entre les éléments à ressort (31).
  9. Cylindre d'actionnement (100) selon la revendication 7 ou 8, caractérisé en ce qu'au moins deux éléments à ressort (31) sont prévus, sachant qu'à l'intérieur d'un premier élément à ressort (31), en particulier d'un premier ressort hélicoïdal de pression (30a), est disposé un deuxième élément à ressort (31), en particulier un deuxième ressort hélicoïdal de pression (30b).
  10. Cylindre d'actionnement (100) selon l'une quelconque des revendications précitées, caractérisé en ce que l'espace intérieur (13) de la tige de piston (12) comporte dans la zone inférieure (23) une section (39) s'élargissant de façon conique vers un côté extérieur de la tige de piston (12).
  11. Cylindre d'actionnement (100) selon l'une quelconque des revendications précitées, caractérisé en ce que le câble de traction (28) est un câble d'acier, de préférence un câble métallique (41).
  12. Cylindre d'actionnement (100) selon l'une quelconque des revendications précitées, caractérisé en ce que le moyen de traction (14) comporte un matériau métallique, en particulier un acier, et/ou en ce que le moyen de traction (14) comporte une matière plastique.
  13. Frein sur rail, en particulier frein sur rail magnétique, comprenant un patin de frottement et un cylindre d'actionnement (100) selon l'une quelconque des revendications 1 à 12, caractérisé en ce que la section de liaison (19) du moyen de traction (14) est directement ou indirectement reliée au patin de frottement de telle manière que le patin de frottement est suspendu au moyen de traction (14) de telle sorte que le patin de frottement peut être déplacé, en particulier orienté au moins dans une direction horizontale (29), par rapport au cylindre d'actionnement (100).
EP18194730.0A 2018-09-17 2018-09-17 Cylindre d'actionnement pour un frein sur rail et frein sur rail doté d'un cylindre d'actionnement Active EP3623252B1 (fr)

Priority Applications (6)

Application Number Priority Date Filing Date Title
PL18194730.0T PL3623252T3 (pl) 2018-09-17 2018-09-17 Cylinder uruchamiający hamulec szynowy i hamulec szynowy z cylindrem uruchamiającym
EP18194730.0A EP3623252B1 (fr) 2018-09-17 2018-09-17 Cylindre d'actionnement pour un frein sur rail et frein sur rail doté d'un cylindre d'actionnement
HRP20230819TT HRP20230819T1 (hr) 2018-09-17 2018-09-17 Pokretački cilindar za željezničku kočnicu i željeznička kočnica sa pokretačkim cilindrom
ES18194730T ES2952201T3 (es) 2018-09-17 2018-09-17 Cilindro de accionamiento para un freno de carril y freno de carril con un cilindro de accionamiento
HUE18194730A HUE063004T2 (hu) 2018-09-17 2018-09-17 Mûködtetõhenger sínfékhez és sínfék mûködtetõhengerrel
RS20230597A RS64468B1 (sr) 2018-09-17 2018-09-17 Pokretački cilindar za šinsku kočnicu i šinska kočnica sa pokretačkim cilindrom

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP18194730.0A EP3623252B1 (fr) 2018-09-17 2018-09-17 Cylindre d'actionnement pour un frein sur rail et frein sur rail doté d'un cylindre d'actionnement

Publications (3)

Publication Number Publication Date
EP3623252A1 EP3623252A1 (fr) 2020-03-18
EP3623252C0 EP3623252C0 (fr) 2023-06-07
EP3623252B1 true EP3623252B1 (fr) 2023-06-07

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Application Number Title Priority Date Filing Date
EP18194730.0A Active EP3623252B1 (fr) 2018-09-17 2018-09-17 Cylindre d'actionnement pour un frein sur rail et frein sur rail doté d'un cylindre d'actionnement

Country Status (6)

Country Link
EP (1) EP3623252B1 (fr)
ES (1) ES2952201T3 (fr)
HR (1) HRP20230819T1 (fr)
HU (1) HUE063004T2 (fr)
PL (1) PL3623252T3 (fr)
RS (1) RS64468B1 (fr)

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2012486A1 (de) * 1969-05-19 1970-11-26 VEB Berliner Bremsenwerk, χ 1134 Berlin-Lichtenberg tentwesen, Ostberlin WP139920 Hubzylinder für Magnetschienenbremse
DE2916460A1 (de) * 1979-04-24 1980-11-06 Knorr Bremse Gmbh Hubzylinder fuer magnetschienenbremsen fuer schienenfahrzeuge
GB2074260A (en) 1980-04-17 1981-10-28 Lucas Industries Ltd Improvements in Disc Bakes for Vehicles
GB9818508D0 (en) * 1998-08-26 1998-10-21 Fluid Power Design Limited Rail vehicle emergency braking system
DE102013223962A1 (de) 2013-11-22 2015-05-28 Continental Teves Ag & Co. Ohg Kolbenanordnung für eine Scheibenbremse
WO2017117303A1 (fr) * 2015-12-28 2017-07-06 Krasnoff Curren Système de freinage

Also Published As

Publication number Publication date
PL3623252T3 (pl) 2023-12-04
HRP20230819T1 (hr) 2023-11-10
EP3623252A1 (fr) 2020-03-18
EP3623252C0 (fr) 2023-06-07
ES2952201T3 (es) 2023-10-30
RS64468B1 (sr) 2023-09-29
HUE063004T2 (hu) 2023-12-28

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