Patent Description:
<CIT> is considered by the issuing authority as the closest prior art disclosing the features of the preamble of claim <NUM>. It shows an apparatus with a trolley for transporting articles along the path of a track and adapted to discharge articles at selected locations. The trolley comprises a conveyor, mounted for movement in a direction transverse to the track, an arm coupled to the conveyor for engaging a member positioned adjacent to the track; and a connector for coupling the arm to the belt, the connector translating movement of the arm upon engagement of the rail into transverse movement of the conveyor for discharging articles carried by the apparatus without the need for a powered drive unit for the conveyor.

Related Art. <CIT> discloses a conveyor system for sorting goods. The conveyor system is also referred to as a crossbelt-sorter. Crossbelt-sorter comprise a plurality of carts, the so-called crossbelt-sorter-carts, which are connected to each other similar to the wagons of a train. The crossbelt-sorter provides a conveying path along which the crossbelt-sorter-carts are driven and that defines a conveying direction following the conveying path of the crossbelt-sorter-carts.

Each crossbelt-sorter-cart comprises a crossbelt that is arranged with a surface facing upwards for transporting goods on it. Said upper surface of the crossbelt is arranged in a substantially horizontally plane. The crossbelt may be driven in a direction that is substantially perpendicular to the conveying direction. Thus, any good arranged on the crossbelt may be discharged and/or unloaded from the crossbelt to the left and/or the right when facing in the conveying direction. The goods may, e.g., be discharged to a predetermined side when the crossbelt-sorter-cart passes a predetermined discharge position.

Known crossbelt-sorter-carts comprise an electric motor as drive means that drives the crossbelt when receiving and/or discharging goods. Because providing each crossbelt-sorter-cart with its own electric motor is expensive, <CIT> discloses a method of driving the crossbelts mechanically. Therein, stationary activation devices, in particular lever arms, spread along the conveying path are controlled to mechanically contact friction wheels arranged at each crossbelt-sorter-cart that drive the crossbelt. At each discharge station, the lever arms may be positioned outside of the path of the friction wheel of the passing crossbelt-sorter-cart. Thus, the friction wheel is not driven and the goods are transported further on the crossbelt-sorter-cart Idle position). The activation devices of the discharge station may selectively be moved into the path of the friction wheel of the passing crossbelt-sorter-cart (drive position). This causes a rotation of the friction wheel that drives the crossbelt of the crossbelt-sorter-cart so that the goods are discharged to the side and into the discharge station.

For the known crossbelt-sorters, a problem arises whenever one of the crossbelt-sorter-carts drives along a curve at high speed. Driving the crossbelt sorter-carts at a rather high speed is desired because it enables a fast sorting of the goods and, thus, a higher performance. Inertia and/or centrifugal forces however may cause problems whenever the crossbelt-sorter-cart drives along a curve. Especially when conveying heavy goods, the centrifugal forces may accelerate the goods in a direction leading out of the curve. The goods may then accelerate the crossbelt so that the goods may fall off the crossbelt-sorter-cart to the side when driven at a high speed along a curve of the conveying path.

The above problems may occur for crossbelt-sorter-carts comprising different kinds of driving means, e.g. electric motors, engines, and/or mechanical driving means.

<CIT> discloses another crossbelt sorter Here the activation of the crossbelt is done via a movable driving belt. The driving belt is driven with a significant speed which is much above the driving speed of the crossbelt cart. Based on the speed of the driving belt in relation to the driving speed of the crossbelt cart the cross belt is driven. Hereby a worm gear drive is provided with causes significant loss of speed in the belt drive and also causes significant loss of driving power. Due to the huge speed reduction of the worm gear drive this kind of drive transmission is not compatible with the stationary activation devices (in particular lever arms) used in <CIT>.

It is an object of the invention to enable an increased performance of a crossbelt-sorter and, in particular, an increased conveying speed of a crossbelt-sorter.

The invention provides a crossbelt-sorter according to claim <NUM> and a method of transmitting torque in a cross belt-sorter according to claim <NUM>.

The crossbelt-sorter-cart of the crossbelt-sorter comprises the crossbelt arranged in an infinite loop spanning about reversing rollers at lateral sides of the crossbelt-sorter-cart. The crossbelt may be driven to rotate about said reversing rollers so that it accelerates goods arranged on an upper surface of the crossbelt in a direction lateral to the conveying direction of the crossbelt-sorter. Therein, the conveying direction may be defined as the direction in which the crossbelt-sorter-carts are driving along a conveying path provided by the crossbelt-sorter. A driven movement of the crossbelt may be desirable when goods are charged onto and/or discharged from the crossbelt-sorter-cart.

The torque transmission device of the crossbelt-sorter-cart comprises two ends, namely the drive end and the crossbelt end. Both said ends may be rotated and are thus rotatably arranged at the crossbelt-sorter-cart. The drive end is coupled to the drive means that drive the crossbelt. For example, the drive end may be coupled to a friction wheel of the crossbelt-sorter-cart and/or it may even be provided as the friction wheel. Alternatively, the drive end may be coupled to a motor as the driving means. The crossbelt end is coupled to the crossbelt, e.g. to a belt-driver like a belt drive roller accelerating the crossbelt. The crossbelt end may even be provided as a part of the belt-driver, e.g. as the barrel of the belt drive roller.

The rotation of the drive end is driven by driving means of the crossbelt-sorter-cart, for example an electric motor, an engine, or by lever arms mechanically contacting a friction wheel. The latter may be constructed similar to what is disclosed by Axmann in <CIT> identified in the introduction. The driving means generate the drive torque. The coupling means are configured to allow the transmission of the drive torque from the rotating drive end to the crossbelt end. Thus, whenever the drive end is rotating, also the crossbelt end is rotating. The crossbelt end is coupled to the crossbelt so that it drives the crossbelt of the crossbelt-sorter-cart.

The unrotatable support at which the coupling means are arranged is connected to a frame of the crossbelt-sorter-cart that prevents the support from at least rotating relative to the crossbelt-sorter-cart. Indeed, the support may be statically fixed to the crossbelt-sorter-cart so that it only moves together with the crossbelt-sorter-cart but not relative to the crossbelt-sorter-cart.

The coupling means is connected to and/or coupled to both the drive end and the crossbelt end. The coupling means is arranged between the drive end and the crossbelt end and it is provided as connector between the drive end and the crossbelt end. Thus, the drive end may be coupled to the crossbelt end via the coupling means and vice versa.

Centrifugal forces may act upon the crossbelt in a curve of the conveying path, in particular whenever a load and/or goods are arranged on the upper surface of the crossbelt. Then, the crossbelt may be accelerated in a direction out of said curve. This may cause a rotation of the crossbelt end that provides the belt torque to the coupling means. This belt torque is undesired and the torque transmission device is configured to reduce and/or inhibit and/or even eliminate said belt torque. The coupling means blocks the belt torque so that the belt torque originating from the rotating crossbelt end is suppressed and, e.g., not transmitted to the drive end.

For supressing the belt torque, the coupling means is arranged at the support. The coupling means may be connected to and/or fixed relative to the support so that it reduces and/or suppresses the rotation of the crossbelt end and does not transmit the belt torque. Rather, the coupling means remains substantially fixed to the support, thereby substantially reducing the belt torque. In this configuration, the coupling means provides a braking function for the crossbelt that prevents the crossbelt from moving when driven by centrifugal forces and/or inertia. The coupling means of the torque transmission device ensures that the crossbelt is only driven by the drive means coupled to the drive end and not whenever the crossbelt itself is pulled and/or pushed.

The coupling means is arranged at the unrotatable support so that it is not moving relative to the support when only a belt torque is acting upon the coupling means. However, whenever a drive torque is acting upon the coupling means, it may be at least partially detached from the support so that the coupling means may follow the rotation of the rotating drive end and the drive torque may be transmitted to the crossbelt end.

In other words, the coupling means may be arranged in at least two different states and/or attachment positions. In a fixed state and/or attachment position, the coupling means is substantially fixed relative to the support. Therein, the coupling means cannot rotate relative to the support and does not transmit any torque. Indeed, the inhibition of the transmission of the belt torque may result in inhibiting the rotation of the crossbelt end altogether. In an at least partially detached and/or freed state and/or attachment position, the coupling means may at least partially rotate relative to the support.

The coupling means may be reversibly brought from the fixed state and/or attachment position into the at least partially detached and/or freed state and/or attachment position and vice versa. The state and/or attachment position of the coupling means may be controlled and/or triggered by whether a drive torque or a belt torque is provided to the coupling means.

Thus, the coupling means transmits the drive torque to the crossbelt end. The coupling means is configured to inhibit any rotation of the crossbelt end that is not driven and/or caused by any drive torque originating from the rotating drive end.

In the detached state and/or attachment position, the coupling means allows a reliable driving of the crossbelt and, thus, a reliable charging and/or discharging of the goods to be sorted.

In the fixed state and/or attachment position, the coupling means inhibits the rotation of the crossbelt end and, thus, provides a braking function for the crossbelt. Said braking function may enable that the crossbelt-sorter-cart is driven along curves of the conveying path at a high speed without losing the goods due to centrifugal forces. This enables a faster sorting of the goods, more complex conveying paths along narrow curves and/or an increased performance of the crossbelt-sorter.

According to an embodiment the torque transmission device is adapted to allow transmission of the drive torque originating from the rotating drive end to the crossbelt end in a manner that the drive end rotates in a same speed as the cross belt end. This enables easy connection between the both ends without significant loss of power in a speed changing transmission.

According to an embodiment, the coupling means allows the transmission of at least <NUM>% of the drive torque originating from the rotating drive end to the crossbelt end and inhibits at least <NUM>% of the transmission of the torque originating from the rotating crossbelt end to the drive end. The transmission of not <NUM>% but only of at least <NUM>% of the transmission of the drive torque may be caused by a clearance needed to switch between the different states and/or attachment positions of the coupling means relative to the support. However, the coupling means is configured to transmit most of the drive torque to the crossbelt end and to inhibit most of the belt torque to ensure both a reliable driving and braking function.

According to the invention, the coupling means comprises a force element fixed to the support in a force fit. Therein, the force element may be fixed to the support in a friction force fit. The force fit establishes the fixed state and/or attachment position of the coupling means. The force fit is sufficiently strong to prevent a rotation of the force element relative to the support whenever only a belt torque is acting upon the force element. Also whenever no torque at all is acting up on the coupling means and/or the force element, it is fixed to the support in the force fit. However, said force fit is at least weakened if not even disengaged completely, whenever a drive torque is acting upon the coupling means and/or the force element.

According to a further development of this embodiment, the force element is provided as a spring element, e.g. as a torsion spring. The spring element may be fixed relative to the support when no torque or only a belt torque is acting upon the spring element, and it may be deformed whenever a drive torque is acting up on the spring element so that the force fit is at least weakened.

The drive torque originating from the rotating drive end at least weakens the force fit in which the force element is fixed to the support. The weakened force fit establishes the at least partially detached and/or freed state and/or attachment position of the coupling means. This enables a relative movement of the force element and/or the coupling means relative to the support. Thus, both the drive end and the crossbelt end may rotate together with the coupling means relative to the support. According to a further development of this embodiment, the drive end comprises an engaging drive element engaging the force element so that the torque originating from the rotating drive end at least weakens the force fit in which the force element is fixed to the support. Herein, the engaging drive element may be provided as a protrusion engaging the force element. The engaging drive element may be coupled to the drive end and/or may be provided as a part of the drive end that is rotating with the drive end. The engaging drive element may be in mechanical contact with the force element, at least when a drive torque is provided. Without the provision of the drive torque, the engaging drive element does not have necessarily to be in mechanical contact with the force element. The weakened force fit results in the at least partially detached and/or freed state and/or attachment position and enables the relative movement of the force element with respect to the support.

The belt torque originating from the rotating belt end strengthens the force fit in which the force element is fixed to the support. Thus, whenever the crossbelt is pulled and/or pushed, this force causing a belt torque even strengthens the force fit so that the force element cannot be moved relative to the support. Thus, the inhibition of the belt torque is strengthened which stops the crossbelt from moving. According to a further development of this embodiment, the crossbelt end comprises an engaging belt element engaging the force element so that the belt torque originating from the rotating belt end strengthens the force fit in which the force element is fixed to the support. The engaging belt element may be provided as a protrusion. It may be in mechanical contact with the force element, at least whenever a belt torque is provided. The engaging belt element may be connected to the belt end and/or may be provided as part of the crossbelt and so that any rotation of the crossbelt end causes a rotating movement of the engaging belt element.

According to an embodiment, the support comprises a through hole and/or a hollow cylinder element. A rotatable element of either the crossbelt end or the drive end is rotatably mounted within said through hole and/or cylinder element. Furthermore, a rotatable element of either the drive end or the crossbelt end is rotatably mounted around said through hole and/or cylinder element. The through hole and/or cylinder element may be statically fixed relative to the crossbelt-sorter-cart. A first rotatable element of either the crossbelt and/or the drive end is rotatably mounted within this through hole and/or cylinder element, and the second rotatable element of the other of the drive and/or the crossbelt end is rotatably mounted around said through hole and/or cylinder element. The coupling means abut at the through hole and/or the cylinder element so that they inhibit the rotation of the drive end and the crossbelt end whenever only a belt torque is acting up on the coupling means. However, when a drive torque is provided to the coupling means, the coupling means allow both a rotation of the drive end and the crossbelt end.

According to an embodiment, the support comprises an axis and/or shaft, in particular a belt drive roller axis, and the drive end and/or the crossbelt end is rotatably mounted around said axis. Herein, the coupling means may be fixed relative to and detached from the axis around which both the drive end and the crossbelt end are rotatably mounted. The axis may in particular be provided as the belt drive roller axis of a belt drive roller. The belt drive roller is driving the crossbelt and, thus, responsible for its movement. This configuration is advantageous because the relevant elements like the drive end, the crossbelt end, and the coupling means may be arranged right at the position where they are needed most. Thus, this configuration may reduce the required installation space.

According to an embodiment, the drive end is rotatable about a drive axis of rotation and a rotation of the drive end about said drive axis of rotation provides the drive torque to the coupling means. Generally, the drive axis of rotation may be arranged through the crossbelt-sorter-cart arbitrarily. However, the drive axis of rotation is preferably arranged substantially vertically or horizontally. The rotation of the drive end about the drive axis of rotation may be caused by the drive means of the crossbelt-sorter-cart and/or of the crossbelt sorter. The corresponding drive torque is provided to and acting upon the coupling means. The coupling means transmit the drive torque to the crossbelt end.

According to an embodiment, the crossbelt end is rotatable about a belt axis of rotation and a rotation of the crossbelt end about the belt axis of rotation provides the belt torque to the coupling means. Generally, the belt axis of rotation may be arranged arbitrarily. Preferably, the belt axis of rotation is arranged either substantially horizontally or substantially vertically. Because the crossbelt enables a conveying of the goods in a substantially horizontal direction and substantially perpendicular to the conveying direction of the crossbelt sorter, the belt axis of rotation may also be arranged substantially horizontally through the crossbelt-sorter-cart. However, the rotating movement of any roller about which the crossbelt is rotating may also be converted into another rotating direction, e.g. into a substantially vertical direction.

According to an embodiment, the drive axis of rotation is substantially aligned with the belt axis of rotation forming a common axis of rotation. This arrangement is advantageous to decrease the loss of torque, e.g. by friction, caused by converting the torque direction. Indeed, this enables a direct transmission of the drive torque to the crossbelt end, thereby reducing potential losses.

Therein, the common axis of rotation may be arranged so that it penetrates a through hole and/or so that it is aligned with an axis of the support. Alternatively or additionally, the common axis may be aligned substantially vertically or horizontally.

According to an embodiment, the drive end comprises and/or is coupled to a rotatable friction wheel, wherein a rotation of said friction wheel provides the drive torque for driving the crossbelt of the crossbelt-sorter-cart. Indeed, the drive end may be provided as the friction wheel of the crossbelt-sorter-cart. Thus, the rotation of the friction wheel, e.g. caused by lever arms of the crossbelt sorter, generates the drive torque. The drive end either comprises the friction wheel or it may be coupled to the friction wheel, e.g. via a gear like a bevel gear.

According to an embodiment, the crossbelt end comprises and/or is coupled to a belt drive roller driving the crossbelt of the crossbelt-sorter-cart. The belt drive roller may be in mechanical contact with the crossbelt. The crossbelt end may either encompass the belt drive roller, in particular the barrel of the belt drive roller, or it may be coupled to the belt drive roller, in particular its barrel. Said coupling may be provided by a gear, for example a bevel gear.

The conveying direction is the direction that follows the conveying path of the crossbelt-sorter-carts along the crossbelt sorter in a substantially horizontal direction. It may encompass curves and/or inclinations along the conveying path.

The lateral direction is usually considered a direction substantially perpendicular to the conveying direction and substantially horizontally. It may refer to the right and left side of the conveying path.

The invention is further illustrated in reference to embodiments shown in the figures. Embodiments of the invention are described with reference to the figures.

<FIG> is a top view of an embodiment of a crossbelt sorter <NUM>. The crossbelt sorter <NUM> comprises a plurality of crossbelt-sorter-carts <NUM> travelling in conveying direction along a closed loop as conveying path. The closed loop may have a more complex form than shown schematically in <FIG>. For example, the closed loop may comprise further curves and/or inclinations along which the crossbelt-sorter-carts <NUM> may travel.

Alternatively to the so called "horizontal" crossbelt sorter <NUM> with the closed loop, the crossbelt sorter may be provided as a so called "vertical" crossbelt sorter comprising a lower run along with the crossbelt-sorter-carts are transported back upside-down, similar to the one disclosed in <CIT> mentioned above.

<FIG> shows a sectional view of an embodiment of a crossbelt-sorter-cart <NUM>. The sectional view may, for example, be the one indicated in <FIG> by the marked line. The crossbelt-sorter-cart <NUM> comprises a plurality of guide rollers <NUM> that roll along rails <NUM> of the crossbelt sorter <NUM>. The rails <NUM> define the conveying path of the crossbelt-sorter-cart <NUM> and may follow the closed loop shown in <FIG>. In the shown embodiment, the crossbelt-sorter-cart <NUM> comprises at least four guide rollers <NUM>, two of which rolling on the rails <NUM> from above and the two others rolling on the rails <NUM> from an inclined direction from below. The rails <NUM> may be connected to and/or supported by a frame <NUM> of the crossbelt sorter <NUM>.

Each crossbelt-sorter-cart <NUM> comprises a crossbelt <NUM> spanned in a loop about two reversing rollers <NUM> at the upper end of the crossbelt-sorter-cart <NUM>. The upper surface of the crossbelt <NUM> forms a transporting surface for goods and/or wares that may be transported along the crossbelt sorter <NUM>. The crossbelt <NUM> is tensioned between the reversing rollers <NUM> so that it may roll about said reverse rollers <NUM> from a left lateral side to a right lateral side of the crossbelt-sorter-cart <NUM> and vice versa. The crossbelt <NUM> is used to discharge the goods conveyed along the crossbelt sorter <NUM> to the left and/or right whenever the crossbelt-sorter-cart <NUM> passes the desired destination. For example, the crossbelt sorter <NUM> may comprise discharge stations as shown in <CIT> mentioned above.

The crossbelt <NUM> is driven by a belt drive roller <NUM> and arranged below crossbelt <NUM> and pressing up against the lower run of the crossbelt <NUM>. The axis of rotation of the belt drive roller <NUM> is substantially parallel to the conveying direction of the crossbelt sorter <NUM> and/or substantially horizontally. The belt drive roller <NUM> is driven via a bevel gear <NUM> transmitting a substantially vertically aligned torque originating from a rotation of a friction wheel <NUM> to the belt drive roller <NUM>.

The friction wheel <NUM> is arranged at a lower section of the crossbelt-sorter-cart <NUM> so that its axis of rotation is substantially vertically aligned. In the shown embodiment, the friction wheel <NUM> comprises two disks with different diameters, an upper larger disk and a lower smaller disk. Depending upon which of the two disks of the friction wheel <NUM> is driven by a lever arm <NUM> of the crossbelt sorter <NUM>, the friction wheel of <NUM> either accelerates the crossbelt <NUM> in a fast or a slow manner.

At a plurality of positions along the conveyor <NUM>, said conveyor <NUM> may comprise one or more stationary activation device <NUM>, that selectively may either be arranged so that they do not contact the friction wheels <NUM> of the passing crossbelt-sorter-carts <NUM> (idle position) or that they engage and drive them (drive position). The stationary activation device <NUM> may be a pivotable lever arm <NUM>. The friction wheels <NUM> may be driven either when a load is received and charged onto the crossbelt <NUM> and/or it may be driven when said load is discharged at its predetermined destination along the conveying path.

<FIG> shows only a single lever <NUM> at a right side. However, another lever <NUM> may be arranged at the left side. Depending upon which of the levers is activated and moved into the path of the friction wheel <NUM>, the crossbelt <NUM> may be driven to the right or driven to the left when facing in conveying direction as in the view shown in <FIG>. The activation of the friction wheel <NUM> by the lever arms <NUM> is explained in further detail in <CIT> mentioned before.

Whenever the crossbelt-sorter-cart <NUM> is driven along a curve, centrifugal forces acting upon the load arranged on the crossbelt <NUM> may accelerate the crossbelt <NUM> so that the load may be moved to the lateral side and/or out of the curve. To inhibit this unwanted acceleration of the crossbelt <NUM>, the crossbelt-sorter-cart <NUM> comprises a torque transmission device <NUM> (not shown in <FIG>) that provides a brake or stop function.

<FIG> shows a sectional view through one embodiment of such a torque transmission device <NUM> for the crossbelt-sorter-cart <NUM>. In this embodiment, the torque transmission device <NUM> comprises components that may rotate about a substantially vertically aligned axis of rotation. Some elements of the torque transmission device <NUM> are better shown in the perspective sectional view shown in <FIG>.

A lower end of the torque transmission device <NUM> is provided by the friction wheel <NUM> of the crossbelt-sorter-cart <NUM>. The friction wheel <NUM> is shown in <FIG> and omitted in <FIG>. It serves as a drive end <NUM> and, in particular, as a rotatable element <NUM> of the drive end <NUM>. The friction wheel <NUM> and, thus, the drive end <NUM> is rotatable about a drive axis of rotation RD indicated by a dashed line. The drive axis of rotation RD is aligned substantially vertically.

The torque transmission device <NUM> is configured to transmit any drive torque originating from the rotation of the drive end <NUM> to a crossbelt end <NUM> of the torque transmission device <NUM>. The crossbelt end <NUM> is provided by a bevel gear <NUM> that may transmit and/or couple the torque to the belt drive roller <NUM> shown in <FIG>. At its upper end, the bevel gear <NUM> comprises teeth at inclined outer surfaces that may engage corresponding teeth of a similar bevel gear arranged at the shaft and/or axis of rotation of the belt drive roller <NUM> (cf.

The bevel gear <NUM> is provided as the crossbelt end <NUM> and provides a rotatable element <NUM> of the crossbelt end <NUM>. Said rotatable element <NUM> of the crossbelt end <NUM> and the crossbelt end <NUM> as a whole is rotatable about a belt axis of rotation RB. The belt axis of rotation RB is substantially vertically aligned and substantially aligned with the drive axis of rotation RD. Thus, the drive axis of rotation RD and the belt axis of rotation RB form a (here: substantially vertically aligned) common axis of rotation Rc.

The torque transmission device <NUM> is arranged at a support <NUM> of the crossbelt-sorter-cart <NUM>. The support <NUM> may be provided as a plate. It may comprise a through-hole <NUM> provided through the support <NUM> at the common axis of rotation Rc. In the shown embodiment, the support <NUM> further comprises a cylinder element <NUM> encompassing the common axis of rotation Rc at its cylinder axis. The cylinder element <NUM> is statically fixed to the support <NUM> and moves only together with the whole crossbelt-sorter-cart <NUM>. The whole support <NUM> including the cylinder element <NUM> is unrotatable relative to the crossbelt-sorter-cart <NUM> but moves together with the whole crossbelt-sorter-cart <NUM>.

At an outside of the cylinder element <NUM>, outer bearings <NUM> are arranged. The outer bearings <NUM> couple the support <NUM> to the drive end <NUM> and enable the rotation of the drive end <NUM> about the cylinder element <NUM>. Within the cylinder element <NUM>, a drive shaft <NUM> is arranged. The drive shaft <NUM> comprises an axis of rotation aligned with the common axis of rotation Rc. The drive shaft <NUM> may be fixed to the crossbelt end <NUM>, e.g. at the bevel gear <NUM>. Thus, the drive shaft <NUM> rotates together with the crossbelt end <NUM>. Also the drive shaft <NUM> may be considered as a rotatable element <NUM> of the crossbelt end <NUM>.

The drive shaft <NUM> is arranged within the cylinder element <NUM> and the through-hole <NUM> of the support <NUM> so that its axis of rotation is aligned with the centerline of the through-hole <NUM> and/or the cylinder axis of the cylinder element <NUM>. The drive shaft <NUM> is rotatably held within the cylinder element <NUM> by inner bearings <NUM>. The inner bearings <NUM> are fixed to the inside of the cylinder element <NUM> with their outer sides and may be coupled to and/or hold the drive shaft <NUM> arranged within.

Whenever the friction wheel <NUM> is activated by a lever arm <NUM> (cf. <FIG>), it rotates about the common axis of rotation Rc. The friction wheel <NUM> rotates about the cylinder element <NUM> and couples its drive torque via coupling means <NUM> to the drive shaft <NUM>. The drive shaft <NUM> rotates within the cylinder element <NUM> and transmits its torque to the bevel gear <NUM> at the crossbelt end <NUM> of the torque transmission device <NUM>.

The torque transmission device <NUM> is configured to at least inhibit a belt torque originating from the rotation of the crossbelt end <NUM>, e.g. also its transmission to the friction wheel <NUM>. The torque transmission device <NUM> may be configured to substantially inhibit any rotation of the crossbelt end <NUM> together with the rotation of the bevel gear <NUM> caused by the crossbelt torque. This enables a stop and/or brake function for the crossbelt <NUM>.

Whenever the rotation of the crossbelt end <NUM> and the bevel gear <NUM> is blocked, also the crossbelt <NUM> cannot move because it is coupled to the crossbelt end <NUM> without idle.

As shown in <FIG>, the coupling means <NUM> are provided as a force fit element <NUM>, in particular as a spring element <NUM>. The spring element <NUM> may be provided as a torsion spring comprising radially inwardly bent ends 42A. The force fit element <NUM> is arranged within the cylinder element <NUM> in a force fit so that the cylinder axis of the torsion spring substantially overlaps the cylinder axis of the cylinder element <NUM> and/or the common axis of rotation Rc. In the shown embodiment, the force fit element <NUM> presses onto the inside of the cylinder element <NUM> causing a friction force fit between them. Thus, the force fit element <NUM> may only rotate about the common axis of rotation Rc against the friction force fit in which it is held against the inside of the cylinder element <NUM>.

The crossbelt end <NUM> is coupled to an engaging belt element <NUM> via the drive shaft <NUM>. The engaging belt element <NUM> is arranged at least partially within the coupling means <NUM>. In the embodiment, the engaging belt element <NUM> is arranged at the center of the force fit element <NUM>. The engaging belt element <NUM> is fixed to the drive shaft <NUM> by a fixing element <NUM>, e.g. a screw. In an embodiment, the engaging belt element <NUM> may be provided as an element of the drive shaft <NUM>, e.g. a protrusion of the drive shaft <NUM>.

<FIG> shows a perspective view of the coupling means <NUM> from a diagonal direction from below. Therein, the friction wheel <NUM> is omitted. <FIG> shows the lower end of the cylinder element <NUM>. The cylinder element <NUM> may be a barrel of a cylinder that is statically fixed to the support <NUM> at the through-hole <NUM> so that the centerline of the through-hole is substantially arranged at the cylinder axis of the cylinder element <NUM>.

<FIG> shows the windings and/or coils of the torsion spring being pressed to the inside of the cylinder element <NUM> in the friction force fit. Each of the two ends of the spring element <NUM> is bent radially inwardly and, thus, forms an inwardly bent end 42A pointing to the inside of the cylinder element <NUM> roughly towards the common axis of rotation Rc. The inwardly bent ends 42A provide two separate obstacles within the hollow inside of the cylinder element <NUM>.

The engaging belt-element <NUM> may mechanically contact these obstacles, i.e. the inwardly bent ends 42A of the spring element <NUM> when it is rotated about the common axis of rotation Rc. The rotation of the engaging belt element <NUM> may originate from the crossbelt <NUM> being accelerated due to centrifugal forces (cf. The engaging belt element <NUM> comprises a ring section arranged around the common axis of rotation Rc. Said ring section ends at its opposite ends at two engaging flanks 21A, each facing a corresponding one of the two inwardly bent ends 42A. The engaging flank 21A is provided as a surface facing its corresponding inwardly bent end 42A. Both are substantially vertically aligned in the embodiment shown in <FIG>.

Under the provision of a belt torque, the engaging belt element <NUM> may rotate about the common axis of rotation Rc so that one of its engaging flanks 21A presses upon the corresponding inwardly bent end 42A. Depending upon the direction of said belt torque (clockwise or counterclockwise), the engaging belt element <NUM> will press upon the corresponding inwardly bent end 42A arranged in the direction in that the engaging belt element <NUM> is moved.

The spring element <NUM> is arranged and oriented within the cylinder element <NUM> so that upon contact of the engaging beltelement <NUM> with the corresponding inwardly bent end 42A, the friction force fit within the cylinder element <NUM> is strengthened. The push from the engaging flanks 21A onto its corresponding inwardly bent end 42A will try to expand the torsion spring <NUM> and increase its outer diameter. Thus, the spring element <NUM> is pressed even harder onto the inside of the cylinder element <NUM>. The provided belt torque strengthens the friction force fit so that the coupling means <NUM> cannot rotate about the common axis of rotation Rc. This blocks and/or inhibits the rotation of the engaging belt element <NUM> and, thus, the rotation of the belt end <NUM> and the whole bevel gear <NUM>. Thereby, the belt torque is suppressed and inhibited from being transmitted to the friction wheel <NUM>. Most importantly, the rotation of the bevel gear <NUM> is suppressed so that the crossbelt <NUM> cannot accelerate upon the crossbelt-sorter-cart <NUM> (cf. The torque transmission device <NUM> inhibits the transmission of the belt torque to the drive end <NUM> and provides a stopping and/or braking function for the crossbelt <NUM>.

The drive end <NUM> also comprises an engaging element, namely and engaging drive element <NUM> that engages the coupling means <NUM>. In the embodiment, the engaging drive element <NUM> is provided as a part of the friction wheel <NUM> that is omitted in <FIG>. However, the engaging drive element <NUM> is shown in <FIG> and protrudes into the spring element <NUM> from below. In an assembled state, the drive engaging element <NUM> will be arranged within a drive-side space <NUM> indicated in <FIG>. Said drive-side space extends between the two inwardly bent ends 42A on the opposite side of the engaging belt element <NUM> and within the spring element <NUM>. Therein, the engaging drive element <NUM> may form a counterpart to the engaging belt-element <NUM>.

Upon rotation of the friction wheel <NUM>, the drive end <NUM> rotates about the common axis of rotation Rc and, thus, also the engaging drive element <NUM> is rotating within the drive-side space <NUM> about the common axis of rotation Rc. Similar to the engaging belt element <NUM>, the engaging drive element <NUM> may engage flanks that may come in mechanical contact with the inwardly bent ends 42A of the spring element <NUM>.

The engaging drive element <NUM> will contact the opposite side of the inwardly bent ends 42A than the engaging belt element <NUM>. This pressure on said opposite side may weaken the friction fit. This is because the spring element <NUM> is arranged and oriented within the cylinder element <NUM> so that upon contact of the engaging drive element <NUM> with the inwardly bent ends 42A, the spring element <NUM> is tensioned and, thus, its force fit within the cylinder element <NUM> is weakened. The contact with the engaging drive element <NUM> may substantially cancel the frictional force fit within the cylinder element <NUM>. Thus, the whole coupling means <NUM> may rotate about the common axis of rotation Rc upon impact of the engaging drive element <NUM> with the inwardly bent ends 42A. Thus, a drive torque originating from the rotation of the friction wheel <NUM> weakens the force fit of the spring element <NUM> and, thus, enables its rotation and the transmission of the drive torque via the drive shaft <NUM> to the bevel gear <NUM> and the belt end <NUM>.

In other words, the torque transmission device <NUM> may inhibit the rotation of the belt end <NUM> and an according belt torque while enabling a reliable transmission of the drive torque originating from the rotation of the friction wheel <NUM> to the bevel gear <NUM> and, thus, to the belt drive roller <NUM> (cf.

<FIG> shows a perspective exploded view of the torque transmission device <NUM> shown in <FIG>. Roughly in the centre of <FIG>, the support <NUM> is shown with the cylinder element <NUM>. To the left of the support <NUM>, corresponding to an upper position in an assembled state, the bevel gear <NUM> is shown as the crossbelt end <NUM> of the gear transmission device <NUM>. The shaft <NUM> is fixed to the bevel gear <NUM> by a feather key <NUM> engaging into a groove and/or notch within the drive shaft <NUM> and/or within the bevel gear <NUM>. A support ring <NUM> may also be provided to ensure said connection. A first of the inner bearings <NUM> is shown at the left side of the support plate <NUM>.

On the other side of the support <NUM>, i.e. in a position that is arranged below the support in the assembled state, the other inner bearing <NUM> is shown together with the coupling means <NUM> provided as a spring element <NUM>. The spring element <NUM> is arranged so that its two ends bent inwardly towards the common axis of rotation Rc.

<FIG> further shows the engaging belt element <NUM> and the fixing element <NUM>. A snap ring <NUM> and/or retaining rings <NUM> may be provided to ensure the position of the outer bearings <NUM> enabling the rotation of the friction wheel <NUM> as drive end <NUM> about the outer barrel of the cylinder element <NUM>.

All of the above elements of the torque transmission device <NUM> that comprise a circular and/or cylindric form are arranged so that their centerline and/or cylinder axis is substantially aligned with the common axis of rotation Rc.

In an alternative embodiment not shown in the figures, the drive axis of rotation RD does not necessarily have to be aligned with the belt axis of rotation RB. These axes may be inclined to each other with the coupling means arranged at their intersection.

<FIG> shows the spring element <NUM> as used in the torque transmission device <NUM> of <FIG> and <FIG>. The spring element <NUM> is provided as torsion spring with two inwardly bent ends 42A that separate the inside of the torsion spring into two sections, namely a belt-side space <NUM> and the drive-side space <NUM>. The belt-side space <NUM> is the area within the spring element <NUM> from which pressure onto the inwardly bent ends 42A of the spring element <NUM> will increase the diameter of the spring element <NUM> and, thus, strengthen the friction fit within the cylinder element <NUM>. The drive side space <NUM> is the area from which a pressure onto the inwardly bent ends 42A of the spring element <NUM> will decrease the total diameter of the torsion spring and, thus, weaken the friction of force fit within the cylinder element <NUM>.

<FIG> shows an alternative embodiment of a spring element <NUM> as coupling means <NUM> and force fit element <NUM>. In this alternative embodiment, the spring element <NUM> comprises radially outwardly bent ends 42B. This embodiment of the spring element <NUM> may be assembled in a friction force fit upon an element protruding through the spring element <NUM>. As shown in reference to the following figures, the spring element <NUM> shown in <FIG> may be arranged upon a shaft-like and/or axis-like support in another embodiment of the torque transmission device <NUM>.

The outwardly bent ends 42B of the torsion spring define the limits between the drive-side space <NUM> and the belt-side space <NUM> outside of the spring element <NUM>. Similar as in the previous embodiment, a pressure from the drive-side space <NUM> upon at least one of the outwardly bent ends 42B may weaken the friction fit of the spring element <NUM> by increasing its inner diameter. Thereby, the friction fit on the shaft-like support may be released. Pressure from the belt-side space <NUM> upon the outwardly bent ends 42B will strengthen the friction force fit by reducing the inner diameter of the spring element <NUM>.

<FIG> shows a perspective view of a gear of a crossbelt-sorter-cart <NUM>. <FIG> shows the friction wheel <NUM> at a lower section that drives the bevel gear <NUM> by a substantially vertically aligned torque. The rotation of the bevel gear <NUM> is transmitted via diagonally aligned teeth onto a belt drive roller bevel gear <NUM> arranged upon a belt drive roller axis and/or shaft <NUM>. The belt drive roller axis <NUM> is arranged essentially horizontally and substantially parallel to a conveying direction of the crossbelt sorter <NUM> (cf. Thus, the torque provided by the rotation of the friction wheel <NUM> may be used to drive a rotation of the belt drive roller <NUM> rotating about and/or with the roller axis <NUM>. This is comparable to the situation as shown in <FIG>.

The rotation of the belt drive roller <NUM> may cause an opposed rotation of a pressure roller <NUM>, because their barrels are pressed together and/or biased. The barrels of the pressure roller <NUM> and the belt drive roller <NUM> may be in (at least indirect) mechanical contact with each. The pressure roller <NUM> and the belt drive roller <NUM> may rotate together about axes that are substantially parallel to each other in opposite directions.

Between the barrels of the pressure roller <NUM> and the belt drive roller <NUM>, the lower run of the crossbelt <NUM> is arranged (thus the indirect mechanical contact between them). The crossbelt <NUM> is only shown stylized in <FIG> by the two lines. Otherwise, the surface of the crossbelt <NUM> would block the view onto the elements of the crossbelt-sorter-cart <NUM>. The upper run of the crossbelt <NUM> may run over an upper side of the pressure roller <NUM> while the lower run is arranged between the lower side of the pressure roller <NUM> and the upper side of the belt drive roller <NUM>. Thus, a rotation of the belt drive roller <NUM> causes the crossbelt <NUM> to move between the belt drive roller <NUM> and the pressure roller <NUM>.

Similarly, an acceleration of the crossbelt <NUM> will also cause a rotation of the belt drive roller <NUM>. Without the torque transmission device <NUM>, its rotation would be transmitted by the gear <NUM>, <NUM> to the friction wheel <NUM>. Such an acceleration of the crossbelt <NUM> caused by, e.g., centrifugal forces may be suppressed by the torque transmission device <NUM> by inhibiting the rotation of the bevel gear <NUM> and/or the belt drive roller <NUM>.

<FIG> shows a side view of an embodiment of a torque transmission device <NUM> for a crossbelt-sorter-cart. Therein, the torque is transmitted along a substantially horizontally aligned axis. <FIG> shows an embodiment arranged a position close to the gear which converts a vertical torque into a horizontal torque, similar to the gear <NUM>, <NUM> shown in <FIG>.

At a lower section, the friction wheel <NUM> is arranged as also shown in <FIG> and <FIG>. The friction wheel <NUM> may be driven by lever arms <NUM> similar to the one shown in <FIG>. At activation, the friction wheel <NUM> rotates about a substantially vertically aligned axis of rotation about which also the bevel gear <NUM> will rotate. In the shown embodiment, the bevel gear <NUM> is not provided with diagonally aligned teeth as in the previous embodiment, but rather with a diagonal friction surface that also allows a transmission of its torque onto the belt drive roller bevel gear <NUM>. Therein, the torque is not transferred by a form fit as in the previous embodiment, but by friction of the diagonally aligned friction surfaces of the two bevel gears <NUM>, <NUM>. Otherwise, the gear works similar to the gear with the diagonal teeth as shown, e.g., in <FIG> and/or at least partially shown in <FIG>, <FIG> and <FIG>. The belt drive roller bevel gear <NUM> may rotate about the belt drive roller axis <NUM> about a substantially horizontally aligned axis of rotation. The barrel of the belt drive roller <NUM> may be driven to a rotation by the rotation of the belt drive roller bevel gear <NUM>. Similar as shown in <FIG> and <FIG>, the rotation of the barrel of the belt drive roller <NUM> drives the crossbelt <NUM> arranged between the belt drive roller <NUM> and the pressure roller <NUM> arranged above (omitted in <FIG>).

<FIG> shows a sectional side view of the torque transmission device <NUM> of <FIG>. The sectional view shows the inside of the belt drive roller <NUM>. In this embodiment, the torque transmission device <NUM> is not arranged at the friction wheel <NUM>, Thus, the friction wheel <NUM> may transmit its torque directly via the drive shaft <NUM> to the bevel gear <NUM>. The drive shaft <NUM> may be rotatably connected via inner bearings <NUM> to a cylinder element <NUM> connected to a first frame element <NUM>. The diagonal upper outer side of the bevel gear <NUM> may be covered by a friction element increasing the friction between the substantially vertically element bevel gear <NUM> and the substantially horizontally aligned belt drive roller bevel gear <NUM>.

Whenever the friction wheel <NUM> is driven, its torque is transmitted to the belt drive roller bevel gear <NUM> causing a rotation of the belt drive roller bevel gear <NUM> about the drive-axis of rotation RD which is arranged substantially horizontally, substantially in conveying direction and/or substantially within the extension direction of the belt drive roller axis <NUM>. The belt drive roller bevel gear <NUM> is mounted rotatably about the belt drive roller axis <NUM> via at least one inner bearing <NUM> arranged on the belt drive roller axis <NUM>. The belt drive roller axis <NUM> is arranged in a fixed position relative to the crossbelt-sorter-cart <NUM>. It may be connected to the first frame element <NUM> and/or a second frame element <NUM>. The belt drive roller axis <NUM> may be arranged with at its two opposite axle ends between the first and second frame elements <NUM> and <NUM>. In this fixed position, the belt drive roller axis <NUM> provides the support <NUM> of the torque transmission device <NUM>. The belt drive roller bevel gear <NUM> provides the drive end <NUM> and the rotatable element <NUM> of the drive end <NUM> of the torque transmission device <NUM>. It is rotatably mounted about the support <NUM> in form of the belt drive roller axis <NUM> defining the drive axis of rotation RD.

At the end of the belt drive roller bevel gear <NUM> facing the bevel gear <NUM> connected to the friction wheel <NUM>, the belt drive roller bevel gear <NUM> protrudes out of the barrel of the belt drive roller <NUM>. The belt drive roller bevel gear <NUM> may comprise a cylindric element arranged within the belt drive roller <NUM> that extends substantially along the whole barrel of the belt drive roller <NUM>. At the end facing the bevel gear <NUM>, it comprises the inclined surfaces for receiving the torque from the bevel gear <NUM>. At its opposite end, i.e. the end facing away from the bevel gear <NUM>, the engaging drive element <NUM> (cf. <FIG>) is provided as an extension of the drive end <NUM>. The engaging drive element <NUM> is arranged so that it may interact with the coupling means <NUM> provided as a force fit element <NUM> in form of a spring element <NUM>.

The spring element <NUM> may be the torsion spring shown in <FIG> that comprises the outwardly bent ends 42B. The spring element <NUM> is arranged around the drive belt roller axis <NUM> in a force fit, i.e. a friction force fit. Thereby, its windings/coils are wound about the drive belt roller axis <NUM>. Thus, the spring element <NUM> sits tightly around the drive belt roller axis <NUM> so that its outwardly bent ends 42B extend substantially radially outwards from the belt drive roller axis <NUM>. The coupling means <NUM> are arranged at the end of the drive belt roller axis <NUM> facing away from the bevel gear <NUM>.

At least one, preferably two, outer bearing(s) <NUM> are arranged around the outer barrel of the drive end <NUM>. The barrel of the belt drive roller <NUM> is mounted on these outer bearing(s) <NUM> so that it may rotate both about the belt drive roller axis <NUM> arranged at its cylinder axis and about the drive end <NUM> and/or the rotatable element <NUM> of the drive end <NUM>. The barrel of the belt drive roller <NUM> may rotate about a belt axis of rotation RB which is, in the shown embodiment, substantially aligned with the drive axis of rotation RD, thus forming a common axis of rotation Rc.

A rotation of the rotatable element <NUM> of the drive end <NUM> about the common axis of rotation Rc driven by the friction wheel <NUM> provides the drive torque to the coupling means <NUM>. A rotation of the barrel of the belt drive roller <NUM> and, thus, the crossbelt end <NUM> of the torque transmission device <NUM> (e.g. caused by an acceleration of the crossbelt <NUM>) about the common axis of rotation Rc provides the belt torque to the coupling means <NUM>. The torque transmission device <NUM> is configured, exactly as the embodiment shown in the previous Figures, to allow the transmission of the drive torque from the rotatable element <NUM> of the drive end <NUM> to the rotatable element <NUM> of the crossbelt end <NUM>. Furthermore, the torque transmission device <NUM> inhibits the rotation of the rotatable element <NUM> of the belt end <NUM> and the transmission of its torque to the rotatable element <NUM> of the drive end <NUM>. This transmitting and inhibiting is enabled by means of the coupling means <NUM> and the support <NUM>.

<FIG> is a perspective view of the end of the belt drive roller axis <NUM> at which the coupling means <NUM> is arranged in a force fit. In this perspective view, the first frame element <NUM> is omitted to grant a better view on the coupling means <NUM>. In axial direction, the coupling means <NUM> may be held in position by one or more retaining rings <NUM> mounted on the outer diameter of the belt drive roller axis <NUM>. The outwardly bent ends 42B of the spring element <NUM> define the drive-side space <NUM> and the belt-side space <NUM>. In the shown embodiment, these spaces <NUM>, <NUM> are arranged within an area inside the crossbelt end <NUM> (provided by the belt drive roller <NUM>) and radially outward of the coils of the spring element <NUM>.

Fixed to the inside of the barrel of the belt drive roller <NUM> is the engaging belt element <NUM>. Engaging belt element <NUM> is provided as a ring section about the common axis of rotation Rc. The ring section may span over an angular section of at least <NUM>°, preferably at least <NUM>°, more preferably of at least <NUM>° with respect to the common axis of rotation Rc. Thus, the engaging belt end <NUM> may fill most and/or substantially the whole angular section of the belt side space <NUM>, e.g. at least <NUM>% or preferably at least <NUM>% of it. This leaves only a small clearing between the engaging flanks 21A and the outwardly bent ends 42B of the spring element <NUM>.

A rotation of the belt end <NUM> caused by an acceleration of the crossbelt <NUM> will rotate the engaging belt element <NUM> about the common axis of rotation Rc until one of its engaging flanks 21A abuts the corresponding outwardly bent end 42B of the spring element <NUM>. This abutting will strengthen the friction force fit of the spring element <NUM> with the support <NUM> in form of the belt drive roller axis <NUM>. Thus, the rotation of the belt end <NUM> and the belt drive roller <NUM> is inhibited and stopped.

Similarly, also the drive end <NUM> provided by the belt drive roller bevel gear <NUM> is connected to and/or comprises a protrusion in form of the engaging drive element <NUM>. This engaging drive element <NUM> is arranged within the drive-side space <NUM>, i.e. in a position radially between the spring element <NUM> and the inside of the barrel of the belt drive roller <NUM>. The engaging drive element <NUM> may be provided as a ring section a ring spanning about at least <NUM>°, preferably about at least <NUM>°, more preferably about at least <NUM>° about the common axis of rotation Rc within the drive side space <NUM>.

Two engaging flanks 11A at the opposite ring section ends of the engaging drive element <NUM> are arranged within vicinity of the two outwardly bent ends 42B of the spring element <NUM>. Any rotation of the friction wheel <NUM> resulting in a corresponding rotation of the drive end <NUM> leads to a corresponding rotation of the engaging drive element <NUM> about the common axis of rotation Rc until one of its engaging flanks 11A press onto the corresponding outwardly bent end 42B. This pressure is directed so that it weakens the force fit of the spring element <NUM> on the support shaft and/or axis <NUM>. This allows a rotation of the coupling means <NUM> about the support <NUM> in form of the drive belt roller axis <NUM> and a transmission of the torque of the drive end <NUM> to the engaging belt element <NUM> of the crossbelt end <NUM>. Thus, the drive torque is transferred to the crossbelt end <NUM> and may drive the belt drive roller <NUM>.

The torque transmission devices <NUM> shown in the Figures operate similarly. The engaging drive element <NUM> and the engaging belt element <NUM> may span over most of the whole angular section of <NUM>° about the common axis of rotation Rc. In the remaining clearance, the ends 42A, 42B of the respective spring element <NUM> may be arranged within a small clearance. The engaging drive element <NUM> and the engaging belt element <NUM> may be arranged in vicinity of the spring element <NUM> so that one of the engaging flanks 11A of the engaging drive element <NUM> is separated from a corresponding engaging element 21A of the engaging belt element <NUM> by one of the ends 42A, 42B, respectively. Every engaging flank 11A of the engaging drive element <NUM> substantially faces its corresponding engaging element 21A of the engaging belt element <NUM>.

The engaging flanks 11A, 21A may be provided as flat surfaces and/or may incorporate at least one groove for receiving the corresponding end 42A, 42B of the spring element <NUM>. The groove may receive the respective end 42A, 42B and, thus, decrease the strain on the spring element <NUM>. Furthermore, it may enable an abutment of the substantially full, corresponding engaging flanks 11A, 21A for a safe transmission of the drive torque.

The drive means causing the drive torque may be provided by the friction wheel <NUM> and/or the lever arms <NUM>. Thus, the drive means may be part of the crossbelt-sorter-cart <NUM> itself and/or may be arranged stationary at the crossbelt-sorter <NUM>.

Claim 1:
A crossbelt-sorter (<NUM>) having at least one crossbelt-sorter-cart (<NUM>),
the crossbelt-sorter-cart (<NUM>) comprising:
- a frame (<NUM>);
- a crossbelt (<NUM>), mounted movably relative to the frame (<NUM>);
- a drive means (<NUM>) for driving the movement of the crossbelt ;
- a torque transmission device (<NUM>),
the torque transmission device (<NUM>) comprising:
- a rotatable drive end (<NUM>), which is, in particular at least temporarily, coupled to the drive means (<NUM>) for driving the crossbelt (<NUM>) of the crossbelt-sorter-cart (<NUM>);
- a rotatable crossbelt end (<NUM>) coupled to the crossbelt (<NUM>);
- an unrotatable support (<NUM>) connected, in particular fixed, to the crossbelt-sorter cart (<NUM>); and
- a coupling means (<NUM>) connecting the drive end (<NUM>) to the crossbelt end (<NUM>) at the support (<NUM>),
wherein the coupling means (<NUM>) allows a transmission of a drive torque originating from the rotating drive end (<NUM>) to the crossbelt end (<NUM>) and inhibits a belt torque originating from the rotating crossbelt end (<NUM>),
characterized in
that the coupling means (<NUM>) comprises a force element (<NUM>, <NUM>) fixed to the support (<NUM>) in a force fit, wherein the drive torque originating from the rotating drive end (<NUM>) at least weakens the force fit in which the force element (<NUM>, <NUM>) is fixed to the support (<NUM>), wherein the belt torque originating from the rotating crossbelt end (<NUM>) strengthens the force fit in which the force element (<NUM>, <NUM>) is fixed to the support (<NUM>).