EP3623252A1 - Actuating cylinder for rail vehicle brakes and rail vehicle brake with an actuating cylinder - Google Patents

Abstract

In order to provide an actuating cylinder for a rail brake, in which the load or pendulum movement occurring due to relative movements of a grinding shoe to be suspended on the actuating cylinder is minimized and for which the space required in a bogie of a rail vehicle for fastening the actuating cylinder is minimized, an actuating cylinder (100) is Proposed for a rail brake, in particular 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) being hollow and has an interior (13), wherein in the interior (13) of the piston rod (12) a traction means (14) is arranged such that it can move in an axial direction (15) of the piston rod (12), the traction means (14) on an in the interior (13) arranged first end (16) has a holding section (17), which is designed to prevent the traction means (14) from sliding out of the piston rod (12), the traction means (14) also having a connection section (19) suitable for connection to a second end (18) protruding from the interior (13) has a rail brake, and the connection section (19) is movable, in particular deflectable, relative to the holding section (17)

Description

The present invention relates to an actuating cylinder 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, with a traction means in the interior of the piston rod is arranged movably guided in an axial direction, the traction means having a holding section at a first end arranged in the interior, which is designed to prevent the traction means from sliding out of the piston rod.

Furthermore, the present invention relates to a rail brake, in particular a magnetic rail brake, comprising a grinding shoe and an actuating cylinder.

Technological background

A rail brake is a brake for a rail vehicle. It comprises an iron grinding shoe, which is lowered onto a rail to brake the rail vehicle. Friction occurs between the rail and the grinding shoe moving forward with the rail vehicle, which converts the kinetic energy of the movement into heat until the kinetic energy is used up.

A most frequently used embodiment of a rail brake is a magnetic rail brake. The magnetic rail brake additionally comprises an electromagnet, which is usually arranged in the grinding shoe. When current flows through the electromagnet, the grinding shoe is pulled onto the rail.

Actuating cylinders are usually provided to lower or raise the grinding shoe of the rail brake, on which the grinding shoe of the rail brake is suspended. When the actuating cylinder is actuated, the rail brake or the grinding shoe of the rail brake becomes so far lowered until, in the case of a magnetic rail brake, the magnetic forces generated by the electromagnets are sufficient to pull the grinding shoe towards the rail.

The actuating cylinder is attached to the rail vehicle, for example on a bogie. In known rail brakes, the connection between the actuating cylinder and the grinding shoe or a tie rod of the grinding shoe is a rigid connection. With the rigid connection, the grinding shoe or the tie rod of the grinding shoe is connected directly to the piston rod of the actuating cylinder. Due to movements of the rail vehicle or due to unevenness in the surface of the rail and when the piston in and out of the actuating cylinder, relative movements of the magnetic rail brake with respect to the rail vehicle and the actuating cylinder occur. In order to minimize the relative movements and the resulting material fatigue, rubber-elastic bearings of the actuating cylinder on the rail vehicle are known in the prior art.

With a rubber-elastic bearing, however, there is a pendulum movement of the actuating cylinder and a higher load on the cylinder connection. This also results in a larger necessary clearance in the bogie.

From the DE 10 2013 223 962 A1 a piston arrangement for a disc brake is known. The piston is designed as a hollow cylinder open on one side without cutting from thin sheet steel or a section of steel wire. The piston further comprises a piston crown and a wall with a groove in one piece, the piston crown, starting from the inside of a pot, with which brake pressure can be applied hydraulically, so that an outwardly directed contact surface of the piston crown 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 2 074 260 A discloses an actuating cylinder for a disc brake. The actuating cylinder has a housing and a hollow, stepped piston which is arranged in a cylinder bore of the housing. There is one in the hollow bulb Arranged sleeve which is positively guided on the stepped piston via a projection formed on the sleeve. When the piston is actuated, a pull rod is actuated via the sleeve. By means of the sleeve arranged in the piston, a transverse component of a braking pressure force can be passed on to the housing of the actuating cylinder.

Presentation of the invention: task, solution, advantages

The present invention has for its object to provide an actuating cylinder for a rail brake, in which due to relative movements of a grinding shoe to be suspended on the actuating cylinder, stress or pendulum movement occurring are minimized and for which the necessary space in a bogie of a rail vehicle for fastening the actuating cylinder is minimized . Furthermore, the present invention has for its object to provide a rail brake with an actuating cylinder with which the aforementioned advantages are obtained.

To achieve the object on which the invention is based, an actuating cylinder 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 is proposed, the piston rod being hollow and having an interior, with the interior being the piston rod a traction means is arranged movably guided in an axial direction of the piston rod, the traction means having a holding section at a first end arranged in the interior, which is designed to prevent the traction means from sliding out of the piston rod, the traction means also being able to move one out of the Interior projecting second end has a connection section suitable for connection to a rail brake, in particular to a grinding shoe of a rail brake, and wherein the connection section is movable, in particular deflectable relative to the holding section , is.

The piston rod is hollow and has an interior. The interior can be designed as an inner bore of the piston rod. Here is the piston rod Open to 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 elongated extension in an axial direction, the interior, in particular the inner bore, extending along the axial direction.

The traction means is arranged at least partially, namely with the first end in the interior, and can be moved back and forth in the piston rod in the axial direction. In this case, a holding section is provided which secures the traction means in the piston rod in the manner of a captive device, so that a complete sliding out of the traction means from the piston rod is prevented.

At the second end protruding from the interior, 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 grinding 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. Movability of the connecting section relative to the holding section means that the connecting section can be moved at least in one plane perpendicular to the axial direction of the piston rod relative to the holding section of the traction means arranged in the piston rod. 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.

In particular, the orientation of the region arranged in the interior of the piston rod or the first end of the traction means is not changed when the region protruding from the interior of the piston rod or the second end of the traction element is moved or deflected. During a movement or deflection of the connecting section, preferably only the area that protrudes from the interior of the piston rod or the second end of the traction device experiences a change in the orientation. In particular, the area of the traction device, in particular the first end of the traction device, is in the interior the piston rod is arranged, can only be moved in the axial direction and, in particular, cannot be moved or can be deflected only in a plane perpendicular to the axial direction or only minimally.

For example, the connecting section can be pivoted, deflected or moved laterally, in particular perpendicular to the axial direction of the piston rod, relative to the holding section. If a rail brake, in particular a magnetic rail brake, is attached to the connection section and thus suspended from the traction means, relative movements of the rail brake, in particular a grinding shoe of the rail brake, are possible due to the mobility or deflectability of the connection section relative to the actuating cylinder, so that pendulum movements, material fatigue and loads on the Actuating cylinder or its suspension on a bogie of a rail vehicle can be reduced.

When the actuating cylinder is arranged on the rail vehicle, it is preferably fastened to a bogie of the rail vehicle. For this purpose, the cylinder housing of the actuating cylinder is fastened to the bogie in a lower region such that an upper region of the actuating cylinder is essentially free-standing. The piston and the piston rod connected to the piston perform a movement in a vertical or vertical direction when the actuating cylinder is actuated. If the piston and the piston rod are lowered, the traction means arranged in the interior of the piston rod is also lowered. In this state of the actuating cylinder arranged on the rail vehicle, the traction means protrudes downward from the hollow piston rod, in particular the connection section is arranged essentially below the holding section.

A tie rod or a grinding shoe of the rail brake can be fastened to the connecting section, the holding section arranged in the interior of the hollow piston rod preventing the traction device from sliding out and thus preventing the grinding shoe arranged at the connecting section of the traction device from falling down. When lowering or lowering the grinding shoe or the rail brake and due to the contact of the Grinding shoe with the friction occurring on the rail can lead to relative movements of the grinding shoe relative to the actuating cylinder, but these relative movements are largely compensated for due to the mobility, in particular the deflectability, of the connecting section relative to the holding section and thus relative to the actuating cylinder.

Due to the mobility of the connection section relative to the holding section and thus relative 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.

In the following, terms such as “above”, “below”, “laterally”, “upper end” and “lower end” are always related to an orientation of the actuating cylinder which corresponds to the orientation of the actuating cylinder in the state arranged on the rail vehicle. In other words, terms such as “above”, “below” etc. are to be referred to an actuating cylinder which is oriented such that the piston and the piston rod connected thereto execute 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 connecting section of the traction means. In the case of a different orientation of the actuating cylinder, for example in the case of a horizontal orientation of the actuating cylinder, that is to say in an orientation in which the piston and the piston rod move in a horizontal direction, terms such as “above”, “below” and related terms are corresponding to transfer or adapt.

The interior preferably has a lower region and an upper region, a diameter of the lower region of the interior being smaller than a diameter of the upper region of the interior, and more preferably a diameter of the holding section larger than the diameter of the lower region of the interior of the Piston rod is.

The interior of the piston rod is divided into an upper and a lower area, in particular in the axial direction, the upper area in the Rail vehicle arranged state of the actuating cylinder is arranged in the vertical direction above the lower region. If the interior is designed as an inner bore, the interior has two substantially cylindrical regions of the bore, which have different diameters. The sections of the inner bore in the upper area and in the lower area of the interior are aligned coaxially to one another. Seen 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 region of the interior, but more preferably at the same time smaller than the diameter of the upper region of the interior. As a result, the holding section and thus the entire traction device is held in the form of a captive device in the interior of the piston rod and the traction device is prevented from sliding downward out of the piston rod. At the same time, a movement of the traction means in the axial direction of the piston rod can be ensured, the movement being limited only downwards by the securing against loss guaranteed by the holding section and the corresponding configuration of the diameter of the lower region and the upper region of the interior.

It is further preferably provided that the diameter of the lower region is between 10 mm and 20 mm, more preferably between 13 mm and 17 mm, particularly preferably 15 mm, and / or that the diameter of the upper region is between 15 mm and 25 mm , more preferably between 18 mm and 22 mm, particularly preferably 20 mm, and / or that the diameter of the holding section is between 13 mm and 23 mm, further preferably between 16 mm and 20 mm, particularly preferably 18 mm.

With the choice of these diameters, a piston rod and a traction means are provided which have sufficient stability to hold or to hang up a grinding shoe of a rail brake. At the same time, the piston rod can have a smaller outer diameter than 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 connecting section relative to the holding section.

It can be provided with further advantage that the traction means, preferably rotatable about the axial direction, is arranged in the piston rod.

The rotatability of the traction means in the hollow piston rod can in particular be ensured in that the traction means, in particular the holding section, has an essentially circular cross section and is arranged in an inner bore of the piston rod with a likewise substantially circular cross section.

Due to the rotatability of the traction means in the piston rod, even complex relative movements of a grinding shoe or a tie rod of a grinding shoe of a rail brake with respect to the actuating cylinder can be compensated for, since the traction means can always assume a position by rotating in the piston rod in which the mobility or deflectability of the connecting section can be compared the holding section can optimally compensate for the relative movements of the grinding shoe.

It can further preferably be provided that the holding section is a flange and / or a turned part, in particular a sleeve, the holding section having a lower contact surface and the interior of the piston rod at a transition between the lower region and the upper region being a contact surface for has the contact surface.

The contact surface is further preferably formed opposite and facing the contact surface of the piston rod. In particular, when the actuating cylinder is arranged on the rail vehicle, the contact surface is located on an underside of the holding section. The contact surface of the piston rod is formed at the transition between the lower region and the upper region, and can be designed in a step-like manner. When the actuating cylinder is arranged on the rail vehicle, the contact surface and the contact surface can be oriented essentially horizontally, that is to say in a plane perpendicular to the axial direction of the piston rod. However, it is also possible for the contact surface and the contact surface to be essentially conical and complementary are trained to each other. The contact surface and the contact surface can further preferably be brought into a flat 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 molded out of the traction means. In addition, 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. In particular if 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 rotating part can also have a flange.

It can be provided with further advantage that the connection section is a sleeve, in particular a press-in sleeve.

By designing the connection section as a sleeve, it can be connected to the traction means in a simple manner. However, the connection section can also be an integral part of the traction means.

It is advantageously provided that 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 integration of the actuating cylinder into existing brake systems can thus be carried out easily.

With a further advantage, the actuating cylinder is designed such that the piston rod connected to the piston is moved out of a starting position in an extension movement in the direction of an end position out of the cylinder housing when the piston is actuated, in particular when pressure is applied.

In the present sense, actuation is understood to mean supplying energy to the actuating cylinder, as a result of which the piston is moved in the cylinder housing. The energy supplied is particularly preferably designed as pressurizing the piston, in particular if the actuating cylinder is designed as a pneumatic cylinder. If no energy is supplied, the piston is in a starting position. By supplying the energy, in particular by pressurizing the piston, the piston and the piston rod connected to the piston are moved from the starting position into an end position in which the piston rod preferably protrudes from the cylinder housing. The actuating cylinder is designed such that the piston in the state arranged on the rail vehicle is actuated when the actuating cylinder is actuated, and thus the piston rod connected to the piston is moved downward.

In the state of the actuating cylinder arranged on the rail vehicle, actuation of the actuating cylinder thus lowers the piston rod, the traction means arranged therein and the grinding shoe attached to the connecting section of the traction means until the grinding shoe comes into contact with the rail, or, in the case of a magnetic rail brake, until Magnetic forces are sufficient to pull the grinding shoe towards the rail.

It can further preferably be provided that the traction device moves from a first position, in which the contact surface is particularly 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 against the extension movement of the piston can be moved into the piston rod.

The traction means 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 captive device provided by the holding section. In the first position of the traction device, in which the contact surface is in contact with the contact surface, the traction device has been moved out of the piston rod as far as possible, i.e. the greatest possible area of the traction device above the connection section protrudes downward from the piston rod. From this position, in which the loss protection or the If the contact surface of the holding section with the contact surface of the piston rod prevents further movement of the traction means downwards out of the piston rod, the traction means in the piston rod can be moved upwards in the axial direction and assume at least a second position in which the contact surface is not included the contact surface is in contact.

Since, when the actuating cylinder is actuated downward, the piston rod is preferably moved out of the cylinder housing in an extension movement from an initial position in the direction of an end position, and since the traction means can be moved into the piston from the first position into the second position against the extension movement of the piston, vertical changes in distance between rail and rail vehicle or rail and actuating cylinder can be compensated for when the actuating cylinder is arranged on the rail vehicle. If the piston and the piston rod in the state of the actuating cylinder arranged on the rail vehicle are in the extended state, that is to say in the end position, the traction means, for example when the sanding shoe slides over an elevation of the rail, can slide upward into the piston rod and this due to the elevation reduced distance between the 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.

It is further advantageously provided that at least one, preferably at least two, particularly preferably four, spring elements, in particular compression coil springs, are provided, the spring elements being particularly preferably designed to pretension the piston into the starting position.

The spring elements are particularly preferably arranged below the piston, so that they push the piston in the actuating cylinder upwards into the starting position. The spring elements are also designed such that the forces exerted by spring elements are sufficient to carry the piston, the piston rod, the traction means and a grinding shoe of a rail brake attached to it. To lower the rail brake, a must comparatively low energy is supplied, or the piston only has to be subjected to a comparatively low pressure, which only has to be sufficient to overcome the spring forces. The weight of the grinding shoe together with the energy supplied, in particular with the application of pressure, causes the grinding shoe of the rail brake to be lowered when the actuating cylinder is actuated or when the actuating cylinder is pressurized.

If 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 extension movement of the piston and the piston rod only has to be carried out until the magnetic forces generated by the magnetic rail brake are sufficient to pull the grinding shoe towards the rail.

If at least two or at least four spring elements are provided, the force profile of the spring elements can be optimized by appropriate arrangement of the spring elements and coordination of the spring constants, and at the same time a trouble-free straight-line extension movement of the piston or the piston rod can be ensured.

It is further advantageously provided that at least two spring elements are provided, the spring elements being arranged one behind the other in the axial direction, and a compensating plate being arranged between the spring elements in the axial direction.

Seen in the vertical direction, a first spring element is thus arranged in the upper region of the actuating cylinder or the cylinder housing and a second spring element is arranged in the lower region of the actuating cylinder or the cylinder housing. When actuated, the piston presses on the two spring elements from above. For better power transmission, a compensation plate is arranged approximately in the middle between the spring elements.

It can be provided with further advantage that at least two spring elements are provided, one being within a first spring element first compression coil spring, a second spring element, in particular a second compression coil spring, is arranged.

The second spring element or the second compression coil spring preferably has a different winding direction than the first spring element or the first compression coil spring. That is, if the outer compression coil spring has a right turn, the inner compression coil spring has a left turn.

If four compression coil springs are provided, two pairs of compression coil springs can be provided, a second compression coil spring being arranged in each case within 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.

It can be provided with further advantage that the interior of the piston rod in the lower section has a section that widens conically to an outside of the piston rod.

In particular, the section is arranged in the lower region of the interior of the piston rod at the transition between the interior and the outside environment of the piston rod. The conically widening section allows movements of the lower region of the traction means projecting from the piston rod to be made possible without strong pressure loads and stresses occurring in the traction means or in the piston rod if an area of the traction means comes into contact with a due to a movement of the connecting section Edge of the piston rod comes.

It can further be provided that the connection section has a thread.

The thread can in particular be designed to fasten a grinding shoe or a tie rod of a grinding shoe to the connection section.

It is particularly preferably provided that the traction means comprises a flexible traction cable, the holding section being arranged at an upper end of the traction cable and the connecting section at a lower end of the traction cable.

The traction means thus comprises a traction cable and a holding section and a connecting 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 connecting section is arranged at the lower end of the traction cable and is thus located at the second end of the traction means and is arranged outside the interior of the piston rod.

The flexibility of the traction cable allows a grinding shoe of the rail brake arranged on the connection section to perform relative movements, in particular in an approximately horizontal plane to the axial direction of the actuating cylinder. In other words, 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.

In particular, if the interior of the piston rod has a section that widens conically outwards, the movements of the connecting section can absorb bends in the pull rope without causing excessively high pressure peaks and pressure loads.

It can be provided with further advantage that 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 one on the Connection section has suspended grinding shoe. If the traction means comprises a traction rope, the traction rope in particular is made of a metallic material, in particular a steel, the metallic material or the steel having sufficient flexibility.

It can be provided with further advantage that the traction rope is a steel rope, more preferably a wire rope.

On the one hand, a wire rope has sufficient stability with respect to tensions in the longitudinal direction in order to hold a rail brake suspended on the wire rope or on the connection section of the wire rope or a grinding shoe suspended on the connection section of the wire rope. On the other hand, wire ropes are flexible, which enables relative movements of the rail brake or the grinding shoe with respect to the actuating cylinder.

Furthermore, it can be provided that the traction means comprises a, in particular rigid and / or inflexible, rod, the traction means having a joint, in particular a universal joint or a ball joint, by means of which the connecting section can be moved, in particular deflected, with the rod and with respect to the rod , connected is.

The joint is preferably not arranged in the interior of the piston rod.

In one embodiment in particular, in which the traction means does not comprise a flexible traction cable, an embodiment with a joint is particularly advantageous. The area of the traction device, in particular the upper end of the traction device, which is arranged in the interior of the hollow piston rod, is then designed as an essentially rigid and inflexible rod. The connecting section is also designed as a rigid rod. The connecting section is connected to the rod via the joint and can be moved, in particular deflected or pivoted, relative to the rod and thus also relative to the holding section arranged at the first end of the traction means.

A further solution to the problem on which the invention is based is to provide a rail brake, in particular a magnetic rail brake, comprising a grinding shoe and a previously described actuating cylinder, the connecting section of the traction means being connected directly or indirectly to the grinding shoe, so that the grinding shoe is suspended from the traction means in this way that the grinding shoe can be moved, in particular deflected, relative to the actuating cylinder at least in a horizontal direction.

The mobility or the deflectability of the grinding shoe is ensured by the connecting section of the traction device, which in turn is designed to be movable or deflectable relative to the holding section of the traction device.

The connection section can be connected to the grinding shoe directly or indirectly. This means that the connecting section of the traction means is either connected directly to the grinding shoe or to a tie rod arranged between the grinding shoe and the connecting section.

It can be provided with further advantage that the connection section is connected to the grinding shoe by means of a thread which is arranged on the connection section and a threaded nut.

In particular, the connection section or the thread arranged on the connection section can be inserted into a bore in the grinding shoe and / or the tie rod. A threaded nut is screwed onto the opposite side, as a result of which the grinding shoe is held and suspended on the connecting section and thus also on the actuating cylinder.

The actuating cylinder of the rail brake can also be designed in accordance with the above-described embodiments.

Brief description of the figures

The present invention is explained in more detail below with reference to the figures.

Fig. 1

eine perspektivische Darstellung einer bekannten Schienenbremse mit einem Betätigungszylinder,

Fig. 2

einen Betätigungszylinder mit einer hohlen Kolbenstange und einem Zugseil,

Fig. 3

eine hohle Kolbenstange,

Fig. 4

ein Zugseil,

Fig. 5

ein in einer hohlen Kolbenstange angeordnetes Zugseil in einer ersten Stellung,

Fig. 6

ein in einer hohlen Kolbenstange angeordnetes Zugseil in einer zweiten Stellung,

Fig. 7

einen Betätigungszylinder mit einer hohlen Kolbenstange und einem Zugmittel mit einem Gelenk, und

Fig. 8

ein Zugmittel mit einer starren Stange und einem Gelenk.

Show it:

Fig. 1

1 shows a perspective illustration of a known rail brake with an actuating cylinder,

Fig. 2

an actuating cylinder with a hollow piston rod and a pull rope,

Fig. 3

a hollow piston rod,

Fig. 4

a pull rope,

Fig. 5

a pull cable arranged in a hollow piston rod in a first position,

Fig. 6

a pulling rope arranged in a hollow piston rod in a second position,

Fig. 7

an actuating cylinder with a hollow piston rod and a traction means with a joint, and

Fig. 8

a traction device with a rigid rod and a joint.

Detailed description of the figures

Fig. 1 shows a known rail brake 200 with an actuating cylinder 201 and a grinding shoe 202. The actuating cylinder 201 has a cylinder housing 203 and is connected via a bracket 204 to a bogie, not shown, of a rail vehicle. A piston rod 205 protrudes downward from the cylinder housing 203. A tie rod 207 of the rail brake 200 is connected to a connecting section 206 of the piston rod 205 by means of a screw connection 208. When the actuating cylinder 201 is actuated, the piston rod 205 is moved out of the cylinder housing 203 in an extension movement in the drawing of FIG Fig. 1 moved down out. Via the tie rod 207, the grinding shoe 202 is thus in a Fig. 1 Lowered rail, not shown. Rubber elements 209 are provided for shock absorption. When the grinding shoe 202 moves up and down and because of the friction between the grinding shoe 202 and the rail, vibrations are generated which can lead to oscillating movements 210 of the actuating cylinder 201.

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. In the interior 13, a traction means 14 is arranged so as to be movable in an axial direction 15. The traction means 14 has at a first end 16 a holding section 17 which prevents the traction means 14 from sliding out of the piston rod 12.

At a second end 18 there is a connection section 19 for connection to a rail brake, in particular to a grinding shoe or to a tie rod of a grinding shoe. A diameter 20 in an upper region 21 of the interior 13 of the piston rod 12 is larger than a diameter 22 in a lower region 23 of the interior 13 of the piston rod 12. The holding section is designed as a turned part 24, in particular as a sleeve 25. A diameter 26 of the holding section 17 in the region of a flange 27 is larger than the diameter 22 of the lower region 23 and smaller than the diameter 20 of the upper region 21 of the interior 13 of the piston rod 12. As a result, the traction means 14 is in the manner of a captive device in the Interior 13 of the piston rod 12 is arranged in such a way that the pulling means 14 is prevented from sliding out of the piston rod 12. At the same time, the traction means 14 can be moved within the interior 13 of the piston rod 12 in the axial direction 15, the movement in the drawing of the Fig. 2 is limited downwards by the interaction of the holding section 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. Because of the flexibility of the pull cable 28, the connecting 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 connecting section 19 or a grinding shoe of a rail brake can thus also at least in the horizontal direction 29 with respect to the holding section 17 and move the actuating cylinder 100 and the cylinder housing 10, respectively.

In the cylinder housing 10, four spring elements 31 designed as compression coil springs 30 are arranged, which the piston 11 in the in Fig. 2 Preload shown starting position A upwards. Two spring elements 31 each 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 spring element pairs 31a, 31b, which is also movable in the axial direction 15 in the cylinder housing 10. Each pair of spring elements 31a, 31b comprised a second compression coil spring 30b arranged inside a first compression coil spring 30a, the winding direction of the second compression coil spring 30b being opposite to the winding 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 pressurized with compressed air. When pressurized, the piston 11 is in the Fig. 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 downward out of the cylinder housing 10. Due to the weight of the traction means 14 and a grinding shoe possibly arranged on the connecting section 19 of the traction means 14, the traction means 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 chosen so that they hold the piston 11, the piston rod 12, the traction means 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 in order to lower the grinding shoe onto a rail.

The connecting element 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.

Fig. 3 shows a hollow piston rod 12. The piston rod 12 has an inner space 13, a diameter 20 in an upper region 21 being larger than a diameter 22 in a lower region 23 of the piston rod 12. Due to the different diameters 20, 22, between the upper area 21 and lower area 23 a step 37 with a contact surface 38 which is oriented substantially perpendicular to the axial direction 15 of the piston rod 12. In the lower region 23, the piston rod 21 also has a conically widening section 39.

Fig. 4 shows a traction means 14 in the form of a traction cable 28. At a first end 16, the traction cable 28 has a holding section 17 which is designed as a rotating part 24 or as a sleeve 25 and further comprises a flange 27. At a second end 18 opposite the first end 16, the connection section 19 is arranged on the pull cable 28, which is designed as a press-in sleeve 40. The pull rope 28 is a flexible wire rope 41, so that the connecting 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. In the in Fig. 5 First position B shown, the contact surface 42 of the holding element 17 is in direct contact with the contact surface 38 in the transition between the lower region 23 to the upper region 21 of the interior 13 of the piston rod 12. The traction cable 28 is movable in the axial direction 15 in the interior 13 of the piston rod 12 arranged. The contact of contact surface 38 and contact surface 42 prevents the pulling cable 28 from sliding out of the interior 13. When the connecting section 19 is deflected in the horizontal direction 29, the pulling cable 28 can be supported on the conical section 39 in the lower region 23 of the piston rod 12.

Fig. 6 shows the pull cable 28 in a second position C in the piston rod 12. The pull cable 28 is 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.

Fig. 7 shows a further embodiment of the actuating cylinder 100. Instead of a traction cable 28, the traction means 14 is designed as a rigid, inflexible rod 43, a holding section 17 also being arranged at a first end 16 of the rigid rod 43. The traction means 14 also has a joint 45 designed as a universal joint 44, via which the connecting section 19 is connected to the rigid rod 43 in an articulated manner and can be deflected or pivoted in the horizontal direction 29. As with the embodiment according to the 2 to 6 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.

Fig. 8 shows the traction means 14 according to Fig. 7 . 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 connecting element 19 is connected to the rigid rod 43 in a deflectable manner via a universal joint 44. The connecting element 19 also has a thread 35.

Referring to the Fig. 2 and 7 the operation of the actuating cylinder 100 is explained in more detail. If compressed air is introduced through the pressure line 33 into the pressure chamber 34 above the piston 11, the piston is moved out of the Fig. 2 and 7 Starting position A shown is moved downward out of the cylinder housing 10 in an extension movement 46. A grinding shoe of a rail brake, which is not shown here and is connected to the connecting section 19, is thereby also lowered together with the traction means 14 arranged in the hollow piston rod 12 until the grinding shoe comes into contact with a rail. The piston 11 and the piston rod 12 can be extended to an end position. If the distance between the rail and the actuating cylinder 100 decreases due to unevenness in the rail or due to vertical movements of the rail vehicle, the traction means 14 can be moved from the position shown in FIGS Fig. 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, against the extension movement 46 of the piston rod 12 in a second position C according to Fig. 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. By this movement of the traction means 14 in the piston rod 12 against the extension movement 46, varying distances of the rail from the actuating cylinder 100 can be compensated. In addition, the mobility or deflectability of the connecting element 19 in the horizontal direction 29 makes it 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 connecting element 19 of the traction means 14 are moved upward again.

List of reference numbers

100

Actuating cylinder

10th

Cylinder housing

11

piston

12th

Piston rod

13

inner space

14

Traction means

15

Axial direction

16

First end

17th

Holding section

18th

Second end

19th

Connection section

20th

diameter

21

upper area

22

diameter

23

Lower area

24th

Turned part

25th

Sleeve

26

diameter

27

flange

28

Traction rope

29

Horizontal direction

30th

Compression coil spring

30a

First compression coil spring

30b

Second compression coil spring

31

Spring element

31a

First pair of spring elements

31b

Second pair of spring elements

32

Compensation plate

33

Compressed air line

34

Pressure chamber

35

thread

36

Threaded nut

37

step

38

Contact surface

39

section

40

Press-in sleeve

41

Wire rope

42

Contact area

43

pole

44

Universal joint

45

joint

46

Extension movement

A

Starting position

B

First position

C.

Second position

200

Rail brake

201

Actuating cylinder

202

Grinding shoe

203

Cylinder housing

204

bracket

205

Piston rod

206

Connection section

207

Tie rod

208

Screw connection

209

Rubber elements

210

Pendulum motion

Claims (15)

Actuating cylinder (100) for a rail brake, in particular 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 (13), a traction means (14) being arranged so as to be movable in an axial direction (15) of the piston rod (12) in the interior (13) of the piston rod (12), the traction means (14) being attached a first end (16) arranged in the interior (13) has a holding section (17) which is designed to prevent the traction means (14) from sliding out of the piston rod (12),
characterized,
that the traction means (14) has a connection section (19) suitable for connection to a rail brake at a second end (18) protruding from the interior (13), and that the connection section (19) is movable, in particular deflectable, relative to the holding section (17) , is. Actuating cylinder (100) according to claim 1, characterized in that the interior (13) has a lower region (23) and an upper region (21), a diameter (22) of the lower region (23) of the interior (13) being smaller than a diameter (20) of the upper region (21) of the interior (13), and that preferably a diameter (26) of the holding section (17) is larger than the diameter (22) of the lower region (23) of the interior (13) is. Actuating cylinder (100) according to claim 1 or 2, characterized in that the traction means (14), preferably rotatable about the axial direction (15), is arranged in the piston rod (12). Actuating cylinder (100) according to one of the preceding claims, characterized in that the holding section (17) is a flange (27) and / or a rotating part (24), in particular a sleeve (25), the holding section (17) being a lower one Has contact surface (42) and wherein the interior (13) of the piston rod (12) at a transition between the lower region (23) and the upper region (21) has a contact surface (38) for the contact surface (42), and / or that the connection section (19) is a sleeve, in particular a press-in sleeve (40). Actuating cylinder (100) according to one of the preceding claims, characterized in that the actuating cylinder is designed in such a way that the piston rod (12) connected to the piston (11) when actuating, in particular when pressurized, the piston (11) consists of a Starting position (A) is moved out of the cylinder housing (10) in an extension movement (46) in the direction of an end position. Actuating cylinder (100) according to one of the preceding claims, characterized in that the traction means (14) from a first position (B), in which the contact surface (42) is preferably in contact with the contact surface (38), into a second position ( C), in which the contact surface (42) is preferably not in contact with the contact surface (38), in particular against the extension movement (46) of the piston (11), into the piston rod (12). Actuating cylinder (100) according to one of the preceding claims, characterized in that at least one, preferably at least two, particularly preferably four, spring elements (31), in particular compression coil springs (30, 30a, 30b), are provided, the spring elements (31) being particularly preferred are preferably designed to bias the piston (11) into the starting position (A). Actuating cylinder (100) according to claim 7, characterized in that at least two spring elements (31) are provided, the spring elements (31) being arranged one behind the other in the axial direction (15), and a compensating plate (32) in the axial direction (15) is arranged between the spring elements (31). Actuating cylinder (100) according to claim 7 or 8, characterized in that at least two spring elements (31) are provided, wherein within a first spring element (31), in particular a first compression coil spring (30a), a second spring element (31), in particular a second compression coil spring (30b), is arranged. Actuating cylinder (100) according to one of the preceding claims, characterized in that the interior (13) of the piston rod (12) in the lower region (23) has a section (39) which widens conically to an outside of the piston rod (12). Actuating cylinder (100) according to one of the preceding claims, characterized in that the traction means (14) comprises a flexible traction cable (28), the holding section (17) at an upper end (16) of the traction cable (28) and the connecting section (19 ) is arranged at a lower end (18) of the traction cable (28). Actuating cylinder (100) according to claims 11, characterized in that the traction cable (28) is a steel cable, preferably a wire cable (41). Actuating cylinder (100) according to one of claims 1 to 9, characterized in that the traction means (14) comprises a, in particular rigid and / or inflexible, rod (43), the traction means (14) having a joint (45), in particular a Universal joint (44) or a ball joint, via which the connecting section (19) is connected to the rod (43) and movable, in particular deflectable, relative to the rod (43). Actuating cylinder (100) according to one of the preceding claims, characterized in that the traction means (14) has a metallic material, in particular a steel, and / or that the traction means (14) has a plastic. Rail brake, in particular magnetic rail brake, comprising a grinding shoe and an actuating cylinder (100) according to one of claims 1 to 18, characterized in that the connecting section (19) of the traction means (14) is connected directly or indirectly to the grinding shoe, so that the grinding shoe on the Traction means (14) is suspended in such a way that the grinding shoe relative to the actuating cylinder (100) can be moved, in particular deflected, at least in a horizontal direction (29).

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