SWITCH WITH DRIVE-OVER MECHANISM

Description

[0001] The invention relates to a switch with an actuating device configured to actuate the switch via a control slide by means of a drive mechanism. The switch has a drive mechanism with a mechanical clutch and a spring element. The clutch is configured to disengage the drive from the control slide when the control slide leaves a target position during the drive mechanism, and the spring element is configured to engage the drive with the control slide when the control slide is in the target position. The invention further relates to an actuating device for a switch, comprising a spring element, wherein the actuating device is configured to be installed in a spring-loaded switch according to one of the preceding claims.

[0002] If a switch is struck by a train traveling in an unpredictable direction, a run-over switch drive should, above a specified impact force, allow the switch blades to move without damage, as forced by the striking wheel. This run-over mechanism in the drive must also be reversible, so that the switch drive is subsequently ready for use again and can return to its original end position. These properties are provided by a return-to-center function of the switch, which can be implemented by a switch drive.

[0003] A run-over turnout is described, for example, in WO 9629227 A1. When the turnout, normally controlled by the turnout motor, is run over (only possible when controlling switch blades, not when controlling a frog), considerable forces are introduced into the turnout motor from the turnout side via the control slide. As soon as the holding force of a locking coupling on the control slide is exceeded, the control slide begins to move in one direction or the other under the influence of the external force (depending on the end position from which the turnout is run over). In this process, the locking slide is pushed out of the recess against the force of a pressure spring by means of ramps on the locking slide and corresponding ramps on a recess in the control slide.Once the locking slide has fully disengaged from the recess of the control slide, the axial fixity of the control slide is released, allowing it to follow the further movement of the switch tongue exposed by the approach.

[0004] The operating mechanism used can employ, for example, a coil spring or a stack of disc springs, which are held in a suitable housing and store energy for the return spring when the switch is opened. In this mechanism, the operating force must overcome a resistance force, which is determined, for example, by a preload force set via an adjusting screw. This preload force then transmits a vertical force to the actuating slide. Accordingly, the resistance force to be overcome is, ideally, a function of the vertical force and the coefficient of friction at the actuating slide.

[0005] Both the vertical force of the ramp coupling and the coefficient of friction change over time (corrosion, contamination, wear). The adjusting screw is subject to settling effects, which can lead to a loss of force. The coefficient of friction at the actuating slide depends on many parameters, including the condition of the lubricant, the surface finish of the friction contact, and any coatings.

[0006] DE 20 2018 101643 U1 also describes a switch drive for a run-over switch.

[0007] The object of the invention is to provide a switch with a ramp mechanism that ensures the most constant possible properties of the ramp mechanism with regard to the forces required for ramping over the operating time.

[0008] This problem is solved according to the invention with the aforementioned subject matter of the claim (switch) in that the spring element consists of a unit or assembly comprising a torsion spring and a bending spring, wherein the torsion spring and the bending spring are mechanically and torsionally rigidly coupled to one another, such that a torque is transmitted between the torsion spring and the bending spring due to the application of a force to the bending spring perpendicular to the axis of rotation of the torsion spring. A unit exists if the torsion spring and the bending spring are permanently connected to one another (for example, by welding). An assembly exists if the torsion spring and the bending spring constitute two components which are connected to one another, for example, by a detachable splined shaft connection. In any case, the connection between the bending spring and the torsion spring is torsionally rigid.In the context of the invention, this means that a bending moment introduced into the torsion spring via the bending spring is transferred completely or at least predominantly to the torsion spring. Of course, no connection between two components is absolutely rigid. However, what is meant here is a connection whose elasticity, compared to the technical spring properties of the torsion spring and the bending spring (elasticity described by a spring constant CB of the bending spring, CT of the torsion spring), is negligibly small and can therefore be technically described as rigid.

[0009] In the context of this invention, "torsionally rigid" also means that a torque, for example, due to a force being applied to the bending spring perpendicular to the axis of rotation of the torsion spring, can actually be transmitted between the torsion spring and the bending spring. The advantage of the rigid connection lies in the fact that the forces introduced into the spring element lead to a deformation of the spring element as a whole without frictional losses (which would act as damping). This also reduces wear effects that would negatively affect the properties and thus the behavior of the approach mechanism during operation. The advantageous consequence is that the spring element exhibits consistent properties even over extended periods of operation, thereby reducing, in particular, the maintenance requirements for the switch drive.

[0010] The spring element, consisting of a torsion spring and a bending spring, also represents the central functional element of a very compact assembly mechanism. The required spring stiffness, i.e., a sufficiently soft spring, is achieved through a mechanical coupling of the torsion spring and the bending spring. This mechanical coupling results in the springs being connected in series, so that the spring stiffness of the spring element is reduced compared to the torsion spring and the bending spring considered individually, according to the formula: CR = CB ⋅ CT / CB + CT with CR resultant spring stiffness CB spring stiffness of the bending spring CT spring stiffness of the torsional spring

[0011] This design advantageously involves a division of tasks within the spring element. The torsion spring can be made relatively soft to primarily absorb the energy introduced into the spring element when the actuating slide is engaged. The bending spring must deform sufficiently to allow the spring element to be released from its receptacle (e.g., recess) in the actuating slide. The deformation of the torsion spring can also provide additional support in this process.

[0012] According to one embodiment of the invention, the bending spring is coupled to the actuating slide at a free end in such a way that a displacement of the actuating slide bends the bending spring.

[0013] In other words, this means that a displacement of the actuating slide must act in a direction that causes a deflection of the bending spring in the direction of deformation (more on this below). This advantageously allows for a design of the drive-on mechanism that is geometrically very simple and therefore particularly robust.

[0014] According to one embodiment of the invention, the mechanical coupling is formed by a positive fit between the free end of the bending spring and the adjusting slide.

[0015] A positive locking mechanism has the advantage that the spring element can be easily mounted in the approach mechanism. A mechanical coupling to the control slide is then also easily possible and reversible; that is, the mechanical coupling can be released when the switch is raised and then re-established.

[0016] According to one embodiment of the invention, the free end of the bending spring engages in a recess in the adjusting slide.

[0017] In other words, the control slide is positioned so that the end of the bending spring protrudes into one direction of movement (usually linear) of the control slide. This means that the bending spring is carried along when the control slide moves, such as when the switch is opened. The deformation of the bending spring (and the torsion spring) then causes the end of the bending spring to move out of the recess, thus creating a mechanical decoupling between the spring element and the control slide. This protects the control device from mechanical damage.

[0018] According to one embodiment of the invention, it is provided that the free end of the bending spring has play in the recess.

[0019] A recess that allows for play between the control slide and the spring element facilitates movement between these two components, as long as a mechanical connection exists between them in the direction of movement of the control slide when the switch is being operated. Specifically, the bending spring can accommodate an angular change between its end and the control slide as it bends, without the two components jamming. This allows for better prediction of the spring element's behavior during operation and advantageously reduces wear during this process.

[0020] According to one embodiment of the invention, it is provided that at least one roller is attached to the end of the bending spring, which is designed to support itself on the bending spring when the switch is being driven up.

[0021] Attaching a roller advantageously reduces friction as the end of the bending spring moves out of the recess. Even as the bending spring continues to move relative to the control slide during further linear movement of the switch (i.e., during a further linear movement of the control slide), while the bending spring has already moved out of the recess, the roller, as it rolls along the control slide, reduces the friction between the end of the bending spring and the control slide. In this way, wear can be further and advantageously reduced.

[0022] According to one embodiment of the invention, the torsion spring is designed as a torsion bar.

[0023] Torsion springs designed as torsion bars advantageously possess structural features that make the spring insensitive to stress concentrations during deformation. This allows the spring to reliably perform its function even during extended use. For example, torsion springs have a torsion section with a reduced diameter, which transitions into a thickening at the ends of the torsion bar. This thickening serves to mechanically connect the ends of the torsion bar to adjacent components (in this case, a clamping element in the housing and a connection to the bending spring).

[0024] According to one embodiment of the invention, the torsion spring is provided to be held in a holder of the adjusting device with a fixed end in a rotationally rigid manner.

[0025] This advantageously results in the torsion spring exhibiting highly predictable spring behavior. The torsionally rigid mounting in the adjusting device creates mechanically predictable conditions in this regard. As already mentioned, such a mounting is not absolutely torsionally rigid, but compared to the spring stiffness of the torsion spring, it can be described as torsionally rigid from a technical perspective.

[0026] According to one embodiment of the invention, it is provided that the torsion spring is rigidly connected to a coupling end of the bending spring by means of a coupling end, forming a coupling point.

[0027] The torsionally rigid connection between the respective coupling ends of the bending spring and the torsion spring also creates unambiguous and easily calculable conditions. The division of tasks between the two springs—namely, that the bending spring primarily bends and the torsion spring primarily twists when a load is transferred to the spring during the actuating slide—is thus inherently predetermined by the design.

[0028] According to one embodiment of the invention, it is provided that the bending spring and the torsion spring form the legs of a right angle at the coupling point in the relaxed state.

[0029] This geometric design of the spring element advantageously ensures that the introduction of a torsional moment into the torsion spring by the bending spring at the coupling point can occur with a comparatively high degree of mechanical certainty. Naturally, the torsion spring is also subjected to a transverse force when the torsional moment is introduced, which will lead to a certain degree of bending. However, due to its geometry, the deformation of the torsion spring will primarily be characterized by torsion, which is why it technically exhibits the properties of a torsion spring.

[0030] According to one embodiment of the invention, it is provided that a further torsion spring is attached to the opposite side of the bending spring, which lies on the same torsion axis as the torsion spring.

[0031] In other words, the spring element created in this way has the shape of a large T, with the bending spring being the vertical beam of this T and the torsion spring being the transverse beam of the T. This arrangement has the advantage that the introduction of a bending moment occurs simultaneously at the ends of both torsion springs. Mechanically speaking, the two torsion springs therefore also form a bending beam, which is stressed in its middle and rigidly clamped at both ends. This structure is significantly stiffer with respect to the introduced bending moment than if only one torsion spring were connected at its end to the end of the bending spring at the coupling point. Therefore, limiting the stress on the torsion spring to torsion allows for even greater isolation from unwanted bending stress.

[0032] As mentioned, the two torsion springs are firmly clamped at their respective other ends. This creates a parallel connection of the torsion springs, meaning that their individual spring stiffnesses must be halved compared to the desired spring stiffness of the torsion spring assembly in order to obtain the desired resulting overall spring stiffness of the torsion spring combination.

[0033] According to one embodiment of the invention, the bending spring and the actuating slide form the legs of a right angle when the switch is not opened.

[0034] This advantageously creates well-defined kinematic relationships between the bending spring and the control slide when the switch is opened. The control slide, with its connection point facing its direction of movement, then engages at a right angle to the end of the bending spring, and can deform it in a defined manner. Simultaneously, the bending spring transmits a torsional moment to the torsion spring connected at the coupling point. The bending spring then oscillates in the lateral direction of the control slide's movement and simultaneously away from it, thus releasing the mechanical connection between the spring element and the control slide (at least in the axial direction of the control slide).

[0035] The aforementioned problem is alternatively solved according to the invention with the subject matter of the claim specified at the outset (adjusting device) by the fact that the spring element consists of a component or assembly comprising a torsion spring and a bending spring, wherein the torsion spring and the bending spring are mechanically and rotationally rigidly coupled to each other, such that a torque is transmitted between the torsion spring and the bending spring due to a force being introduced into the bending spring perpendicular to the axis of rotation of the torsion spring.

[0036] The actuating device achieves the advantages already explained in connection with the switch described in more detail above. The points raised regarding the switch according to the invention also apply accordingly to the actuating device according to the invention.

[0037] Further details of the invention are described below with reference to the drawing. Identical or corresponding drawing elements are each provided with the same reference numerals and are only explained more than once to the extent that differences arise between the individual figures.

[0038] The exemplary embodiments described below are preferred embodiments of the invention. In these embodiments, the described components each represent individual features of the invention that can be considered independently of one another. Each of these features further develops the invention independently and can therefore be considered part of the invention individually or in a combination other than that shown. Furthermore, the described components can also be combined with the features of the invention described above.

[0039] They show: Figure 1A schematic embodiment of the switch according to the invention, showing its interactions. Figure 2 a spring element schematically in a three-dimensional view, as it can be installed in an embodiment of the switch or the actuating device according to the invention, Figure 3 schematically a section showing a detent between the spring element with its bending spring and the actuating slide, whereby these two components are shown in various stages of opening as well as in the closed (installed) state, Figures 4 and 5 Exemplary embodiments of spring elements whose bending spring is provided with rollers at the free end to reduce friction in the indexing RT and during parallel displacement of the spring element and the adjusting slide, Figure 6a switch drive with an embodiment of the actuating device according to the invention in a first drive end position with the locking device according to the invention in a first position - equipped with a further embodiment of a spring element in the form of a T.

[0040] In Figure 1A turnout is shown in a schematic top view in a manner known per se. Rails SN are visible from the turnout, defining a first route FW1 and a second route FW2. The first route FW1 is the one that, when the turnout is set accordingly, leads away from the track in a curve, while the second route FW2 runs straight ahead. To set the turnout, a turnout drive 1 with a sliding lever 14 is provided, which can be moved laterally in the direction LR and is attached to an inner switch blade WZI and an outer switch blade WZA. In this way, the switch blades can be deformed, thereby setting the routes FW1 and FW2 (the target positions of the sliding lever are shown in Figure 1 This can be recognized by the fact that these are determined by the end positions of the switch blades, which are indicated by solid lines for the first route and by dashed lines for the second route. Figure 1The position for the first route FW1 is shown, with the position of the switch points for the second route FW2 indicated by dashed lines.

[0041] For additional guidance, wheel guides (RDL) and a frog (HZ) are provided at the turnout. These reduce the risk of a vehicle derailing at the turnout. This is particularly important when the turnout is approached by a vehicle from a first approach direction (AFR1) along the first route (FW1) or from a second approach direction (AFR2) on route FW2. A derailment occurs when a vehicle approaches from the second approach direction (AFR2) even though the turnout is set to the first route (FW1), or vice versa, when a vehicle approaches from the approach direction (AFR1) even though the turnout is set to route FW2. While routes FW1 and FW2 are traversable in both directions (double arrow), the approach directions (AFR1 and AFR2) only apply from the turnout end towards the frog, as a turnout cannot be approached from the turnout beginning (in this direction, route FW1 and FW2 is defined by the position of the switch blades (WZI and WZA), respectively).

[0042] In Figure 2 The spring element according to the invention is shown schematically. It consists of a torsion spring TF and a bending spring BF, which are connected to each other at a coupling point KPS. The coupling point consists, for example, of a splined shaft connection (not shown in detail), but could also consist of a press fit or a welded joint. In any case, the coupling end of the torsion spring KPT is connected at the coupling point KPS to the coupling end KPB of the bending spring BF in such a way that an application of a downward force F in the actuating slide, which is applied perpendicularly (angle δ) to the path of the bending spring BF, transmits a torque M to the torsion spring TF. For a length I of the bending spring BF, the torque is: M = F ⋅ I

[0043] The impact force F is applied at the free end of the bending spring FRB. Since the torsion spring FTT is clamped at one free end in a bracket HT of the switch drive 1 (not shown in detail), the torsion spring TF will twist and the bending spring BF will bend (the torsion spring TF will also bend to a certain extent, although this actual deformation is not shown in the model according to...). Figure 2 (is not taken into account).

[0044] Depicted in Figure 2 is a torsion angle α resulting from torsion of the torsion spring TF. Additionally, the bending spring BF bends along a deflection curve BL, which is determined taking into account the torsion angle α in Figure 1 is shown. Figure 2, that in the lateral direction LR, in which the impact force F also acts, a deflection of the free end of the bending spring FRB occurs by an amount x, which results from a superposition of the torsion of the torsion spring TF by an amount I ⋅ sin α and the displacement v of the bending spring at the free end FRB (which has an amount of v ⋅ sin α in the shift x).

[0045] The deformation of the spring also causes the free end of the bending spring FRB to deflect perpendicular to the lateral direction LR by the amount y, which moves it away from the control slide and thus allows for mechanical decoupling of these two components (more on this below). Simultaneously, the spring element FE stores energy through deformation so that after the switch is closed, when the switch drive is to be put back into operation, the spring element FE is re-engaged with the control slide by deformation to re-establish mechanical coupling.

[0046] In Figure 3 The schematic representation shows how a collision can occur. The mechanical coupling in Figure 3The recess VT is formed by a groove into which the bending spring BF projects with its free end FRB, creating a clearance SP. The clearance SP is necessary so that when the adjusting slide 14 is moved laterally in the direction LR, the free end FRB of the bending spring BF can tilt without the end FRB becoming jammed in the recess VT. This is in Figure 3 This is illustrated by showing the bending spring BF undeformed in state a and slightly deformed in state b during the ramp-up. In state b, the free end FRB of the bending spring BF rests against the edge of the recess VT and, due to the clearance SP, is slowly pushed out of the recess VT without tilting.

[0047] As the switch continues to move laterally in the direction LR, the bending spring, as shown in state c, completely detaches from the recess VT and rests against an upper surface OS of the control slide 14. Now the control slide 14 can slide under the bending spring BF and the switch can thus be opened without damaging other parts of the switch drive 1 via a mechanical coupling.

[0048] In the Figures 4 and 5 It is shown that the free end FRB of the bending spring BF can be provided with a roller RL in order to prevent both the bending spring BF from being dislodged from the recess VT in the event of a collision (state b according to Figure 3 ) as well as when the bending spring BF slides on the top side OS of the adjusting slide 14 (state c according to Figure 3 ) to prevent the friction that occurs. For better understanding, the free end FRB of the bending spring BF is shown in section, so that the rollers RL with their bearings LG can be seen.

[0049] Figure 4 and Figure 5 differ in that Figure 4 Two rollers RL are arranged on the edges of the bending spring that are perpendicular to the lateral direction, with one or the other of the rollers being used depending on the approach direction.

[0050] In Figure 5 A central roller is positioned, large enough to support movement in both directions. The recess VT is accordingly adapted to the roller RL.

[0051] The Figure 6Figure 1 shows the turnout drive 1 with an actuating device AMSM consisting of a drive module AM ​​and an actuating module SM in a first drive end position, from which it can be moved to a second drive end position. The turnout drive 1 according to the invention can be positioned to the right or left of a turnout on a track and is suitable for connection to movable turnout components that can be moved back and forth, namely both switch blades and a movable frog (however, the approach mechanism according to the invention only functions when mounted on switch blades). In the following, it is therefore assumed that the turnout drive 1 is connected to two switch blades of a turnout (see Figure 1). Figure 1 ).

[0052] A drive housing 2 of this switch drive 1 consists of a preferably metallic housing trough 3 and a walk-on, non-slip cover (not shown), both of which together house essential parts of the switch drive. A drive motor 4 of a drive module AM, for example a three-phase motor, moves a ball screw drive 8 via a gear stage 5 with a pinion, an intermediate gear, and a large gear, or a chain drive (both not shown in detail). This ball screw drive 8 consists of a spindle 7, a spindle nut guided on the spindle 7, and an adjustable actuating clutch 6 encompassing the spindle nut. The actuating clutch 6 acts on a drive mechanism 9 (also called a holding clutch device) of an actuating module SM. The drive mechanism 9 comprises a clutch housing 10 and an adjustable holding clutch 11, which accommodates the spring element according to the invention.

[0053] When the drive motor 4 starts, the longitudinally guided actuating force coupling 8, which encompasses the spindle nut and is guided in a rotationally secure manner, moves from the first end position shown, where it rests against a stop 12 of the coupling housing 10, over a free stroke in one actuating direction R1 on the spindle 7 until it reaches a stop 13 of the coupling housing 10 of the actuating module SM. This coupling housing 10 is structurally integrated with the adjustable holding coupling 11 of the drive-up mechanism 9.

[0054] The holding coupling 11 is engaged via the detent RT (see Figures 3 to 5) positively connected to an actuating slide 14 of the switch drive 1. Until the actuating force coupling 6 abuts the stop 13 of the coupling housing 10, the latter is moved from the first end position shown to the left in the direction of actuation R1 and, via the holding coupling 11, moves the actuating slide 14 from the first end position shown, in which the actuating slide is largely located in the drive housing 2, to a second end position, in which it is extended furthest out of the drive housing. Not shown here, the switch blades WZI, WZA, which are to be moved back and forth in the direction of actuation R1 and R2 respectively, are attached to the end of the actuating slide 14 via an external locking mechanism (compare Figure 1 ) connected.

[0055] During the return movement of the switch drive 1 into the Figure 6In the first drive position shown, the actuating clutch 6 initially traverses the free space (free travel) between the stops 13 and 12 of the clutch housing 10, thereby carrying the actuating slide 14 along the clutch housing 10 and the holding clutch 11 until it reaches stop 12. The respective end position reached by the actuating slide 14 and the respective position of the movable switch blades controlled by the actuating slide 14 are monitored in the switch drive 1 and reported to a control station. The details of how this monitoring is carried out will be explained later.

[0056] The holding coupling 11 is designed to protect the switch drive 1 from damage when the switch is rammed. The holding coupling 11 engages and releases the control slide 14 when the switch is rammed and high external forces are applied to the switch drive 1. The process of ramming a switch will be discussed in more detail later.

[0057] The actuating slide 14 is locked in its two end positions by force and form locking. This is achieved by a first locking slide 15 and a second locking slide 16 of a locking device designated SPV as a whole, wherein the first locking slide 15 can engage in a corresponding first recess of the actuating slide 14 (not shown here), and wherein the second locking slide 16 can engage in a corresponding second recess of the actuating slide 14 (also not shown here). This occurs under the influence of spring devices, each consisting of two coil springs (not shown).

[0058] In the Figure 6In the first drive end position of the switch drive 1 shown, the locking slide 15, under the influence of the coil springs of the spring assembly, has fallen into the first recess of the actuating slide 14 (not shown). At the same time, a first drive contact (not shown) changed its switching position and interrupted the power supply circuit for the drive motor 4. When the switch drive 1 is switched to the second drive end position, whereby the locking slide 15 is disengaged from the first recess of the actuating slide 14 and the first drive contact is switched again, the locking slide 16 falls into its associated second recess of the actuating slide 14 (also not shown) as soon as this recess is aligned with the longitudinal axis of the locking slide 16.In this process, a second drive contact, corresponding to the first drive contact and controlled by the locking slide 16, changes its position and in turn interrupts the power supply circuit for the drive motor 4. Since this clearly limits the travel of the actuating lever 14, an actuating movement can be performed to re-establish a positive connection between the approach mechanism and the actuating slide 14 after the switch has been raised (more on this below) and the holding coupling 11 has been released. This is achieved by ensuring that the holding coupling 11 is always re-closed when the approach mechanism 9 completes its entire travel, limited by the stops 12 and 13, and passes through the recess VT.

[0059] In addition to the actuating slide 14 for moving the switch blades back and forth, the switch drive 1 according to the invention also has a test slide arrangement 21 with two test slides. One of the two test slides is located in the Figure 1 visible and designated with reference number 22. It is – not shown here – hinged to the adjacent switch blade of the switch not shown (cf. Fig. 1The other of the two test slides is located below and is therefore not visible. It is – also not shown here – hinged to the remote switch blade of the turnout. The two test slides 22 serve to report the actual position of the switch blades controlled by the control slide 14 back to the turnout drive 1. In this way, a breakage of the control slide 14, the loss of the linkage of the control slide 14 to the switch blades, or a breakage of the switch blades themselves is to be detected. For this purpose, the test slides 22 are hinged to each of the switch blades of the external track system. They are moved back and forth in the drive housing 2 in a similar way to the control slide 14, but are not driven by the drive motor 4 like the control slide 14, but are driven by the switch blade being monitored.

[0060] The drive housing 2 has a prepared installation space for the test slide assembly 21 on both the left and right sides of the control slide 14. The installation of the test slide assembly 21 in one of the prepared installation spaces depends on the position of the switch drive 1 relative to the switch. The test slide assembly 21 is to be installed on the side of the control slide 14 that faces the points of the switch points.

[0061] In the Figure 6In the depicted drive end position, it is assumed that not only has the actuating slide 14 reached its first end position in a predetermined manner, but that the switch blades it moves have also reached their first predetermined end position. If this is the case, the one test slide 22, which is articulated to the adjacent switch blade, is in a first end position, as is the other test slide 22, which is articulated to the opposite switch blade. An analogous configuration results in the drive end position (other switch position) not shown in Figure 6.

[0062] If the switch is run over, the positions reported by the test slides 22 deviate from the target position corresponding to the current switch setting. This allows the switch to be detected. This can generate an error message, enabling maintenance and safety measures to be initiated to prevent accidents. After maintenance of the switch, which also includes closing the locking coupling 11 as described above, the switch can be released for operation again, provided that no damage has occurred.

[0063] When the switch controlled by the switch drive 1 is traversed (only possible when controlling switch blades, not possible when controlling a frog), considerable forces are introduced into the switch drive 1 from the switch side via the actuating slide 14 after a switch lock is released. As soon as the holding force of the holding coupling 11 is exceeded, the actuating slide 14 begins to move in one direction or the other under the influence of the external force, as shown in the present illustration. Figure 6 to the left. This disengages the spring element FE from the recess VT of the actuating slide.

[0064] In Figure 6 is an alternative design of the holding coupling compared to the one in Figure 2 The geometric shape of the spring element FE is shown. The spring element FE according to Figure 6 has a T-shaped form, whereby according to Figure 6so to speak, looking down at the T. The torsion spring TF and another torsion spring WTF form the crossbeam of the T, which is firmly clamped at the edge in the upper area of ​​the tubular coupling housing 10. In the middle, the bending spring BF is attached to the two coupling ends of the torsion spring TF and the other torsion spring WTF that point towards the center and, in the perspective shown, projects downwards, where the free end of the bending spring BF is in the direction of the Figures 3 to 5 as described, engages in a recess of the actuating slide 14. Reference symbol list

[0065] AM Drive module SM Actuating module AMSM Actuating device RT Detent WZI Inner switch blade WZA Outer switch blade RDL Wheel guide FE Spring element TFT Torsion spring WTF Further torsion spring BF Bending spring SN Rail LR Lateral direction FW1 ... FW2 Travel path AFR1 ... AFR2 Approach direction HZ Core piece SP Play RL Roller LG Bearing FRB Free end Bending spring FTT Fixed end Torsion spring KPT Coupling end torsion spring KPB Coupling end bending spring KPS Coupling point HT Bracket OS Top VT Recess F Impact force v Displacement of the bending spring due to F x Resultant displacement in the direction of F y Resultant displacement perpendicular to F α Torsion angle in the direction of F β Torsion angle (opposite direction) γ Right angle between torsion spring and bending spring δ Right angle between bending spring and adjusting slide BL Bending curve of the bending spring 1. Switch drive 2. Drive housing of the switch drive 1 3. Housing of the drive housing 2 4. Electric motor 5. Gear stage 6. Ball screw drive 7. Spindle 8. Actuating force coupling 9. Holding coupling device 10. Coupling housing of the holding coupling device 9 11. Holding coupling of the holding coupling device 9 12, 13. Stops of the coupling housing 10 for the actuating force coupling 8 14. Actuating slide 15, 16. Locking slide 17, 18. Spring assemblies with two coil springs each 19, 20. Guide pin 21. Test slide assembly with two test slides 22. Test slide of the test slide assembly

Claims

1. Points with a setting apparatus (AMSM), which is configured to use a drive to set the points via a setting slider (14), wherein the points have a driving-on mechanism with a mechanical coupling and a spring element (FE), wherein • the coupling is configured to decouple the drive from the setting slider (14) when the setting slider (14) leaves a target position during the driving-on, • the spring element (FE) is configured to couple the drive to the setting slider (14) when the setting slider (14) is located in the target position, characterised in that the spring element (FE) consists of a structural unit or an assembly, having a torsion spring (TF) and a bending spring (BF), wherein the torsion spring (TF) and the bending spring (BF) are coupled to one another in a mechanically torsionally rigid manner, in such a manner that a torque due to an introduction of force into the bending spring (BF) is transferred perpendicularly to the axis of rotation of the torsion spring between the torsion spring and the bending spring (BF).

2. Points according to claim 1, characterised in that the bending spring (BF) is coupled at a free end to the setting slider (14) in such a manner that a displacement of the setting slider (14) during the driving-on bends the bending spring (BF).

3. Points according to claim 2, characterised in that the mechanical coupling is formed by a positive fit between the free end of the bending spring (BF) and the setting slider (14).

4. Points according to claim 3, characterised in that the free end of the bending spring (BF) engages into a depression (VT) in the setting slider (14).

5. Points according to claim 4, characterised in that the free end of the bending spring (BF) has play (SP) in the depression (VT).

6. Points according to one of claims 3-5, characterised in that at least one roller (RL) is attached at the end of the bending spring (BF) and is configured to support the bending spring (BF) during the driving-on of the points.

7. Points according to one of the preceding claims, characterised in that the torsion spring (TF) is designed as a torsion bar.

8. Points according to one of the preceding claims, characterised in that the torsion spring (TF) is held at a fixed end in a torsionally rigid manner in a bracket (HT) of the setting apparatus (AMSM), in particular of the drive.

9. Points according to one of claims 7 or 8, characterised in that the torsion spring (TF) is connected at a coupling end in a torsionally rigid manner to a coupling end of the bending spring (BF) with the formation of a coupling point (KPS).

10. Points according to claim 9, characterised in that a further torsion spring (WTF), which lies on one and the same torsion axis with the torsion spring (TF), is connected to the opposite side of the bending spring (BF).

11. Points according to claim 9 or 10, characterised in that the bending spring (BF) and the torsion spring (TF), in the relaxed state, form the limbs of a right angle at the coupling point (KPS).

12. Points according to one of the preceding claims, characterised in that the bending spring (BF) and the setting slider (14), in the non-driven-on state of the points, form the limbs of a right angle.

13. Setting apparatus (AMSM) for a set of points, having a drive and a spring element (FE), wherein the setting apparatus (AMSM) is configured to be installed into a set of points according to one of the preceding claims, characterised in that the spring element (FE) consists of a structural unit or an assembly, having a torsion spring (TF) and a bending spring (BF), wherein the torsion spring (TF) and the bending spring (BF) are coupled to one another in a mechanically torsionally rigid manner, in such a manner that a torque due to an introduction of force into the bending spring (BF) is transferred perpendicularly to the axis of rotation of the torsion spring between the torsion spring and the bending spring (BF).