ACTUATOR CLUTCH

Description

[0001] The invention relates to a positioning coupling, in particular for an electromechanical switch drive in railway traffic, with a coupling hub which can be driven so as to rotate about an axial direction of the positioning coupling and in which a threaded spindle can be mounted, wherein the coupling hub is mechanically coupled to a rotatable coupling housing of the positioning coupling via an overload coupling, the coupling housing is rotatably mounted on the coupling hub by means of two coaxial axial deep groove ball bearings and a respective axial deep groove ball bearing is arranged in the positioning coupling in a mechanically clamped manner in the axial direction by means of a respective two-part pressure piece arrangement.

[0002] A generic actuating force clutch is known from the document DE 44 27 809 A1.

[0003] Furthermore, from the document WO 2022 / 089684 A1, an electrical machine is known in which a rotor is rotatably mounted relative to a stator by means of two axially spaced rolling bearings and at least one of the rolling bearings is axially preloaded by a spring element.

[0004] The invention also relates to an electromechanical actuating device for a switch drive and a switch drive for railway traffic.

[0005] Robust and reliable switches are a crucial factor in improving track utilization in rail traffic. This is especially true given the growing demands placed on modern railways, for example, in long-distance traffic, where high speeds are also encountered on a branch track of the switch. However, local and freight traffic also place high loads on switches. A switch drive therefore plays a key role in ensuring safety in rail traffic. It should operate precisely, be reliable, and highly resilient, as well as be economical and versatile for use in local and long-distance traffic for switches of all types and gauges, if possible.

[0006] An electromechanical switch (setting) drive must perform the following tasks safely and reliably: switching a switch, holding the switch blades in their end positions, mechanically securing the switch lock, electrically / electronically signaling a switching operation and the end position of the switch blades to a signal box, opening the collision coupling in the switch drive when a vehicle approaches the switch, and transmitting a collision signal to a monitoring device, etc.

[0007] Not only during the switching operation of the point machine itself, but also outside of it, high forces are introduced into the point machine when a vehicle passes over the point, especially when driving into the point. These forces can damage the switching coupling and, in the long term, lead to the failure of the switching coupling and thus of the point machine. - It is therefore an object of the invention to provide an improved switching coupling for a point machine and an improved switch machine.

[0008] The object of the invention is achieved by means of a positioning coupling, in particular for an electromechanical point drive in railway traffic, by means of an electromechanical actuating device for a point drive in railway traffic, and by means of a point drive for railway traffic, according to the independent claims. Advantageous developments, additional features, and / or advantages of the invention emerge from the dependent claims and / or the following description of the invention.

[0009] Investigations of long-term service life of switch machines for railway traffic have shown that, despite their already high average service life, a current problem with limiting the service life of switch machines is the forces introduced into a switch machine during its service life, particularly the axial forces introduced into a torque limiting clutch. These axial forces particularly damage the three-part axial deep groove ball bearings used in these machines, with their two axial bearing shells and a ball cage containing the rolling balls.

[0010] Following the functional principle of a force clutch, brief force-free moments also occur during a force limit of the force clutch (right / left stop of an overload clutch of the force clutch). This leads to a separation of the mechanical contact between the axial bearing shells and the ball cage in the three-piece loose axial deep groove ball bearings used.

[0011] This means that when the axial deep groove ball bearing is unloaded, its contact bond is temporarily broken and becomes "airy." The ball cage with its rolling balls falls out of a groove in a thrust bearing shell, and only when a counterload is applied does the ball cage suddenly fall back into the groove in question. The separation of the contact bond can damage the axial deep groove ball bearing and thus lead to less controllable function of the actuating force clutch.

[0012] As mentioned at the outset, the actuating force clutch according to the invention comprises a clutch hub which can be driven rotatably about an axial direction of the actuating force clutch and in which a threaded spindle can be mounted, wherein the clutch hub is mechanically coupled to a rotatable clutch housing of the actuating force clutch via an overload clutch, the clutch housing is rotatably mounted on the clutch hub by means of two coaxial axial deep groove ball bearings and a respective axial deep groove ball bearing is arranged in the actuating force clutch in a mechanically clamped manner in the axial direction by means of a respective two-part pressure piece arrangement.

[0013] This also applies conversely, of course: the clutch hub is rotatably mounted inside the clutch housing by means of two coaxial axial ball bearings. Instead of an axial ball bearing, an axial ball bearing can also be used. In this case, the mechanical clamping of the respective axial ball bearings by means of the two-part pressure piece arrangement exists particularly in a closed state (no actuating force limitation of the actuating force clutch, idle state and switching of the actuating force clutch) and preferably also in a released state (actuating force limitation of the actuating force clutch) of the actuating force clutch's overload clutch.

[0014] When the coupling hub is mounted on the threaded spindle, they form a rotationally fixed spindle-hub connection, meaning that the rotational movement of the coupling hub can be transmitted to the threaded spindle. This means that if the actuating force coupling is mounted, for example, on the threaded spindle of a switch machine, the threaded spindle, which is rotatably driven by the actuating force coupling, can convert its rotational movement into a linear actuating movement of the ball screw drive away from the actuating force coupling by means of a ball screw drive mounted on it. Alternatively, the ball screw drive can be installed between the coupling hub and the threaded spindle.

[0015] The three-part design of axial ball bearings poses a problem in that the two bearing shells and the ball cage, as a single assembly, form a loose axial contact assembly that is also not held together. With a permanently mechanically preloaded axial ball bearing, the disintegration of the axial ball bearing assembly can be avoided. This means that the occurrence of "air" is at least reduced in the axial ball bearing, since the axial bearing preload device ensures that the assembly connection is maintained even when the axial ball bearing is free of axial load. This prevents undefined bearing conditions, premature and indeterminate wear, an increase in the actuating force that develops over time, bearing damage, and increased post-delivery costs (NCC costs).

[0016] According to the invention, it is provided that a first pressure piece of the two-part pressure piece arrangement is designed as a pressure pot and a second pressure piece of the two-part pressure piece arrangement is designed as a pressure cover, wherein the pressure pot has in a radial outer section a centering surface designed as an inner-walled centering funnel or centering cone for a centering surface of the pressure cover, and the pressure cover has on a radial outer edge the centering surface for the centering surface of the pressure pot, which is designed as a centering outer edge with a centering cone.

[0017] The respective axial deep groove ball bearing can be designed as a three-part loose assembly or as a one-piece assembly. Furthermore, the axial bearing shells of the respective axial deep groove ball bearing can be arranged in a horizontal axial direction. Furthermore, the respective axial deep groove ball bearing itself can be designed as a low-clearance or a mechanically preloaded axial deep groove ball bearing.

[0018] The actuating force clutch can be designed such that the overload clutch remains essentially closed during actuating operation of the actuating force clutch. During actuating operation of the actuating force clutch, the clutch hub rotates the threaded spindle and provides it with an actuating force. The actuating force originates from the rotatable clutch housing, which is essentially non-rotatably connected to the clutch hub via the closed overload clutch.

[0019] The actuating force coupling can further be designed in such a way that when an actuating force of the threaded spindle is limited by the actuating force coupling, the overload clutch is released. When the actuating force is limited, e.g. because the threaded spindle can no longer be rotated (e.g. actuating device (see below) in the end position (first or second stop), possibly also the end position(s) of the switch tongues or the end position of the frog), the released overload clutch limits an actuating force impressed on the threaded spindle by the coupling hub.

[0020] Furthermore, the actuating force clutch can be designed such that when the actuating force is limited, the axially preloaded plates of the overload clutch slide past each other. This means that the plates of the overload clutch are preferably not disengageable when the actuating force is limited, but retain their mutual preload force. When the actuating force is limited, the circumferential force between the plates becomes greater than the mutual adhesive force due to their mechanical preload force.

[0021] The clutch hub can be arranged radially within the overload clutch. In this case, the clutch hub can be axially supported by a corresponding thrust piece arrangement with a respective axial deep groove ball bearing in the overload clutch. Furthermore, the two thrust piece arrangements can act on a disk pack of the overload clutch in an axially preloaded manner. This means that the overload clutch is designed as a multi-disk overload clutch.

[0022] Furthermore, the plate pack of the overload clutch can be arranged axially between the axial deep groove ball bearings. Preferably, the clutch hub carries the at least one inner plate radially outward, and the clutch housing holds the at least one outer plate of the overload clutch radially inward. Naturally, the respective inner plate and the respective outer plate are provided in a rotationally fixed manner on the clutch hub and in the clutch housing, respectively, and are mounted there for axial displacement.

[0023] The clutch hub can be axially supported by a respective axial deep groove ball bearing. A clutch-side axial bearing shell of the respective axial deep groove ball bearing can be axially seated directly or indirectly on the clutch hub. Furthermore, an inner shoulder of the thrust piece arrangement can be arranged between the clutch hub and the respective axial deep groove ball bearing. This means that this embodiment teaches indirect support of the clutch hub relative to the respective axial deep groove ball bearing. One or the clutch-side axial bearing shell of the respective axial deep groove ball bearing can be radially seated directly on the clutch hub. Furthermore, the thrust piece arrangement can be axially seated directly or indirectly on a plate pack of the overload clutch.

[0024] The two thrust pads can axially accommodate the respective axial deep groove ball bearing between them. Furthermore, the mechanical clamping in the axial direction can be exerted directly by the two thrust pads on the respective axial deep groove ball bearing.

[0025] Furthermore, the respective thrust piece assembly and the respective axial deep groove ball bearing can be designed as a preferably three-part or five-part ring assembly. These five parts, for example, with at least one part optionally being designed as an assembly, are the two thrust pieces, the two axial bearing shells, and the ball cage (including the rolling balls). With three parts, the axial deep groove ball bearing, for example, can be designed as a single, cohesive assembly.

[0026] When the overload clutch in the actuating force clutch is closed, a preload device can exert a mechanical preload force axially on the second thrust piece. The preload device is located axially away from the second thrust piece, preferably on an adjusting element of the actuating force clutch. Furthermore, the second thrust piece can exert a mechanical preload force axially on the respective axial deep groove ball bearing. Furthermore, the respective axial deep groove ball bearing can exert a mechanical preload force axially on the first thrust piece. Furthermore, the first thrust piece can exert a mechanical preload force axially on one or more of the disk packs.

[0027] In this case, two such arrangements (relevant pretensioning device, relevant second pressure piece, respective axial deep groove ball bearing, relevant first pressure piece) can be arranged in a mirrored manner in the actuating force clutch, wherein the two second pressure pieces apply a clamping force in the axial direction to the plate pack at least when the overload clutch is closed, ie by forces directed towards one another in the axial direction.

[0028] The pressure pot and the pressure cover can each have a bearing mount for the respective axial deep groove ball bearing. A single bearing mount can have a radial collar and an axial shoulder of the thrust piece.

[0029] The pressure cover may have an axial shoulder for centering the preloading device on the pressure cover.

[0030] The axial shoulder for the preload device and the axial shoulder for the axial bearing shell extend in opposite directions.

[0031] The thrust piece arrangement can be axially displaceable, the first thrust piece can be circumferentially displaceable or fixed, and / or the second thrust piece can be circumferentially displaceable in the clutch housing. - The two thrust piece assemblies can be axially preloaded against each other axially on the outside by a / the preloading device in the actuating force clutch. In this case, the preloading device in question is in particular a disc spring or a disc spring arrangement comprising at least two disc springs.

[0032] A mechanical preload of the respective preload device can be adjusted and maintained by an adjusting element arranged axially on the outside of the preload device. A mechanical preload of at least the respective preload device can be adjusted by means of an adjusting element. The respective adjusting element can be arranged inside the clutch housing, wherein the adjusting element is preferably arranged in the clutch housing so as to be axially adjustable by means of an adjusting screw connection.

[0033] The invention is explained in more detail below using exemplary embodiments with reference to the attached schematic and not-to-scale drawing. Sections, elements, parts, units, components and / or schemes which have an identical, unique or analogous design and / or function are identified by the same reference numerals in the description of the figures (see below), the list of reference numerals, the patent claims and in the figures (Fig.) of the drawing. A possible alternative not explained in the description of the invention (see above), not shown in the drawing and / or not exhaustive, a static and / or kinematic reversal, a combination, etc. to the exemplary embodiments of the invention or of a component, scheme, unit, part, element or section thereof, can also be found in the list of reference numerals and / or the description of the figures.

[0034] In the invention, a feature (section, element, part, unit, component, function, size, etc.) can be configured positively, i.e., present, or negatively, i.e., absent. In this specification (description (description of the invention (see above), description of the figures (see below)), list of reference symbols, patent claims, drawing), a negative feature is not explicitly explained as a feature unless it is important for the invention to be absent. This means that the invention actually made, and not one constructed by the prior art, consists in omitting this feature.

[0035] A feature of this specification may be applied not only in a specified manner and / or form, but also in another manner and / or form (isolation, combination, replacement, addition, uniqueness, omission, etc.). In particular, it is possible to replace, add, or omit a feature in the patent claims and / or description based on a reference symbol and a feature associated with it, or vice versa, in the description, the list of reference symbols, the patent claims, and / or the drawing. Furthermore, this may allow a feature in a patent claim to be interpreted and / or further specified.

[0036] The features of the description can also be interpreted as optional features (in view of the (initially usually unknown) prior art); i.e., each feature can be understood as an optional, arbitrary, or preferred, i.e., non-binding, feature. This makes it possible to isolate a feature, possibly including its periphery, from an embodiment, whereby this feature can then be transferred to a generalized inventive concept. The absence of a feature (negative feature) in an embodiment shows that the feature is optional with regard to the invention. Furthermore, a species term for a feature can also be interpreted as a generic term for the feature (possibly a further hierarchical division into subgenres, etc.), whereby a generalization of the feature is possible, e.g., taking into account equal effect and / or equivalence.

[0037] The figures (Fig.) are purely exemplary and show: the Fig. 1 a plan view of a conventional railway switch, the switch tongues of which can be actuated by a slide valve of a switch drive to set their travel paths, the Fig. 2 a plan view of a point machine open at the top, with the mechanical, electrical and electromechanical interior of the point machine only shown schematically, the Fig. 3 a central and axial-radial sectioned perspective view through a power clutch for a switch drive in railway traffic, e.g. the switch drive from the Fig. 2 , with a two-part pressing piece according to the invention, and the Fig. 4 the two parts of the two-part pressing piece according to the invention from the Fig. 3 in central and axial-radial sectioned side views (Fig. 5) in a disassembled state of the pressure piece.

[0038] Although the invention is described and illustrated in more detail above and below by means of preferred embodiments, the invention is not limited to the disclosed embodiments, but is of a more fundamental nature. Other variations may be derived from this and / or from the above (description of the invention) without departing from the scope of the invention.

[0039] The invention is explained below with reference to embodiments of a specific embodiment ( Fig. 3 ) of a variant of a servo coupling 100 for a switch drive 1 is explained in more detail. The drawing only shows those spatial sections of an object of the invention that are necessary for understanding the invention. The explanation of the invention with reference to the drawing refers below to an axial direction Ax, a radial direction Ra, and a circumferential direction Um of the servo coupling 100.

[0040] The Fig. 1 shows a switch 8 whose rails define a first track 81 and a second track 82. The first track 81 is the one which, when the switch 8 is in the corresponding position, leads away from a curved track, while the second track 82 runs straight ahead. To set the switch 8, a switch drive 1 is provided with a control slide 2 which can be moved back and forth in a lateral direction (double arrow on the switch drive 1) and is attached to an inner switch blade and an outer switch blade of the switch 8. In this way, the switch blades can be actuated, whereby the tracks 81, 82 for a railway vehicle can be set. The target positions of the control slide 2 are predetermined by the end positions of the switch blades.

[0041] For additional guidance, check rails 83 and a frog 84 are installed in the switch 8. These reduce the risk of a vehicle derailing on the switch 8. This applies in particular if the switch 8 is driven onto by a vehicle. A collision occurs when a vehicle approaches from one direction of travel although the switch 8 is set for the other direction of travel. - During operation of the switch machine 1, shocks occur, for example due to adjusting movements, vehicles driving over it and the approaching of the switch 8, which are introduced into the switch machine 1 in particular via the adjusting slide 2. In particular, an adjusting module 10 (cf. Fig. 2 ) for the adjusting slide 2 must absorb these shocks, whereby the required for a spindle-hub connection 130 (cf. Fig. 3 ) a servo clutch 42 (cf. Fig. 2 ), 100 (cf. Fig. 3 ) a control device 40 of the control slide 2 is loaded.

[0042] The Fig. 2 shows an exemplary point machine 1 with an adjusting device 4 consisting of the actuating module 10 and a drive module 20 in a first end position (stop 65, see below), from which the point machine 1 can be transferred to a second end position (stop 66). The point machine 1 can be positioned to the right or left of a point 8 on a track and is suitable for mechanical connection to reciprocating switch parts, such as switch tongues or an actuatable frog 84. In the following, it is assumed that the point machine 1 with its adjusting slide 2 is mechanically connected to two switch tongues of a point 8 (see Fig. 1 ).

[0043] A drive motor 22 of the drive module 20, designed for example as a three-phase motor 22, rotates via a gear stage 30, e.g. with a pinion, an intermediate gear and a large gear, or a chain drive (both in Fig. 2 not shown), a positioning clutch 42. A spindle-hub connection (not shown) of the positioning clutch 42 is formed with a threaded spindle 52 and has a coupling hub of the positioning clutch 42 that is non-rotatably seated on the threaded spindle 52. The positioning clutch 42 acts on a drive-on mechanism 62, also referred to as a holding clutch device 62, of the positioning module 10. The drive-on mechanism 62 comprises a clutch housing 63 and an adjustable holding clutch 64.

[0044] When the drive motor 22 starts up, the coupling hub rotates and moves an adjusting device 44 of the adjusting device 40, which is guided longitudinally on the threaded spindle 52 in a rotationally secure manner, from the illustrated first end position, in which the adjusting device 44 rests against a (first) stop 65 of the adjusting module 10, over an adjusting path in an adjusting direction on the threaded spindle 52 until it rests against a (second) stop 66 of the adjusting module 10 (i.e. to the left in the Fig. 2 ). For this purpose, a ball screw drive is arranged between the adjusting device 40 and the threaded spindle 52, which converts or translates the rotational movement of the threaded spindle 52 into a linear actuating movement of the adjusting device 40. The coupling housing 63 is structurally combined with the adjustable retaining coupling 64 of the drive-on mechanism 62.

[0045] Until the adjusting device 44 strikes the second stop 66, the coupling housing 63 is driven from the illustrated first end position to the left in the setting direction and, via the retaining coupling 64, moves the control slide 2 from the illustrated first end position, in which the control slide 2 is largely located in a drive housing 12 of the point machine 1, into a second end position, in which the control slide 2 is extended furthest out of the drive housing 12. Not illustrated here is an external lock of the control slide 2, with which the control slide 2 can be mechanically connected to the switch blades that can be moved back and forth in the setting directions.

[0046] When the switch drive 1 or the control slide 2 returns from the second drive position (adjusting device 44 is located at the second stop 66) to the position shown in the Fig. 2 In the first drive position shown (adjustment device 44 is positioned at the first stop 65), the actuating force coupling 42 travels the actuating path between the stops 66, 65 of the actuating module 10 in the reverse direction. The adjusting device 44 thereby carries the actuating slide 2 via the coupling housing 63 and the retaining coupling 64 up to the first stop 65.

[0047] The holding coupling 64 is designed to protect the point machine 1 from damage, particularly when the point 8 is driven up. The holding coupling 64 then responds and releases the control slide 2 when the point 8 is driven up and high forces are transferred from the outside into the point machine 1. However, the holding coupling 64 cannot prevent the bearing (in Fig. 2 not shown) of the actuating clutch 42 shocks are transmitted.

[0048] The control slide 2 can be fixed in its two end positions in the switch machine 1, preferably in a force-locking and form-locking manner. A first locking slide 72 and a second locking slide 74 of a locking device 70 are used for this purpose, wherein the first locking slide 72 can engage a corresponding first recess (not shown) in the control slide 2 for the first end position, and the second locking slide 74 can engage a corresponding second recess in the control slide 2 for the second end position (not shown). This is achieved, for example, by means of spring devices. - Upon reaching an end position, shocks can occur, which are introduced by the control slide 2 into the bearing of the actuating force coupling 42 and place mechanical stress on it.

[0049] When the switch 8 controlled by the switch drive 1 is driven (only possible when controlling switch tongues, not possible when controlling a frog), after the release of a switch lock from the switch side, considerable forces are introduced into the switch drive 1 via the control slide 2. As soon as the holding force of the holding coupling 64 is exceeded, the control slide 2 starts to move in one direction or the other under the influence of the force acting on it from the outside, in the present illustration the Fig. 2 to the left. A spring element of the retaining clutch 64 is mechanically decoupled from the adjusting slide 2.

[0050] The Fig. 3 shows a power coupling 100 for a switch drive 1, for example the one shown in the Fig. 2 illustrated or another. The actuating force clutch 100 has a one-piece, single-piece, or integral clutch housing 110 with, for example, a drive wheel 112 mounted thereon, which is closed at two opposite end faces by an adjusting member 127 each, which in the present embodiment are preferably designed as adjusting nuts 127. The adjusting members 127 have a through-opening through which a threaded spindle 134 can be passed ( Fig. 3 left) or extendable in or through ( Fig. 3 right).

[0051] The threaded spindle 134 can be enclosed in the region of the clutch housing 110 by a clutch hub 132 as a drive of the threaded spindle 134, wherein each adjusting member 127 is supported on an outer circumferential surface of the threaded spindle 134 by a bearing, in this case designed as a plain bearing, or vice versa. A different bearing is of course usable. In this way, the threaded spindle 134 can not only be rotated in the clutch housing 110, but also displaced in the axial direction Ax. The threaded spindle 134 and the clutch hub 132 form a rotationally fixed spindle-hub connection 130, e.g., by means of a key, a splined shaft connection, etc. Furthermore, the threaded spindle 134 and the clutch hub 132 can be axially fixed to one another, which can be achieved, for example, by means of a shoulder on the threaded spindle 134 and a shaft nut.- Instead of the threaded spindle 134, the coupling hub 132 can be mounted in the coupling housing 110 in a similar way to the threaded spindle 134 (not shown).

[0052] An overload clutch 120 is formed between the clutch hub 132 and an inner side of the clutch housing 110. In the present embodiment, the overload clutch 120 is a multi-plate clutch with outer plates 113 of the clutch housing 110 and inner plates 133 of the clutch hub 132. The outer plates 113 and the inner plates 133 are designed as friction plates 113, 133 (plate pack 113, 133), with the outer plates 113 being axially displaceable and rotationally fixed inside the clutch housing 110, and the inner plates 133 being axially displaceable and rotationally fixed outside on the clutch hub 131.

[0053] The disk pack 113, 133 of the overload clutch 120 is delimited by two thrust piece assemblies 150 / 160 of the overload clutch 120, wherein a single thrust piece assembly 150 / 160 comprises two thrust pieces 150, 160. Between each adjusting member 127 and a respective thrust piece assembly 150 / 160, a preloading device 125 is arranged, which exerts preload forces on the respective thrust piece assembly 150 / 160 depending on each adjusting member 127. In the present embodiment, the preloading device 125 is preferably a spring device 125, in particular a disc spring assembly 125. Other springs or spring devices are, of course, applicable.

[0054] By rotating one or both adjusting elements 127, a preload force and thus also a release force of the overload clutch 120 can be adjusted. In a preferred embodiment, both adjusting elements 127 are rotated by the same amount, so that equal preload forces occur. Directional dependencies can be compensated for by an unequal adjustment. - Furthermore, the clutch hub 132 is axially supported indirectly, if necessary also directly, via two axial deep groove ball bearings 140, with the actual overload clutch 120 being arranged between the axial deep groove ball bearings 140 in the actuating force clutch 100. The axial deep groove ball bearing 140 is preferably designed as a three-part loose axial deep groove ball bearing 140.

[0055] A single two-part pressure piece arrangement 150 / 160, see also the Fig. 4 , comprises two pressure pieces 150, 160, wherein a first pressure piece 150 is preferably designed as a (pot-shaped) pressure pot 150 (cf. the Fig. 4 right) and a second thrust piece 160 are preferably designed as a (cover-shaped) thrust cover 160. A respective axial deep groove ball bearing 140 is arranged axially Ax between the two thrust pieces 150, 160 in a single thrust piece arrangement 150 / 160. Furthermore, the respective axial deep groove ball bearing 140 is preferably arranged radially Ra inside the thrust piece arrangement 150 / 160.

[0056] To accommodate the respective axial deep groove ball bearing 140 in the respective two-part thrust piece arrangement 150 / 160, the respective thrust piece 150, 160 has a bearing receptacle 152, 162. The respective bearing receptacle 152, 162 comprises a circumferential axial shoulder 154, 164 for this purpose. Furthermore, the respective bearing receptacle 152, 162 has a radial collar 153, 163 for this purpose. the respective axial deep groove ball bearing 140 is held by the two radial collars 153, 163 axially Ax and by the axial shoulders 154, 164 radially Ra in the thrust piece arrangement 150 / 160, wherein an anti-parallel, mechanical preload force of the thrust piece arrangement 150 / 160 on both sides of the axial deep groove ball bearing 140 originates from the preload device 125 and a counter bearing (disk pack 113, 133).

[0057] The respective axial deep groove ball bearing 140 is equipped with an axial bearing shell 146, in particular a clutch-side axial bearing shell 146, in the bearing receptacle 152 of the pressure vessel 150, and with an axial bearing shell 148, in particular a clutch-side axial bearing shell 148, in the bearing receptacle 162 of the pressure cover 160. Between the axial bearing shells 146, 148 is a ball cage 147 with the rolling balls of the axial deep groove ball bearing 140. The respective installed axial deep groove ball bearing 140 is preferably not axially preloaded. An axial Ax preload is produced by the two-part pressure piece arrangement 150 / 160, whose pressure pieces 150, 160 are axially Ax mechanically preloaded against each other (preloading device 125) in the actuating force coupling 100.

[0058] During a changeover process of a switch drive 1 (see the Fig. 2) the threaded spindle 134 rotates to move the adjusting slide 2 translationally. In doing so, the actuating force coupling 100 rotates. At the end of the changeover process, a corresponding end position should be reached both during extension and retraction. During the changeover process and in the "reaching an end position" phase, the overload clutch 120 in the actuating force coupling 100 becomes active and interrupts the flow of force (limiting the actuating force). This means that the overload clutch 120 is triggered, and the rotational movement of the drive motor 22 to the coupling hub 132 is interrupted.

[0059] This, and shocks introduced linearly into the actuating force coupling 100 via the adjusting slide 2 (see above), can cause damage to the actuating force coupling 100. According to the invention, the problem arises when, due to design reasons, there is no axial preload on both sides of the axial deep groove ball bearings, which are otherwise not subjected to axial Ax load (i.e., apart from the limit of the actuating force) (see also the description of the invention above), both during switching and when an end position is reached (release of the coupling). This creates an undefined state. The bearing elements (axial bearing shells, ball cage) can lift off and move apart from one another. This can cause bearing damage, which can lead to functional failure of the switch drive 1.

[0060] To counteract this, a one-piece pressure piece is designed as a two-piece pressure piece arrangement 150 / 160, whose pressure pieces 150, 160 are mechanically preloaded against one another (preloading device 125 and counterbearing). See also the description of the invention above. - As a result, an axial force flow of a non-triggered actuating force clutch 100 is maintained via the respective axial deep groove ball bearing 140, compared to an actuating force clutch without a two-piece pressure piece arrangement 150 / 160. By setting up the two-piece pressure piece arrangement 150 / 160, an additional force flow is established in the actuating force clutch 100. This force flow goes from the second pressure piece 160 (pressure cover 160) via the axial deep groove ball bearing 140 to the first pressure piece 150 (pressure pot 150) and vice versa.

[0061] The force flow of a released actuating clutch 100 for a loaded side of the actuating clutch 100 is analogous to that of an actuating clutch 100 with one-piece thrust pieces. The respective axial deep groove ball bearing 140 is located in the force flow between the threaded spindle 134 and the preloading device 125 (although there is a problem of the bearing elements being suddenly pressed against one another, see below). - The force flow of a released actuating clutch 100 for a relieved side of the actuating clutch 100 is from the preloading device 125 (via the second thrust piece 160) via the axial deep groove ball bearing 140 (via the first thrust piece 150) to the clutch housing 110 and / or the clutch hub 132, or vice versa.

[0062] If the respective two-part thrust piece arrangement 150 / 160 is missing, the axial deep groove ball bearings 140 of the non-released overload clutch 120 are not in a force flow, and there is no axial preload of the axial deep groove ball bearings 140. - When the overload clutch 120 is released, an axial preload of the respective axial deep groove ball bearing 140 is suddenly applied for a loaded side of the actuating force clutch 100. The bearing elements (axial bearing shells 146, 148, ball cage 147) are suddenly pressed against one another, which can lead to damage in and to the respective axial deep groove ball bearing 140.

[0063] By means of the two-part thrust piece arrangement 150 / 160, a constant axial preload is applied to the respective axial deep groove ball bearing 140, even when the respective axial deep groove ball bearing 140 is unloaded by the release of the overload clutch 120. The sudden pressing of the axial bearing shells 146, 148 and the ball cage 147 onto one another is effectively prevented. List of reference symbols

[0064] 1Switch drive 2 Adjusting slide 4 Adjusting device 10 Adjusting module 20 Drive module 22 Drive motor 30 Gear stage 40 Adjusting device 42 Adjusting force coupling 44 Adjusting device 52 Threaded spindle 62 Drive-on mechanism 63 Coupling housing 64 Holding coupling 65 (first) stop 66 (second) stop 70 Locking device 72 (first) locking slide 74 (second) locking slide 100 Actuating clutch 110 Clutch housing 112 Drive gear 113 (Outer) plate 120 Overload clutch 124 Inner shoulder of the thrust piece assembly 150 / 160 125 Pretensioning device 127 Adjusting element 130 Spindle-hub connection 131 Outer shoulder of the clutch hub 132 132 Clutch hub 133 (Inner) plate 134 Threaded spindle 140Thrust ball bearing, preferably loose in three parts 146(coupling-side) thrust bearing shell 147Ball cage (with rolling balls) 148(non-coupling-side) thrust bearing shell 150 (first) thrust piece of the two-part thrust piece arrangement 150 / 160, pressure pot 151 Centering surface, in particular centering funnel or centering cone 152 Bearing seat 153 Radial collar 154 Axial shoulder 160 (second) thrust piece of the two-part thrust piece arrangement 150 / 160, pressure cover 161 Centering surface, in particular centering outer edge with centering cone 162 Bearing seat 163 Radial collar 164 Axial shoulder for axial bearing shell 148 165 Axial shoulder for preload device 125 AxAxial direction of the actuating force coupling 100, the axial deep groove ball bearing 140, the thrust piece arrangement 150 / 160 etc. RaRadial direction of the actuating force coupling 100, the axial deep groove ball bearing 140, the thrust piece arrangement 150 / 160 etc. UmCircumferential direction of the actuating force coupling 100, the axial deep groove ball bearing 140, the thrust piece arrangement 150 / 160 etc. 8(Railway) switch 81First track 82Second track 83Wheel check 84Crosspiece

Claims

1. Actuating force coupling (100), in particular for an electromechanical point machine (1) in railway traffic, having a coupling hub (132) which can be driven in a rotatable manner about an axial direction (Ax) of the actuating force coupling (100), in which coupling hub a threaded spindle (134) can be mounted, wherein • the coupling hub (132) is mechanically coupled by way of an overload coupling (120) to a rotatable coupling housing (110) of the actuating force coupling (100), • the coupling housing (110) is mounted in a rotatable manner on the coupling hub (132) by means of two coaxial axial groove ball bearings (140, 140) and • by means of an associated two-part pressure piece arrangement (150 / 160) a respective axial groove ball bearing (140) is set up in the axial direction (Ax) such that it is mechanically clamped together in the actuating force coupling (100), characterised in that a first pressure piece (150) of the two-part pressure piece arrangement (150 / 160) is embodied as a pressure vessel (150) and a second pressure piece (160) of the two-part pressure piece arrangement (150 / 160) is embodied as a pressure cover (160), wherein • the pressure vessel (150) has a centring surface (151) embodied as an inner-wall centring funnel or centring cone for a centring surface (161) of the pressure cover (160), and • the pressure cover (160), on a radial (Ra) outer edge, has the centring surface (161) for the centring surface (151) of the pressure vessel (160), embodied as a centring outer edge with a centring cone.

2. Actuating force coupling (100) according to the preceding claim, characterised in that: • the respective axial groove ball bearing (140) is embodied as a three-part loose or a single-part module (140), • the axial bearing shells (146, 148) of the respective axial groove ball bearing (140) are arranged in the horizontal axial direction (Ax), and / or • the respective axial groove ball bearing (140) is itself embodied as a low-backlash or mechanically pretensioned axial groove ball bearing.

3. Actuating force coupling (100) according to one of the preceding claims, characterised in that the actuating force coupling (100) is embodied such that: • the overload coupling (120) remains substantially closed in an actuating operation of the actuating force coupling (100), • if an actuating force of the threaded spindle (134) is limited by the actuating force coupling (100), the overload coupling (120) is released, and / or • if the actuating force is limited, the plates (113, 133) of the overload coupling (120) which are pretensioned axially (Ax) against one another slide past one another.

4. Actuating force coupling (100) according to one of the preceding claims, characterised in that the coupling hub (132) is set up radially (Ra) within the overload coupling (120), wherein: • the coupling hub (132) is supported axially (Ax) by way of an associated pressure piece arrangement (150 / 160) with a respective axial groove ball bearing (140) in the overload coupling (120), • the two pressure piece arrangements (150 / 160) act in an axially (Ax) pretensioned manner on a plate stack (113, 133; ...) of the overload coupling (120), and / or • the plate stack (113, 133; ...) of the overload coupling (120) is set up axially (Ax) between the axial groove ball bearings (140).

5. Actuating force coupling (100) according to one of the preceding claims, characterised in that the coupling hub (132) is supported axially by way of a respective axial groove ball bearing (140), wherein • a coupling-side axial bearing shell (146) of the respective axial groove ball bearing (140) rests axially directly or indirectly on the coupling hub (132), • an inner shoulder (124) of the pressure piece arrangement (150 / 160) is set up between the coupling hub (132) and the respective axial groove ball bearing (140), • a / the coupling-side axial bearing shell (146) of the respective axial groove ball bearing (140) rests radially directly on the coupling hub (132), and / or • the pressure piece arrangement (150 / 160) rests axially directly or indirectly on a plate stack (113, 133) of the overload coupling (120).

6. Actuating force coupling (100) according to one of the preceding claims, characterised in that: • the two pressure pieces (150, 160) receive the respective axial groove ball bearing (140) axially (Ax) between one another, • the mechanical clamping together in the axial direction (Ax) is effected directly by the two pressure pieces (150, 160) onto the respective axial groove ball bearing (140), and / or • the associated pressure piece arrangement (150 / 160) and the respective axial groove ball bearing (140) is embodied as a preferably three-part or five-part ring arrangement (140 / 150 / 160).

7. Actuating force coupling (100) according to one of the preceding claims, characterised in that, when the overload coupling (120) is closed, in the actuating force coupling (100): • a pretensioning facility (125) exerts a mechanical pretensioning force axially (Ax) onto the second pressure piece (160), • the second pressure piece (160) exerts a mechanical pretensioning force axially (Ax) onto the respective axial groove ball bearing (140), • the respective axial groove ball bearing (140) exerts a mechanical pretensioning force axially (Ax) onto the first pressure piece (150), and / or • the first pressure piece (150) exerts a mechanical pretensioning force axially (Ax) onto a / the plate stack (113, 133).

8. Actuating force coupling (100) according to one of the preceding claims, characterised in that: • the pressure vessel (150) and the pressure cover (160) in each case have a bearing receptacle (152, 162) for the respective axial groove ball bearing (140), • an individual bearing receptacle (152, 162) has a radial collar (153, 163) and an axial shoulder (145, 164) of the pressure piece (150, 160), and / or • the pressure cover (160) has an axial shoulder (165) for centring the pretensioning facility (125) on the pressure cover (160).

9. Actuating force coupling (100) according to one of the preceding claims, characterised in that: • the pressure piece arrangement (150 / 160) is set up in a displaceable manner in the axial direction (Ax), • the first pressure piece (150) is set up in a displaceable or fixed manner in the circumferential direction (Ax), and / or • the second pressure piece (160) is set up in a displaceable manner in the circumferential direction (Ax) in the coupling housing (110).

10. Actuating force coupling (100) according to one of the preceding claims, characterised in that: • the two pressure piece arrangements (150 / 160) are set up axially (Ax) externally pretensioned axially (Ax) against one another in each case by a / the pretensioning facility (125) in the actuating force coupling (100), • a mechanical pretensioning of the respective pretensioning facility (125) can be adjusted and is maintained by an adjustment element (127, 127) set up in each case axially (Ax) externally on the pretensioning facility (125, 125), and / or • the respective adjustment element (127) is set up internally in the coupling housing (110), wherein the adjustment element (127) is preferably set up to be adjustable in the axial direction (Ax) in the coupling housing (110) by means of an adjustment screw joint.

11. Electromechanical actuating facility (4) for a point machine (1) in railway traffic, characterised in that the actuating facility (4) comprises a drive motor (22) and an actuating force coupling (100), wherein the actuating force coupling (100) is embodied according to one of the preceding claims.

12. Point machine (1) for railway traffic, characterised in that the point machine (1) comprises an actuating facility (4) and / or an actuating force coupling (100), wherein the actuating facility (4) is embodied according to claim 11 and / or the actuating force coupling (100) is embodied according to one of the preceding claims 1 to 10.