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(11) | EP 2 999 821 B1 |
| (12) | EUROPEAN PATENT SPECIFICATION |
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| (54) |
SWITCH WITH STRAIGHT LINE AND TURNING LINE WEICHE MIT GERADER STRECKE UND KURVENSTRECKE AIGUILLAGE AVEC LIGNE DROITE ET LIGNE DE VIRAGE |
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| Note: Within nine months from the publication of the mention of the grant of the European patent, any person may give notice to the European Patent Office of opposition to the European patent granted. Notice of opposition shall be filed in a written reasoned statement. It shall not be deemed to have been filed until the opposition fee has been paid. (Art. 99(1) European Patent Convention). |
Technical Field
[0001] The technical solution relates to a switch with straight line and turning line, with one rail of the track to consist of a latch movable towards the relevant stock rail.
Hitherto State of the Art
[0002] When a carriage passes through a switch, there changes the direction of power effects operation. When driving on the turning line of a switch, the rails are subject to vertical power effects as well as to significant power effects (guiding powers) in transversal direction. The rising powers are restrained by switch parts - by latches, rails of the central part and the frog. Due to arrangement of possibility for the carriage to change the travel direction, the parts of the switch must be construction adjusted in such a way so as to arrange gradual and fluent ride from straight direction to the turning line and vice versa.
[0003] From this point of view, latch is the most important part of the switch. There are flexed latches in switches and switch constructions. For arrangement of the above stated function it is necessary for the latch to have an appropriate geometrical shape. As from the beginning of the latch tip its width gradually increases. That indicates that at the beginning of the latch tip the width is the smallest and it is exactly this area where maximal stress and wear and tear occur due to power effects operation - the stress and wear and tear is caused by repeated touch (transversal power impulse) at the beginning of the contact zone of rolling outline of the wheel and the latch. Due to operation strains there may develop rollovers, crumbling, material drawing, which may cause even chipping of material in the form of an edge in the length of several dozens of centimetres. The stress and intensity of wear and tear depend mainly on geometry, directional layout and speed of movement on the switch. That is why there appeared a solution, that is based on flexion of the stock rail in as many as 15 mm, which leads to strengthening of latch in incriminated area as well as to more fluent passage of the carriage through the switch / turn out with minimisation of side attacks of the latch by the flange. The disadvantage of the solution is the necessity of use of different cross-ties respectively slide plates in the area of stock rail flexion and significant step extension of the pitch, which may be evaluated by the measuring carriage as a fault.
[0004] Another solution according to EP 1516091 is the solution considering finishing of the stock rail head. The finishing is performed on the stock rail as from the beginning of the latch with the value of 0 mm and it increases up to the maximal value of stock rail finishing. At that point, the slope changes, i.e. there decreases the value of finishing of the stock rail head side up to the value of 0 mm. The disadvantage is the sudden increase of finishing of the stock rail head side from 0 mm to maximal value and non-reaching of maximal value of the latch strengthening in a longer section in the field of increased stress of the latch tip.
Technical Solution Base
[0005] The aim of the technical, solution is to reduce to the maximal possible extent the wear and tear of the switch and to reach on the maximal possible level for the real turn-off to theoretically approach even more the drive way and so as there occurs - compared to the known state of the art - further reduction of power effects of carriages and consequently prolongation of service life of the latch.
[0006] This can be reached to a significant level by a switch with straight line and turning line with one rail of each track consisting of the latch movable in relation to the stock rail according to the technical solution based on the fact that the depth of recession in the stock rail increases up to the spot of beginning of maximal stress of the latch, while the depth of recession in the section of maximal stress of the latch is constant and as from the end of the section of maximal stress the depth of recession fluently reduces up to the zero value.
[0007] It is purposeful for the tip of the latch to abut against the stock rail in recession in the stock rail, while in the place of contact of the latch tip with the stock rail, the depth of recession in the stock rail is bigger or it is equal to the value from the formula d= L5*a/ (L3+ L5)
[0008] Depending on load, it is suitable to select maximal depth of recession in the stock rail within the range 1 - 6 mm.
[0009] In consideration of the maxima! possible load/stress of the latch it is suitable if as from the beginning of maximal depth of recession the width of the latch surpassing the recession increases from the value of 2 mm up to the value of 15 mm in the end of the constant depth of recession in the stock rail.
[0010] From the functional point of view it seems favourable for the beginning of the latch to abut against the stock rail in values of lengths that are defined by formulas
List of Figures in Drawings
[0011] The technical solution will be explained in detail using the drawings, schematically showing Fig. 1 top view of a part of the switch, where the latch abuts against the stock rail, Fig. 2: cross section in point A-A from Fig. 1 and Fig. 3 cross section according to Fig. 1 in point B-B, Fig. 4 cross section in point C-C according to Fig. 1 and Fig. 5 cross section in point D-D according to Fig. 1 .
Description of Sample Designs
[0012] Switch with straight line and turning line according to the technical solution, partially shown in Fig. 1 in the place where tip 3 of the latch 4 of the turning line 5 abuts the stock line 1 of the straight line 2. The latch 4 and the stock rail 1 are a part of the half of the switch or switch construction. The latch 4 may reach two positions. In case of the latch 4 to be in position abut against the stock rail 1, the wheel of the non-shown carriage moving on the stock rail 1, gradually enters the latch 4 and the load is passed from the stock rail 1 to the latch 4 and simultaneously, the carriage turns off. If the latch 4 goes off the stock rail 1, a free space is developed between them and it is designed for passage of the wheel on the stock rail 1 to the opposite direction.
[0013] The contact surfaces of the tip 3 of the latch 4 and the stock rail 1 are machined / finished usually under some slope, but they may also be machined vertically in such a way that on the contact side 41 of the tip 3 of the latch 4 - in the area where maximal operation problems with pulling of the tip 3 of the latch 4 - the strengthening of the tip 3 of the latch 4 reaches the maximal value. The area can be found in section L between sections B-B and C-C according to figure. 1. So as to arrange an increase of width of the tip 3 of the latch 4 on its contact side 41, the machining of the stock rail 1 starts in the location of section A-A before beginning of the latch 4. Between the sections A-A and B-B according to Fig. 1 in the section of L1 length, there gradually increases the depth of recession 11 of the stock rail 1 from the value 0 mm to the maximal value a at the tip 3 of the latch 4 gradually increases in width surpassing the recession from the value b=2 mm up to the value c=15 mm. The value of recessing of the tip 3 of the latch 4 to the recession 11 of the stock rail 1, which in the maximally stressed area depending on the stress may reach the values within the range a=1-6 mm. But in the section with the length L between sections B-B and C-C, the depth "a" of recession 11 of the stock rail 1 and so also the depth of recession of tip 3 of the latch 4 to the stock rail 1 constant. Behind the place of section C-C up to the place of section D-D in the length L2 the value "a" of the depth of recession 11 in the stock rail 1 and recession of the tip 3 of the latch 4 to recession 11 in the stock rail 1 gradually decreases to zero.
[0014] The shape of the tip 3 of the latch 4 and the stock rail 1 is reached by machining in the field starting before the beginning of the tip 3 of the latch 4 so as to reach maximal prolongation of the area of gradual extension of pitch and consequently more fluent passage of the carriage through the switch. The lengths of inlets L1 and outlets L2 must be designed in such a way so as to be gradual and allow fluent passage and o as they respect given geometry. The proposed measured enlarge the area of the latch section and they increase the width of the latch in the field of maximal side load and wear and tear of the tip 3 of the latch 4 by the wheel outline. The length of the section of constant recession of the latch to the stock rail "L" set by the thickness of the latch tip surpassing the value of recession corresponds with the formula:
The distance of the beginning of the section with constant recession from the beginning of radius corresponds with the formula:
The minimal overlap of the beginning of recession before the beginning of the latch:
[0015] The values of machining of the tip of the latch and the stock rail are considered in horizontal plane placed 14mm under the level of the highest point of non-machined latch and stock rail. On the inner side of the rail oriented away from the axis of the rail, the crossing is called "travelled edge".
Samples of technical Solution Realisation
Example 1
[0017] The beginning of the tip 3 of the latch 4 abuts against the stock rail 1 in recession 11 in the stock rail 1, while in the point of contact of the beginning of tip 3 of the latch 4 with the stock rail 1, the depth of recession 11 in the stock rail 1 reaches 0,5 mm. The maximal value and strengthening of the tip 3 of the latch 4 on its contact side 41 is measured as from the beginning of the tip 3 of the latch 4 is in the distance of L3=1018 mm and the distance is 3mm, while maximal value and strengthening of the tip 3 of the latch 4 can be found in the point of transfer of the depth of recession 11 in the stock rail 1 from the length of L1= 1236 mm to L=1103 mm that means that the original width of the latch is 2mm (in the distance L) respectively 5mm (in the distance L+L1) it increases in the above specified 3mm. The lengths L1=1236 mm of the inlet and L2=2500 mm of the outlet must be gradual so as to allow fluent passage and to respect the geometry of the tip 3 of the latch 4. The above described adjustments of the stock rail 1 and tip 3 of the latch 4 arrange an increase of the surface of section of the tip 3 of the latch 4 and an increase of its width in the field where maximal load / stress occurs as well as wear and tear of the tip 3 of the latch 4 by the rolling outline.
Example 2
[0019] The beginning of the tip 3 of the latch 4 abuts against the stock rail 1 in recession 11 in the stock rail 1, while in the point of contact of the beginning of tip 3 of the latch 4 with the stock rail 1 the depth of recession 11 in the stock rail 1 reaches 3,1 mm. The maximal value and strengthening of the tip 3 of the latch 4 on its contact side 41 is measured as from the beginning of the tip 3 of the latch 4 is in the distance of L3=607mm and the distance is 5mm, while maximal value and strengthening of the tip 3 of the latch 4 can be found in the point of transfer of the depth of recession 11 in the stock rail 1 from the length of L1= 1615 mm to L=637,5 mm that means that the original width of the latch is 2mm (in the distance L) respectively 5mm (in the distance L+L1) it increases in the above specified 3 mm. The lengths L1=1236 mm of the inlet and L2=3170 mm of the outlet must be gradual so as to allow fluent passage and to respect the geometry of the tip 3 of the latch 4. The above described adjustments of the stock rail 1 and tip 3 of the latch 4 arrange an increase of the surface of section of the tip 3 of the latch 4 and an increase of its width in the field where maximal load / stress occurs as well as wear and tear of the tip 3 of the latch 4 by the rolling outline.
Industrial Applicability
1. Switch with straight line (2) and turning line (5) with one rail of each said line
consisting of a latch (4) movable in relation to the corresponding stock rail (1)
of the switch, each stock rail (1) comprising a recession (11), whereby the depth
of recession (11) in the stock rail (1) increases up to the place of beginning of
maximal stress of the tip (3) of the latch (4), characterized in that consequently, the depth of recession (11) in the section of maximal stress of the
tip (3) of the latch (4) is constant and as from the end of the section maximal stress
the depth of recession (11) fluently decreases up to zero value.
2. Switch according to claim 1, characterised by the fact that tip (3) of the latch (4) abuts against the stock rail (1) in the recession
(11) in the stock rail (1), while in the place of contact of the tip (3) of the latch
(4) with the stock rail (1) the depth (x) of the recession (11) in the stock rail
(1) is bigger or equals the value from the formula d= L5*a/(L3+ L5)
3. Switch according to claim 1 and 2, characterised by the fact that maximal depth of recession (11) in the stock rail (1) is within the
range 1 - 6 mm.
4. Switch according to claim 1 and 3, characterised by the fact that as from the beginning of maximal depth of recession (11) the width
of the tip (3) of the latch (4) surpassing the recession (11) increases from the value
of 2 mm to the value of 15 mm in the end of constant depth of recession (11) in the
stock rail (1).
5. Switch according to any of the claim 1 up to 4, characterised by the fact that the beginning of the latch (4) abuts against the stock rail (1) in
length values that are defined by relations
1. Weiche mit einem geraden Gleis (2) und einem Zweiggleis (5), bei welchen eine Schiene
jedes gegebenen Gleises von einer zur entsprechenden Backenschiene (1) beweglichen
Zunge (4) der Weiche gebildet wird, jede Backenschiene (1) beinhaltet dabei eine Aussparung
(11), wo die Tiefe der Aussparung (11) in der Backenschiene (1) sich bis zur Stelle
des Anfangs der Maximalbelastung der Spitze (3) der Zunge (4) vergrößert, gekennzeichnet dadurch, dass die Tiefe der Aussparung (11) also im Abschnitt der Maximalbelastung der Spitze (3)
der Zunge (4) konstant ist und ab dem Ende des Abschnittes der Maximalbelastung sich
die Tiefe der Aussparung (11) reibungslos zum Nullwert verkleinert.
2. Weiche nach Anspruch 1, gekennzeichnet dadurch, dass die Spitze (3) der Zunge (4) an die Backenschiene (1) in der Aussparung (11) in der
Backenschiene (1) anliegt, wobei an der Kontaktstelle der Spitze (3) der Zunge (4)
mit der Backenschiene (1) die Tiefe (x) der Aussparung (11) in der Backenschiene (1)
grösser oder gleich dem Wert vom Verhältnis d = L5*a/(L3+L5) ist.
3. Weiche nach Anspruch 1 und 2, gekennzeichnet dadurch, dass die Maximaltiefe der Aussparung (11) in der Backenschiene (1) im Bereich von 1-6
mm liegt.
4. Weiche nach Anspruch 1 und 3, gekennzeichnet dadurch, dass ab dem Anfang der maximalen Tiefe der Aussparung (11) an sich die die Aussparung
(11) überragende Breite der Spitze (3) der Zunge (4) von einem Wert von 2 mm bis zum
Wert von 15 mm am Ende der konstanten Tiefe der Aussparung (11) in der Backenschiene
(1) erhöht.
5. Weiche nach einem der Ansprüche 1 bis 4, gekennzeichnet dadurch, dass der Anfang der Zunge (4) an die Backenschiene (1) anliegt, in Längenwerten, welche
von den folgenden Verhältnissen definiert werden
1. Aiguillage comprenant une voie directe (2) et une voie déviée (5), chaque rail de
chacune des voies concernées étant formée par une lame d'aiguille (4) mobile par rapport
au rail contre-aiguille (1) respectif, chaque rail contre-aiguille (1) comportant
un évidement (11), où la profondeur de l'évidement (11) dans le rail contre-aiguille
(1) augmente jusqu'au point de début de la sollicitation maximale de la pointe (3)
de la lame d'aiguille (4), caractérisé en ce que la profondeur de l'évidement (11) étant, par conséquent, dans le tronçon de la sollicitation
maximale de la pointe (3) de la lame d'aiguille (4) constante et en ce que la profondeur de l'évidement (11) diminue en continu à partir de la fin du tronçon
de la sollicitation maximale juqu'à un valeur nulle.
2. Aiguillage selon la revendication 1, caractérisé en ce que la pointe (3) de la lame d'aiguille (4) s'applique contre le rail contre-aiguille
(1) dans l'évidement (11) dans le rail contre-aiguille (1), au point de contact de
la pointe (3) de la lame d'aiguille (4) et du rail contre-aiguille (1) la profondeur
(x) de l'évidement (11) dans le rail contre-aiguille (1) étant supérieure ou égale
à la valeur découlant de la relation : d= L5*a/(L3+ L5)
3. Aiguillage selon la revendication 1 et 2, caractérisé en ce que la profondeur maximale de d'évidement (11) dans le rail contre-aiguille (1) est comprise
entre 1 - 6 mm.
4. Aiguillage selon la revendication 1 et 3, caractérisé en ce que depuis le début de la profondeur maximale de l'évidement (11), la largeur de la pointe
(3) de la lame d'aiguille (4) dépassant l'évidement (11) augmente de 2 mm jusqu'à
15 mm à la fin de la profondeur constante de l'évidement (11) dans le rail contre-aiguille
(1).
5. Aiguillage selon l'une quelconque des revendications 1 à 4, caractérisé en ce que le début de la lame d'aiguille (4) s'applique contre le rail contre-aiguille (1)
à des valeurs de longueur définies par les relations suivantes :
REFERENCES CITED IN THE DESCRIPTION
This list of references cited by the applicant is for the reader's convenience only. It does not form part of the European patent document. Even though great care has been taken in compiling the references, errors or omissions cannot be excluded and the EPO disclaims all liability in this regard.
Patent documents cited in the description