DE8026898U1 - HYDRAULIC PISTON TRACK BRAKE FOR BRAKING RAILWAYS - Google Patents

Description

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Patent attorney Rudi Beyer Gneisenaustraße {D-V030 Rat'ingen 6 (Hosel) "

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St and the art

The invention relates to a hydraulic piston rail brake for braking railroad cars, the piston rail brake is arranged by a holder on a rail.

The braking of railway wagons in the roll-off systems of freight yards for the purpose of keeping a distance and Automation takes place with the help of rail brakes. Bar track brakes, rubber track brakes are usually used for this purpose and electrodynamic rail brakes are used. For special roll-off systems that are on a continuous slope, Hydraulic piston rail brakes are used in a relatively large number over the entire route of the railroad car arranged distributed. According to the external structure, these are hydraulic dampers in In the form of piston-cylinder units (DE-OS 1 605 326, DE-OS 2 043 369, DE-OS 1 605 327, DE-OS 1 530 283, DE-AS 1 183 530, DE-PS 1 162 866, Dowty prospectus "Oleo-Gleisbremsen - DHU / 261/1/400 / TY 2/76 and brochure from the same company "Hydraulic Units Lt DHU / 268 / l / 100 / TY April 1976). The holding and guiding devices of such hydraulic piston rail brakes are with bolts in the rail web, and on the inside of the rails, it is attached «The actual damper in the form of a hydraulic piston-cylinder unit (Hydraulic cylinder) is guided vertically or approximately vertically in the holding device, whereby its piston rod is supported on the floor and the damping cylinder with its pi-Iz-shaped head is about 50 mm above it the upper edge of the rail protrudes from the inside of the rail. When a wagon wheel rolls, the damping cylinder of the hydraulic piston brake with the mushroom-shaped Head pushed down vertically through the wheel flange against a hydraulic damping force. These piston queues have the task of the well-running car

Patent attorney Rudi Beyer Gneisenaustraße Ί 0-4030 Rating'en 6 (hiosel) "

from the given tendency for the poor runner to withdraw any excess energy and keep the running car at constant or approximately constant Keep speed. The constant or approximate constant travel speed of the railroad cars is at the piston track brake for the various tasks adjustable and is controlled by an internal valve system automatically controlled. The disadvantage of such hydraulic piston rail brakes is that they are rolled over the mushroom-shaped heads with the wheel flanges protruding above the rail head make loud noises in the form of rattling and ringing. Although it has already been proposed in DE-OS 1 605 327, one Part of the holding device of such a hydraulic piston brake with a certain resilience to design. However, the at Impact of the wagon wheels on the head of such hydraulic piston rail brakes eliminates the strong noises occurring will. Otherwise, this solution has not found its way into practice.

DE-OS 1 530 283 has also proposed an elastic shock absorber between the one that encompasses the wheel To arrange the head of the piston brake and the actual power transmission body. It should be, however it is merely a matter of a number of elastic bushings that accommodate several pins that form the actual head of the damper that comes into contact with the wheel. Apart from the fact that with this solution very high, shock-like Surface pressures occur in the bushings, which are relatively small in diameter, with this solution the risk of tilting or jamming of the Head and thus an uneven load, so that malfunctions are to be feared. These too The solution has therefore not found its way into practice.

All known hydraulic systems are particularly disadvantageous Piston track brakes that their holder is attached to the vertical rail web with bolts that penetrate it are. This results not only in proportion

high cost of attaching the to the rail webs, rather it weakened to a considerable extent.

The rail web will also have through holes

Patent attorney Rudi Beyer Gneisenaustraße 1 D- ^ 030 Ratingen 6 (Hösel)

Furthermore, the piston-cylinder units, i.e. the telescopically telescoping parts of the hydraulic units Damper, unprotected against shock and impact as well as contamination in the previously known types.

Another disadvantage is the inadmissible heating the state-of-the-art hydraulic piston rail brakes. This is a particular danger for Piston track brakes that are located within the distribution zone or directly behind the drainage mountain. In these areas of the marshalling yard, the distribution of the entire wagon volume has not yet or only partially began.

In contrast to the piston track brakes in the direction tracks, which only brake a fraction of the entire car the piston rail brakes in the distribution zone are stressed many times more. By The heat generated by the braking process with each stroke cannot be dissipated quickly enough. The piston rail brakes heat up so quickly that with drainage rates of about 300 cars per hour within 10 minutes almost 180 degrees Celsius can be reached within the individual hydraulic piston rail brakes. That is already the upper limit for the use of sealing elements. Quite apart from that, the lifespan will be the piston rail brakes are reduced at a constantly high operating temperature, which leads to an ongoing renewal, i.e. increased maintenance costs and operational disruptions.

So far, these heating problems have been solved in such a way that the drainage rates are reduced until the brake heats up to a permissible level is roughly in equilibrium with the heat dissipation through the ambient air. With that, however, the Piston rail brakes due to the heating problems in their possible applications on drainage systems with relatively small Push-off performance is limited, which is particularly true in countries where the outside temperatures are constantly high is to count, z. B. in the tropical zones.

Patent attorney Rudi Beyer Gneisenaustraße 1 D - /) u30 Ratingen 6 (Höselj

task

The invention is based on the object of a hydraulic To improve piston track brake according to the preamble of claim 1 considerably. In particular the maintenance effort is to be reduced considerably, which is achieved through better protection against inadmissible heating should be achieved.

Lsnsmnig

The object is achieved by the features given in claim 1.

Some ¥ ο ι · parts

The fact that the hydraulic piston brake is assigned a cooling device, the construction can Such piston track brakes can be used to the full possible maximum braking power, and indeed also at constantly high outside temperatures, as z. B. is the case in tropical regions. As with the invention the hydraulic fluid of the piston rail brakes is constantly cooled by the cooling device, does not need to be feared that ζ. B, damage to the seals or any other risk of overheating Parts of the piston rail brakes occurs.

In particular, the drainage capacity no longer needs to be reduced to such an extent by trial and error - as was previously the case - until a permissible brake heating is approximately in equilibrium with the heat dissipation through the ambient air.

This makes it possible to reduce the maintenance effort to a more economical one Reduce measure, because when the inventive idea (task and solution) is implemented, the thermal The load on the piston rail brakes can be reduced to a structurally predictable amount by which the shunters don't really need to worry when the cooling device is in operation.

Each hydraulic piston rail brake can have one such cooling device can be assigned. As part of the However, the idea of the invention also includes embodiments in which a plurality or plurality of hydraulic piston rail brakes are connected to a remotely located cooling device are connected.

Patent attorney Rudi Beyer Gneisenaustraße 1 D-4030 Railn'gen 6 (Hosel) ¹

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Come as a heat transfer medium for the cooling device z. B. Consider substances that do not pose any sealing problems, for example also hydraulic oils, with which also the hydraulic dampers of the piston rail brakes are filled. But it is also possible for others suitable heat transfer media, for example the cooling liquids commonly used in refrigeration technology to use. It is possible to use suitable switching elements for the individual hydraulic piston rail brakes. ζ. B. assign temperature sensors with remote sensors that ensure a corresponding flow of cooling liquid to the individual piston rail brakes. Are for example several hydraulic piston rail brakes connected to a central cooling device via lines, so can be via valve controls, especially electrical Valve controls achieve that, depending on the heating, the cooling medium depends on the stress on the hydraulic Piston track brakes are fed to these piston track brakes. Even if every piston brake has a cooling device is assigned, the use of such cooling devices depending on the thermal stress on the piston rail brakes be controlled. For example, depending on the hydraulic damper in question When the temperature occurs, a suitable motor drive for the heat transfer medium and / or a compressor is switched on that promotes the heat transfer medium in the circuit to the hydraulic damper in question. Around the investment outlay is economically within limits hold, you will naturally such cooling devices only use where extremely high thermal loads on piston rail brakes are to be expected, thus primarily in the distribution zone of large drainage systems.

In a hydraulic piston rail brake according to the invention the moving masses in contrast to piston rail brakes are the moving masses in contrast to piston rail brakes of the prior art is much lower. This contributes significantly to noise reduction * In addition, the Number of items compared to a piston track brake as it is the subject of DE-PS 20 43 369, considerably low As a result, the manufacturing cost of one is also in accordance with the invention hydraulic piston brake by a substantial amount less than z. B. the manufacturing costs of a piston brake according to DE-PS 20 43 369.

Another major advantage is the fact that a piston track brake is used for the hydraulic damper according to the invention a series part, for. B. from the automotive industry, can be used. This is, inter alia, possible because the hydraulic damper in the pipe construction according to the invention is arranged protected. Furthermore, other items that are already on the market as series items can also be used use hydraulic dampers that can be easily and without special adaptation within an inventive ~~ n "y" £ rr "a" ti ~ jr3rs ~ CTi "e ~ n K ~ o * jrb" e'n'g ~ Jr € -3rs ~ b ~ i '"e * ms ο eiR-3 ct ζ er J. q gsgrs

Patent attorney Rudi Beyer Gneisenaustraße 1 D-itO3O Ratingci 6 (Hc.se »

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In addition, the invention enables the circulation of the heat transfer medium via the stroke of the hydraulic damper to control or initiate. So it is B. möylich, the stroke movement of the hydraulic damper itself to To be used by pumping the heat transfer medium or for sucking in cooling air and for expelling heated air.

Further execution format

In the embodiment according to claim 2 , a particularly compact design results.

If an embodiment according to claim 3 is chosen, a larger number of hydraulic piston rail brakes can be connected to a central cooling device which, for. B. is arranged at a certain distance from the tracks and is set in motion by remote control means, in particular electrical automatic remote control, or promotes the heat transfer medium to the individual piston rail brakes.

Describes a compact but very stable embodiment Ainisproclhi 4. In this embodiment are special Few individual parts required, which are largely made up of turned parts, but also in one piece in terms of material, ζ. B. by injection molding.

A particularly advantageous embodiment is described in claim 5 . In addition to the thermal protection of the hydraulic dampers, this embodiment has the advantage that the hydraulic piston rail brakes can be arranged in retaining tabs which are coupled to the rail foot by means of a clamp connection. This eliminates the need for holes weakening the web of the rails. In addition, the hydraulic dampers can be arranged in a protected manner.

According to claim 6 , a connecting piece is provided which forms a flat container which contains at least part of the cooling liquid. This container can be provided at least partially below the rail foot or below a clamping lug which is arranged on the rail foot above the lower edge of the sleeper and does not interfere here in any way.

If an embodiment according to claim 7 is selected, so relatively large amounts of coolant can be accommodated in a small space. Also the maintenance of the hydraulic This does not make the damper itself more difficult.

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Patent attorney Rudi Beyer Gneisenaustraße 1 D- ^ 030 R * atingen 6 (

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In the configuration according to Airospriuiclfo H, the with the Surface area that comes into contact with ambient air is enlarged, which results in a correspondingly greater cooling capacity.

The Amspiriuicthie 9 to 16 describe advantageous embodiments the invention.

In the drawing, the invention is illustrated in several exemplary embodiments - partly schematically. It demonstrate :

1 shows a hydraulic piston rail brake in partial longitudinal section;

FIG. 2 shows a partial side view of FIG. 1;

3 shows a further embodiment, also in partial longitudinal section and

4 again shows a further embodiment of the invention

The reference numeral 1 denotes a wheel of a railway car, not shown, which is on a conventional rail 2 with vertical web 3 and foot 4 rolls. The reference number 5 denotes the flange of the wheel 1, the one Head 6 of a hydraulic piston track brake 7 when rolling over downwards, ie centrally in direction X against a hydraulic damping force pushes. The one in the piston rail brake 7 provided valves correspond to conventional constructions of such hydraulic piston rail brakes and are therefore not necessary for an understanding of the invention and have therefore not been shown.

In all of the embodiments shown in the drawing, the damper 7 can with regard to the response speed the car can be trained so that only the so-called Gutin ufer of the dampers 7 are detected and slowed down while the bad runner delayed less or not at all. In order to So the Goschwind ig can wedge and the distance hold u η cj the not daroes te 111 en E i üenbahnwacjon qercqolt been.

Patent attorney Rudi Beyer Gneisenaustraße 1 D-4030 Raunten 6 (pants!)

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Each of the dampers 7 exists in the illustrated embodiments from two: telescope-like, aiso variable-length telescope parts 8, 9, which are guided into one another form a piston-cylinder unit. These telescopic parts 8 and 9 also take - which is also from the drawing does not emerge - the hydraulic damping medium and the valve devices on.

1 clearly shows that the telescope part, which is smaller in diameter, is used in this embodiment at the top, d. H. the end of the damper facing the wheel 1

7 is arranged and here by means of a snap ring 11 or in some other suitable manner releasable with the head 6 is coupled. This head 6 is in the embodiment according to Figure 1 approximately linsenförmi usges and is given by a bevel an upward, approximately convex Design. This head 6 engages in the embodiment according to Figure 1 in a guide tube 12 and is fixedly but detachably coupled to this by thread 13. That too Guide tube 12 runs coaxially to the telescope parts

8 and 9 and ends at a certain length distance - with the damper 7 pushed together - in front of the end of the telescopic part 9. As a result, the guide tube 12 moves together with the head 6 and the telescopic part 8 in the longitudinal direction of the damper 7.

The telescopic parts 8 and 9 and the guide tube 12 are coaxial arranged in a bearing tube 14, which is welded at its end facing the ground 15 by a Plug 16 is tightly closed. This plug 16 serves at the same time to support the telescopic part 9, which is mounted on the stopper 16 via a space hinge 17 is. This space joint 17 is formed by a spherical cap which is connected to the end face of the telescopic part

9 is firmly connected and rests in a bearing recess of the plug 16 of adapted shape. The guide tube 12 is via two spaced-apart slide bearing rings 18 and 18a fastened in the bearing tube 14 Can be moved lengthways and without tilting. aside from that is at the front, upper end of the bearing tube 14 a wiper seal 19 is arranged in the bearing tube 14, which is located on the outer, cylindrical jacket surface of the guide tube 12 leads.

Patent attorney Rudi Beyer Gneisenaustraße 1 D-4030 Ra'tinyfcn 6 (Höstil) ¹

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The telescope telescope 9, which is larger in diameter, can also be arranged at the top, while the telescopic part B is at the bottom, that is, where in Fig. 1 the telescopic part 9 is arranged. In addition, it is possible in this case to arrange the space joint 17 instead of below, above, z. B. to form the head 6 itself spatially articulated, for. B. in that the head 6 is made of a rubber-like elastomer will be produced. Furthermore, it is conceivable, above and below, that is, in the area of the head 6 and in the area of the Plug 16 each to arrange a space hinge to prevent tilting of the telescopic parts 8 and 9 with eccentric Exclude force introduction.

The reference numeral 20 denotes a retaining tab, which has a supporting surface 21 which runs parallel to the underside of the foot 4 and on which the foot 4 rests. With the retaining tab 20 is one piece in terms of material upwardly open bearing or a bearing socket 22 connected on which the bearing tube 14 with the interposition of a Spacer ring 23 rests with a ring shoulder 24. The bearing 22 has a cylindrical through opening 25 through which the bearing tube 14 engages.

A clamping lug 26 is connected to the bearing 22 and is equipped with a bevel 27 adapted to the foot 4 is that rests as full as possible on the corresponding slope of the foot 4. Otherwise is between the support surface 21 and the bearing 22 a recess 28 is provided into which part of the foot 4 of the rail 2 is positively locked intervenes.

As can be seen in particular from FIG. 1, the applies Retaining tab 20 on the side opposite the bearing 22 so far beyond the local foot area that here space for two in the longitudinal direction of the rail 2 with Clearance is given through bores arranged from one another, of which only one 29 can be seen from FIG. 1, while the other through hole 30 in Fig. 2 only the center line has been illustrated. This The center line became the reference number of the relevant Assigned through hole. Through the through holes 29 and 30 each engage a screw, of which only screw 31 is illustrated in FIG. These Screws have a hammer-like head 32, which

Patent attorney Rudi Beyer Gneisenaustraße 1 D-4030 Haiihgen '6 (Kös "ei. \ > '

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is inserted from below in a form-fitting manner into a corresponding depression in the relevant through-hole 29 or 30 and is thereby secured against rotation. From above, a clamping piece 33 engages against the shoulder of the retaining tab 20 and against the adjacent foot part 4 _; so that after the nuts 34 of the screws 31 have been tightened, the hydraulic piston brake is connected to the rail 2 by clamping, that is to say in a non-positive manner. The longitudinal axis 35 of the damper 7 runs at an acute angle to the longitudinal axis 36 of the rail 2.

The structure of the only indicated schematically in Fig. 3 Embodiment is essentially the same as in the embodiment of Figures 1 and 2, so that the same reference numerals have been used for parts with the same function. However, while in the embodiment According to Figures 1 and 2, the head 6 consists entirely of a rubber-like elastomer, which forms a shock absorber, this shock absorber 38 is in the embodiment of FIG. 3 by a convex Layer formed between a metallic cover 39 and the guide tube 12. To this end, the metallic cover 39 has a concave bearing recess 40 with which the shock absorber 38 by gluing and / or Vulcanizing is connected.

The telescopic part 9 is also such a concave bearing recess 41 assigned, in which the shock-absorbing body 38, likewise by gluing and / or vulcanizing, is attached is.

All of the execution farms shown in the drawing a cooling device 42 is assigned, its not shown The cooling medium is hydraulic oil. But it can of course, other suitable cooling media in Be considered, z. B. Frigen.

In the embodiment according to FIG. 1, the bearing tube penetrates 14 two circular, coaxially arranged openings 43 and 44, both of which open out to the outside.

Patent attorney Rudi Beyer Gneisenaustraße 1 D-4030 Ratln ^ en 6 (M'ösei)

ti «I I

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The bearing tube 14 is through on its outer circumferential surface only schematically indicated seals 46 and 47 are sealed coolant-tight to the outside.

The connection of the coolant tank designed as a connection piece 45 with the bearing tube 14 is carried out by snap rings 48 for retention. Can be used as an anti-twist device a nose 49 on the connecting piece 45 is used, which engages in a recess 50 of the retaining tab 20.

Of course, it is also possible for the bearing tube 14 to be polygonal at least on its outer circumferential surface to design and to lock it against the retaining tab 20 and / or against the intermediate piece 45 against rotation, for which purpose the openings 43 and 44 can be correspondingly adapted in terms of shape.

The coolant tank 45 is provided with a plurality of vertically extending cooling fins 51, which is made of the drawing, however, cannot be seen in detail.

A fill level and compensation chamber 53 is connected to the interior 52 of the coolant container 45, the in the embodiment shown in FIG. 1 as Tube is formed which opens into the interior 52 of the intermediate piece 45 and at its upper mouth opening is releasably closed by a screw plug 54, which is only indicated schematically. The volume of this Filling level and compensation space 53 is dimensioned so large that any bubbles or eddies that occur during actuation the hydraulic piston brake could arise in the interior, can compensate here.

As can be seen, this surface 55 of the cooling medium normally extends so far that the one telescopic part 9 is almost always completely surrounded by the cooling medium.

56 and 57 represent flow openings, which the interior of the bearing tube 14 with the interior 52 of the coolant container 45 in a coolant-conducting manner and with one another in a streamlined manner associate.

Patent attorney Rudi Beyer Gneisenaustraße 1 D- * t030 Ra'tlngtn 6 (Hösel)

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The bearing tube 14 and the level and compensation space 53 form, so to speak, the U-legs of a structure with a U-shaped cross-section, the web of which is formed by the intermediate piece 45 is shown.

In the embodiment shown in FIG. 3 are The same reference numerals have been used for parts with the same function as in the embodiments described above.

The embodiment of FIG. 3 differs from the embodiment according to FIGS. 1 and 2 still characterized by that the cooling device is designed slightly different. While one embodiment of FIG. 1 is usually for If lower thermal loads are used, the embodiment according to FIG. 3 is for larger thermal loads Designed for stresses. In this embodiment the intermediate piece 45 is designed to be larger in volume, so that a considerably larger amount of cooling medium is accommodated can be. Instead of a level and compensation space as in the embodiment according to FIGS. 1 and 2, one is Embodiment according to FIG. 3 parallel to the hydraulic Damper 7, a cooler 58 connected, which in this embodiment as a tube with a large storage capacity for the cooling amount is used. The cooler 58 is like the bearing tube 14 with the intermediate piece 45 via snap rings 59 and seals 60 or 61 connected in a coolant-tight manner. In the area of the interior 52, the cooler 58 has two coaxially to one another arranged through-flow openings 62 and 63, which thus open out into the interior 52 and in the rest of the from Fig. 3 apparent embodiment coaxial to the Through-flow openings 56 and 57 are arranged.

In this embodiment too, the cooler 58 is the same far filled with cooling medium that the telescopic part 9 flows around practically in every operating position of the cooling medium and experiences intensive cooling as a result.

The reference numeral 64 denotes a screw cap which closes the upper mouth opening of the cooler 58. If necessary, cooling medium can be passed through this opening refill.

Also in the embodiment according to FIG. 3, the hydraulic Damper 7 with the cooler 8 and the intermediate piece 45 a U.

Patent attorney Rudi Beyer Gneisenaustraße 1 D-i (030 Ratingen 6 (Hösel)

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In all embodiments, in the telescopic part 9 resulting heat dissipated by the cooling medium. By actuating the guide tube 12, the above the surface 55 of the cooling medium located air 65 is compressed, which when relaxing for a corresponding circulation of the cooling medium within the supply in the connection piece 45 and in the level and compensation space 53 or in the cooler 58 cares. This is also promoted by the large throughflow openings 56 or 57 and 62 or 63.

In the embodiment according to FIG. 3, this is not the only thing Intermediate piece 45 the mentioned vertical cooling fins 51, but also the cooler 58 is with a plurality of cooling fins, in particular vertical cooling fins 66.

The small volume of oil in the telescopic part 9 is due to the cooling medium, ζ. B. oil, the cooling system many times over enlarged, su that in addition to an oil cooling in the telescopic part 9 itself also considerably longer heating times of the overall system can be achieved. A further increase in the mass to be heated is also achieved in that Via the telescopic part 9, which is surrounded on all sides by the cooling medium, the retaining bracket 20 and, in part, the running rail 2 with it be included. This also leads to an enlargement of the radiating surface and thus to less intense heating the piston rail brake.

In all cases, the level or equalizing pipe 53 or the cooler 58 should be at least as high as the actual bearing tube 14.

Contrary to the illustration, the cooler 58 or the filling level and compensating pipe 53 with the connecting piece 45 be formed in one piece in terms of material, for example by injection molding these parts.

In the embodiment according to FIG. 3, too, the cooler is 58, in particular by a nose, arranged so that it cannot rotate.

In the embodiment according to FIG. 4, this is in plan view shown track on one side assigned a plurality of hydraulic piston track brakes 7, which over Coolant lines to a central cooling device 42 are connected. Only one of the connecting lines has been designated with the reference numeral 67.

Patent attorney Rudi Beyer Gnelsenaustraße 1 D- £ | O3O Ratingen 6 (Hösel)

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The cooling device 42 has a not shown in detail engine coolant system on, e.g. B. a compressor, which the WMrmeaustauschmedium, z. B, Frigen, to the individual hydraulic piston rail brakes 7 transported and also promotes it back again. This can be a achieve intensive cooling of a plurality or plurality of hydraulic piston rail brakes.

Those described in the description and in the claims and features shown in the drawing can be used both individually and in any combination for the Realization of the invention be essential.

Patent attorney Rudi Beyer Gneisenaustraße 1 D- * t030 Ratingen 6 (Hösel) '

Literature Clhinis

DE-OS DE-OS DE-OS DE-OS

DE-PS DE-AS

1 530

1 605

2,043,1605

1 162

1 183

Dowty brochure "Oleo Track Brakes - DHU / 261/1/400 / TY 2/76 "

Dowty brochure "Hydraulic Units Lt DHU / 268 / l / lOOO / TY April 1976 "

Patent attorney Rudi Beyer Gneisenaustraße 1 D ~ / f030 Ratingen 6 (Hösel)

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Reference number list

1 wheel _ 2 rail Snap ring 3 web Guide tube 4th foot thread 5 Flange Bearing tube 6th head soil 7th Piston brake, damper Plug 8th Telescopic part Space joint 9 Il Plain bearing ring 10 π 11th Wiper seal 12th Retaining tab 13th Support surface 14th Bearing, bearing pan 15th Spacer ring 16 Ring shoulder 17th Through opening 18th Clamp attachment 18a Slope 19th Recess 20th Through hole 21 Il 22nd Robbery 23 head 24 KIEM PIECE 25th mother 26th Longitudinal axis 27 Il 28 29 30th 31 32 33 34 35 36

ϊ 4
| Ι) II Shock absorbers Patent attorney Rudi Beyer Gneisenaustraße 1 D-4030 Ratinger Cover, reinforcement - 21 - Bearing recess 38 Il 39 Cooling device 40 opening 41 Il 42 Coolant tank, intermediate piece 43 poetry 44 45 Snap ring 46 nose 47 Recess 48 Cooling fins 49 inner space 50 Level and compensation space, pipe 51 Screw plug 52 surface 53 Flow opening 54 Il 55 cooler 56 Snap ring 57 poetry 58 59 Flow opening 60 61 Screw cap 62 air 63 Cooling fins 64 Connecting cable 65 Direction of movement 66 Direction of movement 67 X Y

Claims (1)

Protection claims Hydraulic piston track brake for braking railroad cars, the piston track brake being arranged on a rail by a holder, thereby gekenozeiclhiimiEt that a cooling device (z. B. 42) is assigned to the piston track brake. J Hydraulic piston rail brake according to claim 1, dadmirch gelkemezelclhiniet that the hydraulic damper (7) is arranged - at least partially - in a cooling container (45) filled with the cooling liquid. _t Hydraulic piston rail brake according to claim 2, dadiuirch gelkeeimzelclhipet that the hydraulic damper (7) through coolant lines (e.g. 67) with the cooling container (45) and / or the cooling device (42) Conducting coolant in the sense of a certain spatial shape connected is . Patent attorney Pudi Beyer Gnelsenaustraße 1 D-i (030 Ratingen 6 (Hösel) Hydraulic piston rail brake according to claim 1 or one of the following, characterized in that the hydraulic damper (7) and the cooling device (42) form a U-shaped basic shape with each other in a vertical section straight through the longitudinal axis of the hydraulic damper (7). Hydraulic Kalbengleisbremse according to claim 1 or one of the following, wherein the hydraulic damper is surrounded by a guide tube with radial spacing and is arranged with this in a bearing tube open at the top together with the damper adjustable in the longitudinal direction and that the bearing tube in one of the rail foot reaching under Rail foot non-positive, e.g. B. clamped, holding bracket is mounted, characterized in that the bearing tube (14) is arranged with part of its length in the coolant container (45) or in a connecting piece connected to the coolant container and that the interior of the bearing tube (14) via flow openings ( 56, 57) is connected to the cooling container (45, 53, 58) in a coolant-conducting manner. Hydraulic piston rail brake according to Claim 1 or one of the following claims, characterized in that the connecting piece (45) is a flat container with a rectangular cross-section. Hydraulic piston rail brake according to claim 1 or one of the following, characterized in that a fill level and display space (53) or a tubular cooler (58) is arranged parallel to the hydraulic damper (7) and is approximately filled with cooling medium and that the fill level and compensation space ( 53) or the tubular cooler (58) communicating with the bearing tube (14) or the guide tube (7) is connected in a cool-medium-conducting manner. Patent attorney Rudi Beyer Gneisenaustraße 1 D-4030 Ratingen 6 (H'osel) " 8. Hydraulic piston rail brake according to claim 1 or one of the following, dadorclh gekemozelclhnet that j the coolant tank and / or the connector S (34) and / or a level and compensation space j (53) and / or a tubular cooler (58) on their j outer surfaces with a variety of particular vertical cooling fins is provided. ! 9. Hydraulic piston track brake according to claim 1 or j one of the following, dadiurclh gielkeiniinizelcltunet that the intermediate piece (45) parallel and at a distance C. j to each other each have a pair in each case coaxially to one another S arranged openings (43, 44), wherein through which a pair of said openings (43, 44) the \ bearing tube (14) of the hydraulic damper (7) back; reaches through and locked here and opposite the Walls of the coolant container (45) is arranged sealingly ', while by the other pair of Openings of the cooler (58) in the same way; goes through and also sealed here and how the bearing tube (14) is arranged so that it cannot rotate. '■ 10. Hydraulic piston-type rail brake according to claim 1 or one of the following, daduirclh gekennTizeiiclhiiniet., That only the bearing tube (14) is arranged sealed to the associated hydraulic damper (7) in the intermediate piece (45) and through the throughflow ; (56, 57) is in communication with the interior (52) in a coolant-conducting manner. (11. Hydraulic piston rail brake according to claim 1 or one of the following, thereby gelkeirwruzeiclhniet that the cooler (58) extends approximately to the height of the head (6) of the hydraulic damper (7). 12. Hydraulic piston rail brake according to claim 1 or one of the following, thereby germinating that Connection piece (14) and cooler (58) materially in one piece, in particular as an injection molded part 1 det are. Patent attorney Rudi Beyer Gneisenaustraße 1 * D-AÖ30 Ratingen 6 (HöseI) ' 13. Hydraulic piston rail brake according to claim 1 or one of the following, dadwirclhi characterized in that parallel to the hydraulic damper (7) a level and compensation space (53) is arranged, which opens into the interior (52) of the connecting piece (45). 14. Hydraulic piston rail brake according to claim 13, characterized in that the level and compensation space (53) is formed by a smooth-walled tube with a screw cap (64) closing the upper mouth opening. 15. Hydraulic piston rail brake according to claim 1 or one of the following, characterized in that the bearing tube (14) secured against rotation via a nose (49), for. B. is arranged in a recess (50) of the retaining tab (20). 16. Hydraulic piston rail brake according to claim 1 or one of the following, characterized in that the larger diameter part (9) in the bearing tube (14) is arranged at the bottom and is supported via the space joint (17) on the end wall of the bearing tube (14)