FI79737C - ANALYZING FOER AVESTANDE AV SKENOR. - Google Patents

Description

79737

Device for attaching counter rails or guide rails to gears

The invention relates to a device for fastening counter rails or guide rails in gearboxes with a washer for rails, which has either a slide base for gear tongues arranged on the counter rails or a guide rail support rail with guide rails on the guide rails. or a clamp or clamp mounting on the outside of the rail leg of the counter rail or guide rail. In addition, it consists of a substantially U-shaped resilient handle inserted into the recess extending to the inside of the rail foot, on the underside 15 of the slide surface or guide rail support bracket. with the formations in the upper part or in the guide rail support bracket, and wherein the recess on the underside of the slide or guide rail support bracket or on the upper side of the elastic strap has a convex formation acting as a counter surface when tensioning the elastic member. The slide or guide rail support bracket 25 may be welded to the washer. It can also be a cast or forged slide plate or a guide rail support plate in one piece.

Such devices for fastening rails to gearboxes are known, for example, from DE-AS 2,000,482, DE-PS 2,153,534 and DE-AS 2,409,138. inside as a 2 79737 rail mount (IBAV). In principle, as devices of the same construction, these devices can also be used for fastening rails to gears. as an internal mortgage (IFAV). The inner guide rail fastening (IFAV) differs from the inner 5 counter rail fastening (IBAV) only in that a guide rail support stand is arranged on the rail washer instead of the gear tongue slide base.

Over the last decade, modern railways have increasingly introduced devices 10 for attaching rails to switches operating under an inner counter rail and busbar attachment system. It has been found that the shock-absorbing effect of this system, especially with the inner counter rail attachment, can reduce the steering force by more than 40% compared to the known, outer, rigid counter rail supports. This, in turn, substantially reduces wear on the rails of the gear tongues and also on the wheel rims of rail vehicles. Furthermore, it has been found that the devices for attaching the rails to the gears, the maintenance work of the latter can be substantially reduced, and nevertheless a considerable extension of the service life of the tongue devices can be achieved. Finally, the improved shock absorption of these fastening devices greatly improves driving comfort, namely because there are no jerky lateral accelerations in rail vehicles when driving to the tongue device.

Practical experience has shown that these known inner mounts of the counter rail and the guide rail still have disadvantages in that they have undesired fractures of the clamping handle and the slab, as well as loosening of the support rails of the slides or the guide rail. When the loosening of the slides is mostly due to the system, fractures of the slab occur after a certain service life of 3,79737, especially in heavily stressed gears, such as inner and outer curve gears, which are subjected to high centrifugal forces. Conversely, overload cracks in the tension bars are caused by the very frequent tilting of the rails. These violent fractures are then due to the fact that the overload or inclination limiter arranged on the inner counter rail and guide rail fastenings extends vertically about 1.5 mm above the rail foot at the rounding radius of the slide collar arm. The lever arm acting on this is thus the same as normal with tension. When the rail strikes at an overload or tilt limiter, the tension in the tensioning bar increases linearly in response to the force-travel diagram, so that cracks in the tensioning bar can occur.

15 In order to prevent the vertical deflection distance from becoming too large when the rail is tilted, it is known to reduce the vertical distance between the rail grip and the overload or tilt limiter. However, it has been found that this makes it much more difficult to fit the rails, and in particular the curved counter rails, and that by reducing the distance between the overload or tilt limiter and the rail foot, increased point stresses may adversely affect the origin of the weld at the transition point from the washer to the slide base or guide rail support bracket. In order to reduce the consequent problems, the joint plate is normally annealed in the welding constructions in order to remove the stresses 30 and to improve the joint in the area of the weld seam, as this can prevent the weld seam from tearing. At the end of the annealing phase, however, the entire slab must be straightened again, which incurs high costs.

4,79737

The invention is based on the object of providing a device according to the type definition for fastening rails, and in particular both counter rails and guide rails, to gears, which not only prevents loosening of the slides and guide rail supports, but also prevents fractures of washers and clamps.

According to the invention, the solution to this object is obtained primarily by the features defined in the features of claim 1.

These measures provide the substantial advantage that when tilted from normal stress, the main stress is in a relatively thin cross-sectional area on the chassis plate or guide rail plate, and when tilting 15 rails further, the force application point shifts to a substantially larger not only in the critical cross section of the slide stand or guide rail support bracket, but also in the clamping bracket. It is further preferred that the inner counter rail fastening (IBAV) or the inner rail fastening (IFAVj) comprising the features of the invention has a force-travel characteristic curve in which, in contrast to the force-travel characteristic curve of known structures, there is not only one progression but even two such progressions. which has a positive effect on the size of the clamping height without exceeding the permissible tension of the clamping bracket, in addition to which it is possible to achieve a clamping force of more than three times that of hitherto known structures, which is achieved in particular by shortening the lever arm.

5,79737

In a joint plate made as a welding structure - consisting of a washer and a sliding base or a washer and a guide rail support bracket - the welds are no longer stressed at points at the beginning of the seam, but over a longer distance 5 and especially with respect to sliding. This not only avoids cracking of the slab, but also prevents the welds from tearing due to overload. It is no longer necessary to anneal the welds, so that the straightening of the joint plates is also eliminated and thus the manufacturing costs 10 are considerably reduced.

In one piece, cast or also forged 1-digit base or guide rail support bracket plates, the previous Heikki transition point is avoided, and the main load is applied to a larger cross-sectional area.

15 A particularly important advantage is that the vertical distance between the rail foot and the collar arm of the sliding base or guide rail support that grips on it doubles compared to the previous construction, namely it can be increased from 1.5 to 3 mm without any further, and thus fits curved counter rails even in low-radius gears without problems and quickly. Because tilting the rail results in, due to overload and a new arrangement of the tilt limiter, substantially shortening the lever arm in the tensioning bar, fractures of the tensioning bar 25 can no longer occur in the inner counter rail attachment or inner guide rail attachment.

6 79737

In another embodiment of the device according to the invention for attaching the counter rails and the guide rails to the gearboxes, the features according to claims 2-4 have proved to be particularly advantageous. It has been found that in this way a structure can be obtained in which the retaining force of the rail inclination with respect to the normal stress can increase more than three times without exceeding the permissible stress in the critical cross section. Even when the corrective force of 5000 kp present when adjusting gears with a very har-10 butter occurs, the elongation limit of the clamping bracket is not reached.

From a structural point of view, it has proved particularly advantageous to use the features of claim 5 according to the invention.

According to an embodiment according to claims 6 and 7, the invention provides the advantage that already installed sliding or guide rail support plates can be used to improve the operation of the IBAV and IFAV fasteners and increase their durability by changing the clamping brackets.

Other features and advantages of the subject matter of the invention will be described below with reference to the working examples shown in the drawings.

Fig. 1 shows an inner counter rail fastening according to the invention in its normal stress state, Fig. 2 shows a plan view of the inner counter rail fastening according to Fig. 1, Fig. 3 shows in approximate life a part of the inner counter rail fastening essential to the invention, the rail being subjected to torsional load overload or tilt protection or limiter, 7 79737 Fig. 4 shows an inner guide rail fastening with a structure according to the invention, in a state of normal stress in the longitudinal direction of the rail, Fig. 5 is a plan view of the inner 5 rail fastening according to the invention the area with the rail tilted and the overload or tilt limiter in the operating position, Fig. 7 is a side view and Fig. 8 is a top view of a a part of the tensioning strap which is essential for the invention, which bracket is intended for retrofitting to already existing internal mounts of the counter rail or guide rail.

In the device shown in Figures 1-3 of the drawing for fastening the counter-rails, the counter-rail 1 is placed with its rail foot 2 on a washer 3, which is fastened in the usual way to the sleeper with screws or the like.

The washer 3 has a side 4 against which the rail foot 2 rests. By means of a tightening screw 5 and a nut 6 attached to the side 4, it is possible, for example, to press the tightening plate 7 onto a part of the rail foot 2 adjacent to the side 4.

On the opposite side of the counter rail 1 there is a sliding base 8 on the washer 3 for the gear tongue, which base extends over the adjacent - inner - part of the rail foot 2 with a clearance. The washer 3 and the sliding base 8 can then be welded together. It is also possible to make these as one kappa-30 Leena by casting or forging.

s 79737

On the one hand, the slide 8 and on the other hand the base 3 delimit a recess 10 which extends over the entire length of the slide. At the end of the slide 8 facing away from the rail foot 2 there is a recess 12, which is limited by the side strips 13 and each has a shoulder 14 on the inner side with support stops 15. The shoulders 14 are raised relative to the washer 3 so that a distance is created between them and the washer 3 16.

In the tensioned state, the resilient bracket 17 can be introduced through the recess 10 into the recess 10 of the sliding base 8, so that the loop part 18 slides close to the end part 11 of the recess 10 on the inner part of the rail foot 2. In this position of the elastic strap 17, the arms 20 of the strap are at their ends in the area below the shoulders 14, from where they can be pressed inwards below the shoulders 14 against the sieves 15 by means of a supported lever tool and then lifted upwards inside the shoulders 14. The loop part 18 then rests on the upper side of the rail foot 2, while the arms 20 of the handle move on the other hand in the direction of the upper groove surface 21 of the recess 10 of the slide base 8. The upper delimiting surface 21 of the recess 10 of the slide 8 is provided with a convex formation 21 'which, as shown in Fig. 2, extends as a transverse strip over the entire width of the recess 10. The distance 22 'of this convex formation 21' from the delimiting edge 23 of the slide base 8 facing the inner part 25 of the rail foot 2 is preferably 70 mm. Protruding from this boundary edge 23 extends to the part of the slide base 8 in one piece over the inner part of the rail foot 2 with a clearance such that the minimum vertical distance 25 between the edge side edge of the rail 30 and the collar arm 24 of the adjacent slide base 8 is.

3 mm.

9,79737

When levering the bracket arms 20 of the elastic strap 17 to the shoulders 14 of the sliding base 8, these will rest against the convex formation 21 'on their upper surfaces, while still maintaining the distance to the interface 21 of the recess 10 5 in the sliding base 8 and thus force the loop part 18 with a high holding force over the inner part of the rail foot 2.

The support stops 15 in the side strips 13 act together with the end surfaces of the ends 19 of the branches to prevent the elastic bracket 17 from moving longitudinally due to vibrations and / or the horizontal force component of the tension force and thus sliding off the rail foot 2. Furthermore, the side surfaces of the support stops 15 act together with the sides of the ends 19 of the branches so that the resilient bracket 17 does not need any locking towards the rail foot 2 before the loop part 18. Namely, if the elastic strap 17 inadvertently slides on the rail foot, both arms 20 of the bracket-20 should approach a dimension greater than the smallest distance between the bracket arms 20 with respect to the length of the elastic strap, thereby preventing such inadvertent movement of the support stops 15.

At a distance 22 "from the delimiting edge 23 of the slide 8, a second convex formation 21" is arranged on the upper interface 21 of its concavity 10, the distance 22 "being n.

20 to 30 mm and accordingly has a ratio of the first convex formation 21 'to the distance 22' of between 0.25: 1 and 0.5: 1.

10 79737

On the other hand, the height of the second convex formation 21 "relative to the upper interface 21 of the concave 10 is dimensioned so that in the normal stress state of the elastic strap 17, as shown in Fig. 1, between the upper surface 5 of the elastic strap 17 and this convex formation 21" in the loop portion 18 - a gap of 0.5 mm 26. In this way it is ensured that the normal tension of the elastic strap 17 depends only on its loop part 18 resting on the inner part of the rail foot 2, the ends 19 of each of the 10 leg branches rest on the shoulders 14 and have a first convex backing formation 21 '. If the counter rail 1 tilts, e.g. by the arrow 27 in Fig. 3, due to the centrifugal force of the running rail vehicle, the inner part of the rail foot 15 2 rises from the washer 3. The bending force then acts on the loop part 18 of the elastic strap 17, which increases the bias of the elastic around the convex formation 21 'and thus bringing the loop portion 18 to press against the second convex formation 21 ". At this point, the bending lever arm of the elastic strap 17 shortens to a dimension 28 and thus a fraction of the length of the normal tension bending arm. The tilt of the counter rail 1 the effective tilt retaining force increases many to 25 times the normal tension without substantially reducing the distance 25 between the inner part of the rail foot and the collar arm 24. Thus, the resilient bracket 17 completely dampens the tilting movement of the counter rail 1 because its loop portion 11a 18 also has sufficient clearance in the region of the collar arm 24 30 to the upper interface 21 of the recess 10, as is clear from Fig. 3.

11 79737

It can also be seen from Figure 3 that the increased tilt retaining force of the resilient bracket 17 is not applied to the washer 3 in a dotted manner, i.e. not only at the beginning of the weld between the sliding base 8 and the washer 3, but is distributed over a much longer area 30. The length of the joint the angle between the slide 8 and the washer 3 is then determined by the 90 ° angle whose tip is located at the fulcrum formed by the second convex formation 21 "for the resilient part 17, and then the normal plane through this fulcrum corresponds to a 90 ° angle bisector, as shown in FIG. .

The part of the loop part 18 which is still spring-acting alone after settling on the second convex formation 21 "is so designed that the inclination retaining force of the required elastic travel of about 8 mm increases more than three times with respect to the spring force at normal tension, e.g. to about 4000 kp without increasing the allowable tension in the critical cross section of the resilient bracket 17 20. In this case, the recess 10 of the sliding base 8 is dimensioned in its end region 11 so that the loop part 18 of the resilient bracket 17 does not rest on it even when the inner part 24 against the lower surface 25 in the region of the radius of curvature of the boundary edge 23. This applies not only to the welding constructions, but also to the one-piece cast and forged slide and guide rail support girder plates.

Figures 4 to 6 of the drawing show an inner passage-30 rail fastening - IFAV - which has a substantially similar structure to the inner counter rail fastenings - IBAV shown in Figures 1-3.

12,79737

The guide rail 31 also rests here on its rail foot 32 on a base plate 33, which is fastened to the sleeper with screws.

The washer 33 is provided with a side 34 against which the handle 32 rests. With the clamping screw wool 35 and nut 36 attached to the side 34, the clamping plate 37 can be pressed over a portion of the rail foot 32 adjacent the side 34.

On the opposite side of the guide rail 31 there is a guide rail support bracket 38 for the guide rail 39 on the washer 33. The guide rail support bracket 38 thus has two spaced apart supports 10 'and 38 "symmetrically welded to the washer 33 with respect to the base plane 33, between which a free opening 40 is formed which tapers in the direction of the rail foot 2 to a dimension 41 at the end 42 away from the rail foot 32. the guide rail support bracket 15 38 to the supports 38 'and 38 "with two rear counter-supports 43, each having a shoulder 44 with support brackets 45 therewith. The shoulders 44 are thus arranged elevated relative to the washer 33, as is particularly evident from Figure 4, so that there is a distance 46 between them. In the tensioned state, the resilient part 47 can be pushed under the shoulders 44 into the opening 40, whereby its loop part 48 slides into the narrowest area 41 of the opening 40 over the inner part of the rail foot 32. At this position of the resilient handle 47, the ends of the handle arms 50 are located in the distance region 25 below the shoulders 44. For example, by means of a lever tool supported against the side strips 43, they can then be pressed inwards below the shoulders 44 and finally lifted up into these shoulders. The loop portion 48 then rests against the top side of the rail foot 32 while the arms 50 of the handle 30 are raised and will abut the bottom side of the crossbar 51 'interposed between the supports 38' and 38 "of the support bracket 38. By inserting the ends 49 of the handle arms 50 into the shoulders 44, the handle arms 50 are subjected to bending tension 79737 over the crossbar 51 ', and thus force the loop portion 48 with considerable retaining force over the inner portion of the shank 32.

The support stops 45 in the rear abutments 43 act together with the end faces of the ends 49 of the arms 5 and prevent the resilient bracket 47 from moving longitudinally due to vibrations and / or the horizontal force component of the tension force and sliding away from the rail foot 32. with the fact that the resilient bracket 47 needs an additional locking towards the rail groove 32 before the loop part 48.

The crossbar 51 'is placed on the guide rail support bracket 38 or its side supports 38' and 38 "so as to have a distance 52 'from the boundary edge 53 of the guide rail support bracket 38 located in the direction adjacent to the inner part of the rail rail 32. The distance 52' is preferably about 70 mm. In connection with the stop edge 53, the guide rail support bracket 38 or its side sides 38 'and 38 "have a collar arm 54, 20 extending over the inner part of the rail foot 32 with a clearance 55 of at least 3 mm.

At a distance 52 "from the boundary edge 53, the guide rail support bracket 38 or its supports 38 'and 38" are provided with a second transverse strip 51 ", the distance 52" preferably having a dimension of between 20 and 30 mm. The cross strip 51 "is then arranged and formed in such a way that it has a distance 56 from its upper surface of between 0.3 and 0.5 mm in the normal tension state of the elastic strap 47.

14 79737

Both crossbars 51 'and 51 "are preferably formed as part of a shaped body 51 placed on supports 38' and 38" and welded together therewith.

The running rail 31 acting on the direction of the arrow 57, 5 6 according to a horizontal force pattern, the running rail 31 attempts expensive nucleus relative to the base plate 33, as shown in Figure 6 is shown. The inner part of the rail foot 32 then acts on the loop portion 48 of the resilient bracket 47 and first places it around a fulcrum formed by the crossbar 51 'in the direction of the lever arm 59 until it is against the second crossbar 51 ". As a result, the resilient bracket 48 lever arm 58, with the result that the tilt retaining force 15 provided by the elastic strap 47 rises sharply, namely to a value at least three times higher than the normal tension of the elastic force acting on the guide rail 31. Also in this case the elastic strap 47 through the loop portion 48 the force is not applied point by point, but through the welds connecting the supports 38 'and 38 "of the guide rail support bracket 38 to the washer 33, through a relatively large length area 60 to the washer 33, as indicated by the 90 ° angle in Fig. 6 n 51 "at the fulcrum, namely so that its 25th bisector forms a normal plane for the washer 33.

In principle, the same also applies to one-piece cast or forged slide and guide rail plates.

Both the inner counter rail mounting - IBAV - of Figures 1 to 3 and the inner busbar mounting - IFAV - of Figures 4-6 are particularly advantageous when used in heavily stressed outer and inner arc gearboxes.

is 79737 subject to very high centrifugal force overload. The elastic overload or tilt protection achieved by the equipment described above can prevent both welded and cast slabs from breaking in their critical cross-sectional area. It also resists overloading the elastic strap. The welds are no longer loaded in a point-like manner and can therefore potentially be reduced in cross-section.

Figures 7 and 8 show a resilient bracket 67 with an essential front part essential to the invention, which is particularly suitable for use where the gears are already fitted with slipper plates or guide rail support bracket plates with only one convex formation 21 'or 51'.

This resilient bracket 67 with its loop portions 68 and both handle arms 70 is symmetrical not only with respect to the end plane but also with respect to the horizontal plane. It has a convex formation 71 "near its loop portion 68 on both its upper side and its lower side, projecting stepwise from each branch 70 of the handle 20.

At a distance 72 behind the convex formation 71 ", the resilient handle 67 further, again above and below, has a flat support surface 71 'which acts as a contact area for the convex formations 21' or 51 'on the underside of the skid surface 8 or guide rail support bracket 38.

It has proven advantageous when the distance 72 between the convex formations 71 "and the flat support surfaces 71 'is about 50 mm. On the other hand, the height of the convex formation 71" should be dimensioned so that in the normal tension condition of the elastic strap 67 and its slide surface 8 or guide rail support bracket The distance between the 38 sub-sides is 0.3 to 0.5 mm.

Claims (7)

A device for fastening rails, in particular counter-rails or guide rails, to gearboxes, comprising a washer for a rail and a slide-5 base or support stand gear for a tongue or guide rail, a clamping plate or a clamping rail or a clamping rail on the outside, and in an opening extending above the inside of the rail foot, on the underside of the slide base 10, or in a substantially U-shaped resilient rail insert with the openings on the underside of the surface of the sliding surface or in the support rail of the guide rail and / or the elastic bracket on its upper surface being provided with a convex 20 between the convex formation (21 'or 51') and the inside of the rail foot (2 or 32) on the underside of the sliding surface (8) or on the guide rail support bracket (38) or resilient part (17). or 47 25 or 67) is provided with a second convex formation (21 "or 51") with a small clearance (26 or 56) in the normal tension of the tensioning strap (17 or 47) with the upper side of the elastic strap (17 or 47) and / or with the support surface on the slide (8) or on the guide rail support bracket (38). 17 79737 Device according to Claim 1, characterized in that the ratio of the distances (22 ': 22 "or 52': 52 * ') between the two convex formations (21' and 21" or 51 'and 51 ") and the rail foot (2 or 32) between the inner side 5 is 1: 0.25 to 1: 0.5. Device according to one of Claims 1 and 2, characterized in that the distance (22 'or 52') of the first convex formation (21 'or 51') from the inner side of the rail foot (2 or 32) is about 70 mm, while the second convex the distance (22 ”or 52") of the assembly (21 "or 51") from the inside of the rail foot (2 or 32) is 20-30 mm. Device according to one of Claims 1 to 3, characterized in that the clearance (26 or 56) between the second convex formation (21 "or 51") and the abutment surface adjacent to the elastic strap (17 or 47) is 0.3 to 0. 5 mm. Device according to one of Claims 1 to 4, characterized in that the convex formations (21 'and 21 "or 51' and 51") in the slide base (8) or in the guide rail support bracket (38) run transversely in the recess (40) of the opening (40). 10) over the entire width. Device according to one of Claims 1 to 4, characterized in that the elastic strap (67) 25 in each case has a convex formation (71 ") on its upper and lower sides, which extends over each branch (70) of the elastic strap in the form of a transverse strip near the loop part (68). Device according to one of Claims 1 to 4 and 6, characterized in that the resilient bracket (67) is provided at its distance (72) behind the convex formation (71 ") with a flat support surface (71 ') on its upper and lower sides on its upper and lower sides. or 51 ') on the underside of the upper surface of the slide stand or guide rail support bracket (38).