RU2532155C1 - Redirection and changeover mechanisms exploiting variable-diameter rollers - Google Patents

Abstract

FIELD: transport.

SUBSTANCE: proposed mechanism serves to change the sheet direction and comprises pairs of rollers. Note that both rollers in every pair are located in common plate of revolution and have adjustable clearance there between so that the sheet can be fed through said clearance. Note also that pairs of rollers are located successively every pair defining the direction of motion within the boundaries of sheet path. Proposed mechanism differs from know designs that at least one pair of rollers located downstream of the first pair of rollers in motion path is located across the first pair of rollers in motion path. Note also the at least one roller of whatever pair is a variable-diameter roller.

EFFECT: high speed and precision of transfer.

26 cl, 32 dwg

Description

BACKGROUND OF THE INVENTION

In General, the invention relates to the manipulation of sheet-like material. First of all, the invention relates to a redirection mechanism and a switching mechanism using rollers of variable diameter. The redirection mechanism and the switching mechanism according to the invention can be used in transport systems for manipulating sheets, and more particularly in banknote manipulation machines.

In addition, the invention relates to rollers of variable diameter, which can be used in transport systems for handling sheets. More specifically, variable diameter rollers according to the invention can be used in banknote handling machines.

In banknote manipulation machines, redirection mechanisms selectively direct the transported sheet to one of the transport directions. In banknote handling machines, transported sheets move at a high speed (usually above 2.7 m / s). In order to maintain this speed, the mechanisms must work quickly and with high accuracy.

US 5,480,022 (Matsuda et al.) Discloses a redirection mechanism for changing the direction of movement of an object transported by a conveyor belt. This mechanism uses rollers of variable diameter. The mechanism contains sequentially located rollers that specify the trajectory of movement for the transported object. In addition, the mechanism comprises rollers located transverse to the upstream rollers for transporting the object in the transverse direction. In the mechanism, rollers of variable diameter are used as transverse rollers, in their reduced configuration remaining below the level of the conveyor belts so that the object can move on the conveyor belts, and in their expanded configuration, raising the object above the conveyor belt to transport it in the transverse direction. The mechanism is reversible.

Obviously, the use of the mechanism is limited to solid three-dimensional objects. The mechanism is not suitable for handling lightweight and flexible sheets such as banknotes.

A switching mechanism for selectively guiding a sheet to one of two conveying directions is disclosed in US 6,547,241 (Yoshida et al.). The mechanism comprises a pair of guide rollers, such that the sheet can be fed between the rollers in pairs, and a rotatable separation element downstream of the guide rollers, and the separation element has two guide sides, each side defining one of the transport directions. Directions are selected by rotating the spacer between the first and second positions. In the first position, the receiving surface on the first side of the separation element is tangentially in the path of the transported sheet, so that the sheet engages in a guide engagement with the separation element and is guided further by its guide side following the receiving side on the first side in the first conveying direction. In the second position, the receiving side on the second side of the separation element is tangentially located in the path of the transported sheet, so that the sheet engages in a guide engagement with the separation element and is guided further by its guide surface following the receiving surface on the second side in the second conveying direction.

The guide surfaces on the separation element are long enough to smoothly guide the sheets into their respective transport directions. Therefore, the separation element has a significant size and, therefore, mass. In order to maintain high handling speeds in the handling machine, the massive spacer element must rotate between its positions for a very short time with high accuracy, and this can be a problem. In addition, the rotation of the spacer element may generate noise and cause severe wear on the device providing this rotation.

A roller of variable diameter, provided with a pair of sliding disks mounted on the axis of the roller and arranged to move to each other and from each other in the axial direction by means of a drive mechanism, is disclosed in publication US 2003/0136643 (Mayerberg II et al.). A drum-shaped resilient member is located between the sliding discs. Axial compression of an elastic element by disks leads to its radial expansion. The roller is used to drive the conveyor belt. However, this roller must have a large axial dimension to provide a tangible change in diameter. This may be acceptable in conveyor belts, but in banknote handling machines, space is much more limited. In addition, for the stability of the sheet transported in the banknote handling machine, it is preferable that the sheet is clamped by at least two axially spaced pairs of rollers. This is another factor limiting the axial size of the roller, which will be much less than half the transverse size of the sheet. In addition, a larger diameter roller may become uneven along the edge due to the natural heterogeneity of the material of the roller. This may affect the stability of the clamp / release sheets. To overcome this drawback, high-quality rubber in a drum-shaped elastic member can be applied. However, this will increase costs.

US 5,480,022 (Matsuda et al.) Discloses a roller of variable diameter comprising a roller body and a segmented rim, with each rim segment movably mounted on the roller body. In addition, the roller contains plungers made with the possibility of reciprocating radially relative to the housing of the roller, with each plunger connected to a segment of the rim. The plungers are driven by a pneumatic system. This requires a rather complicated sealing system, which includes elastic sealing diaphragms provided for each plunger and a source of compressed air under high pressure.

OBJECTS OF THE INVENTION

The purpose of the invention is to create a redirection mechanism for changing the direction of movement of lightweight and flexible sheets, such as banknotes. In addition, the aim of the invention is to provide a redirection mechanism having sufficient speed and accuracy for use in transport systems for manipulating sheets, more specifically, in machines for manipulating banknotes.

Another objective of the invention is to provide a switching mechanism for selectively guiding lightweight and flexible sheets, such as banknotes, into one of at least two conveying directions. Another objective of the invention is to create a switching mechanism having sufficient speed and accuracy for use in transport systems for manipulating sheets, more specifically, in machines for manipulating banknotes.

Another objective of the invention is to create a roller of variable diameter, which can be used in the redirection mechanism and the switching mechanism according to the invention. In addition, the aim of the invention is to create a roller of variable diameter, which can change its diameter with high speed and accuracy.

Another objective of the invention is to create a roller of variable diameter, which may have a configuration in which it has an intermediate diameter between the increased diameter and the reduced diameter.

SUMMARY OF THE INVENTION

The above objectives are achieved by creating a redirection mechanism to change the direction of movement of the sheet containing pairs of rollers, both rollers in each pair lying in the common plane of rotation and have an adjustable gap between them, so that the sheet can be fed through the gap, and the pairs of rollers are arranged in series, each pair sets the direction of movement within the path for a sheet, characterized in that at least one pair of rollers downstream of the first pair of rollers in the path It is transverse to the first pair of rollers in the trajectory of motion, and at least one roller in any pair of rollers is a roller of variable diameter. The use of pairs of rollers, including rollers of variable diameter, provides quick and accurate sheet redirection.

At least one roller in at least one pair of rollers may be a drive roller. Thus, no additional drive means is required to move the sheet along the path.

Each roller in the mechanism can be equipped with a similar roller located axially at a distance. Preferably, the pairs of rollers should be spaced so as to remain within the appropriate size of the banknote as it moves between them. This will lead to increased stability.

In the absence of, or in addition to, drive rollers, the drive side of the conveyor belt may be passed between at least one pair of rollers to act as drive and / or sheet guiding means.

In addition, the above objectives are achieved by creating a switching mechanism for the selective direction of the sheet in one of at least two directions of transportation, including at least one pair of guide rollers, made so that the sheet can be fed between the rollers in pairs, and at least one spacer element downstream of at least one pair of guide rollers, and at least one spacer element has two sides, each side defining one of the directions a conveyor, characterized in that at least one pair of guide rollers includes at least one roller of variable diameter, and the guide rollers and the spacer element are designed to guide the sheet on one side of the spacer element, when the diameter of the at least one roller of variable diameter increases , and to direct the sheet to the other side of the spacer member when the diameter of at least one roller of variable diameter decreases.

In the switching mechanism according to the invention, the separation element has a fixed position, therefore, in contrast to US 6547241 by Yoshida et al., The problem of turning the separation element between its positions in a very short time is eliminated with high accuracy.

At least one roller in at least one pair of guide rollers may be a drive roller. Thus, no additional drive means is required to move the sheet along the path.

In each pair of guide rollers, one roller may have a fixed axis, and the other roller may have a movable axis to be spring loaded relative to the fixed axis roller.

Alternatively, in each pair of guide rollers, both rollers may have movable axes, with one guide roller being spring loaded relative to the other guide roller, the latter being spring loaded relative to the holding roller having a fixed axis.

Both rollers in each pair of guide rollers can be rollers of variable diameter, and each roller in a pair is configured to reduce its diameter when the diameter of the other roller in the pair increases, and to increase its diameter when the diameter of the other roller in the pair decreases. In this embodiment, the speeds of rotation of the rollers must be variable to move the sheet at a constant speed.

Another separating element may be located parallel to the first with a gap formed between them. In this embodiment, the rollers of variable diameter should be configured to have an intermediate diameter between the increased diameter and the reduced diameter, and the guide rollers and spacer elements should be made to guide the sheet into the gap between the two spacer elements when the diameter of the roller of variable diameter is intermediate. This configuration provides the ability to switch sheets to three motion paths.

In addition, the above objectives are achieved by creating a roller of variable diameter containing a pair of sliding disks mounted and centered on the axis of the roller and configured to move to each other and from each other in the axial direction by means of a drive mechanism, the flexible rim element being connected to each of sliding disks, with each flexible element of the rim protruding beyond the sliding disk in the axial direction to another flexible element of the rim, and the flexible elements of the rim are made so that the movement the sliding disks towards each other would press the flexible elements of the rim against each other, thus causing a radial expansion of the flexible elements of the rim. Unlike the drum-shaped resilient member used in US 2003/0136643 (Mayerberg II et al.), Flexible rim members are used for compression by sliding disks. This reduces the axial size of the roller. In addition, flexible rim elements made of sheet rubber are cheaper than a drum-shaped elastic element of high quality rubber.

In addition, the roller may comprise a roller casing in which a pair of sliding disks is mounted, the edge of the roller casing having two rims located so that there is a radially open annular gap between them, and the flexible elements of the rim are shaped and arranged so that they pass through the annular gap when radial expansion of the flexible elements of the rim occurs.

Preferably, in addition, the roller contains a guide element located between the flexible elements of the rim to facilitate the translation of the axial deformation of the flexible elements of the rim in their radial expansion and to facilitate the direction of the flexible elements of the rim through the annular gap. The guide element makes the roller work more stable and accurate.

Each flexible element of the rim may be in the form of a flat ring, the inner diameter of the ring being smaller than the diameter of the saddle on the sliding ring to accommodate the flexible element of the rim.

The drive mechanism may comprise an axial plunger passing through the roller body. The sliding discs and the axial plunger can be connected to a link mechanism configured to convert the reciprocating motion of the axial plunger into the movement of the sliding discs.

Alternatively, the drive mechanism may comprise a central component rotationally connected to the roller housing. The sliding discs and the central part may be connected to means configured to convert the rotation of the central part to the movement of the sliding discs.

In addition, the above objectives are achieved by creating a roller of variable diameter comprising a roller casing and a segmented rim, wherein each rim segment is movably mounted on the roller casing, in addition, the roller contains a central part mounted centrally relative to the roller casing and configured to move at least between by two positions by means of a drive mechanism, the rim segments being respectively engaged with the central part so that the movement of the central part is pre Braz, at least a radial displacement of the rim segments. Unlike US 5,480,022 (Matsuda et al.), Pneumatics are not used to move rim segments in the roller. Accordingly, a sealing system is not used.

The central part may be rotatable between at least two positions, and the central part may have eccentric pivot points spaced around the circumference. In addition, the roller may contain levers having their axis of rotation spaced around the circumference on the roller housing, each lever containing a rim segment, and the engagement between the rim segments and the central part can be realized by rods having their first ends pivotally connected to the shoulders corresponding levers, and having their second ends, respectively connected to the corresponding turning points of the central part.

Alternatively, reciprocating radially relative to the roller housing, the plungers can be used with a central part that is capable of pivoting between at least two positions and provided with eccentric pivot points spaced apart along the edge. Each plunger can be connected to a segment of the rim, and the engagement between the plungers and the central part can be realized by rods having their first ends, pivotally connected to the corresponding plungers, and having their second ends, respectively connected to the corresponding turning points of the central part.

The central part may be a gear, each rim segment may be rotatably mounted on the roller housing and provided with teeth that mesh with the teeth of the central part.

Alternatively, the central part may be an axial plunger passing through the roller housing and configured to reciprocate. In this embodiment, the roller may further comprise radial plungers arranged to reciprocate with respect to the roller body, each plunger being connected to a rim segment, the engagement between the plungers and the central part being carried out by rods having their first ends pivotally connected with corresponding plungers, and having their second ends, respectively connected to the corresponding turning points of the central part.

In addition, the above objectives are achieved by creating a roller of variable diameter containing an axis and a plurality of partially overlapping segment elements, wherein each segment element is movable relative to the axis of the roller by a drive mechanism, characterized in that the contour of each segment element has at least two parts each of which has an arc configuration, the radius of the arc in one part of the segment element being different from the radius of the arc in the other part of the segment element one, the drive mechanism being configured to move each segment element to any of at least two positions, and in each of at least two positions parts of the segment elements having the same corresponding radius together form a circular edge of a roller having a corresponding diameter.

In addition, the roller may comprise a concentric axis of the roller of the round casing, the outer diameter of the casing being smaller than the diameter of the circular edge of the roller at any specified position of the segment elements, and the drive mechanism is further configured to move each segment element to the position where the segment element located radially within the roller housing.

Brief Description of the Drawings

The present invention will be more apparent by describing some exemplary embodiments with reference to the accompanying drawings. Shown on:

Figure 1: schematically, a side view and an end view of one embodiment of the claimed redirection mechanism, in which the sheet enters the mechanism,

Figure 2: schematically, a side view and an end view of the variant according to figure 1, in which the sheet is fed across,

Figure 3: schematically, a side view and an end view of another embodiment of the claimed redirection mechanism, in which the sheet enters the mechanism,

Figure 4: schematically, a side view and an end view of the variant according to figure 3, in which the sheet is fed across,

5-9: schematically, a side view, a top view and an end view of various embodiments of the claimed switching mechanism

10-12: schematically, a cross section of the claimed roller of variable diameter, which could be applied in three configurations in the claimed switching mechanism,

13-16: schematically, a cross-section of another embodiment of a roller of variable diameter, which can be applied in four configurations in the claimed switching mechanism,

Figa-17G: the location of the round casing and a possible drive mechanism in the claimed roller of variable diameter,

Fig: schematically, a side view, a top view and an end view of an embodiment of the claimed switching mechanism comprising two spacer elements,

Fig.19-32: cross sections of other embodiments of the claimed roller of variable diameter.

Detailed Description of Exemplary Embodiments

Now, some exemplary embodiments of the present invention will be described in more detail with reference to the accompanying drawings.

Figure 1 and figure 2 schematically shows a side view and an end view of an exemplary embodiment of the redirection mechanism 1 used to change the direction of movement of the sheet, such as banknotes 4. The mechanism can be integrated into a machine for manipulating banknotes (not shown), for example, following a sensor (not shown in the drawings) for analyzing banknotes. The mechanism 1 comprises rollers 2 of variable diameter and support rollers 3 arranged in pairs 5-10, defining a path for a sheet, for example banknote 4. Both rollers 2 and 3 in each pair lie in a common plane of rotation, that is, both rollers 2 and 3 in each pair are rollers of opposite rotation with parallel axes and edge surfaces that define an adjustable clamping gap between them, so that banknotes 4 can be fed through an appropriately adjusted gap. Banknote 4 can move downstream when the gap between the rollers 2 and 3 of each pair is minimal and the rollers rotate synchronously in different directions, preferably having the same tangential speed in the gap between them. Preferably, each roller 2 is connected to a continuously operating drive (not shown in the drawings), an adjustable or constant speed of rotation. Thus, each roller 2 is a drive roller, while each roller 3 is a freely rotating roller. It will be apparent to those skilled in the art that the number of drive rollers 2 may vary, and the support rollers 3 may also be drive rollers. Additionally or alternatively, other drive means, such as a conveyor belt, passed between at least one pair of pairs of 5-10 rollers 2 and 3, can be used to move the banknotes, as described below with reference to FIGS. 3 and 4.

In the embodiment shown in FIGS. 1 and 2, pairs of rollers 5, 6, 7, and 8 are arranged in a line, forming a rectilinear or longitudinal part of the path for banknotes 4 in the mechanism 1. Preferably, the central part of the banknote 4 is fed through a gap defined between the rollers of pairs 5, 6, 7 and 8. For specialists it should be obvious that at least one of the pairs 5, 6, 7 and 8 can be provided with axially spaced pairs of rollers (not shown), which are laterally parallel to the corresponding pairs 5, 6, 7 and 8 on the same axles rotation. In this case, the Central part of the banknote 4, preferably, should be located centrally between the respective axially spaced pairs of rollers during movement.

Pairs of rollers 9 and 10, which form the rest of the motion path or the transverse part of the motion path, are located across the upstream pair of rollers 5. The pairs of 9 and 10 rollers are axially spaced relative to each other, that is, they are located at a distance between each other along the longitudinal part of the trajectory defined by the pairs of 5, 6, 7 and 8 rollers.

In the process, the banknote 4 is included in the redirection mechanism 1, for example, comes from the upstream mechanism into the machine for manipulating banknotes. For specialists, it should be obvious that the redirection mechanism 1 may contain appropriate guiding means (not shown in the drawings) for guiding the incoming banknote into the gap between the rollers 2 and 3 of the pair 5. In the first "longitudinal" stage shown in figure 1, the rollers 2 the variable diameter pairs 5, 6, 7 and 8 are in their expanded configuration and have an increased diameter, so that the gap between the rollers 2 and 3 pairs 5, 6, 7 and 8 is minimized to enable clamping of the banknote 4. The front end of the banknote 4, inserted into the gap between the rotating with rollers 2 and 3 of pair 5, it is clamped and carried away downstream by rollers 2 and 3 of pair 5, and then sequentially rotating rollers 2 and 3 of pairs 6, 7 and 8. In figure 1, banknote 4 is shown in the position when its front end all 5-8 pairs went along the longitudinal part of the trajectory, just before the start of the next stage.

In the next “transverse" stage shown in FIG. 2, the rollers 2 of variable diameter pairs 5, 6, 7 and 8 are converted to their reduced configuration so as to have a reduced diameter, thereby increasing the clearance between the rollers 2 and 3 of pairs 5, 6, 7 and 8 and freeing banknote 4 from it. In contrast, in pairs 9 and 10, the rollers 2 of variable diameter are translated into their expanded configuration to have an increased diameter, as shown in FIG. 2. Thus, the banknote 4 is released from the corresponding rollers 2 and 3 of the pairs 5, 6, 7 and 8 and clamped by the corresponding rollers 2 and 3 of the pairs 9 and 10 to move laterally and make an L-shaped trajectory in the redirection mechanism 1.

In the event that the banknote does not need to change its movement in the longitudinal direction, as shown in FIG. 1 and FIG. 2, the configuration and diameter of the rollers 2 of variable diameter is maintained unchanged, as in the first stage. In this case, the banknote continues to move in the longitudinal direction defined by pairs 5, 6, 7, and 8 until it leaves mechanism 1, for example, into the outlet mechanism or other redirection mechanism.

Figure 3 and figure 4 schematically shows a modified version of the redirection mechanism 1, illustrating the principle of using conveyor belts as a drive means for moving banknotes. In figure 3 and figure 4, the mechanism contains the same pairs of rollers 5-8 and 9, 10, each of which consists of rollers 2 and 3, as in the embodiment shown in figure 1 and figure 2. The longitudinal belt conveyor 11 is located in a row with pairs of 5-8, 9 and 10 rollers. The conveyor 11 has a return span 12 and a bearing span 14. The bearing span 14 of the conveyor 11 is passed through the gap between the rollers 2 and 3 in each of the pairs 5-8. Here, the conveyor belt 11 is used as a drive means for moving banknotes, thus allowing longitudinal movement of the banknote 4 along the longitudinal part of the trajectory defined by the pairs of 5-8 rollers. In this embodiment, the drive means connected to the rollers 2 is omitted, and the variable-diameter rollers 2 are freely rotatable as the support rollers 3. However, in another embodiment, the rollers 2 can still remain driven, and the conveyor belt 11 can be used as an additional drive means to drive rollers 2.

In addition, in the embodiment disclosed with reference to FIGS. 3 and 4, transverse conveyor belts 16, 18 are provided. The conveyor belt 16 comprises a support roller 3 of a pair 9, and the conveyor belt 18 comprises a support roller 3 of a pair 10, the rollers being arranged so the same as the corresponding rollers 3 in figure 1 and figure 2. In addition, the conveyor belt 16 comprises a roller 20 downstream of the support roller 3 of the pair 9, and the conveyor belt 18, furthermore, contains the roller 22 downstream of the support roller 3 of the pair 10. The rollers 20 and 22 can be drive rollers. The tape 24 of the conveyor belt 16 surrounds the support roller 3 of the transversely arranged pair 9 and the roller 20, and the tape 23 of the conveyor belt 18 surrounds the support roller 3 of the transversely arranged pair 19 and roller 22, respectively.

Pairs of rollers 9 and 10, which form the rest of the motion path or the transverse part of the motion path, are located across the upstream pair of rollers 5. The pairs of 9 and 10 rollers are axially spaced from each other, that is, are located at a distance between each other along the longitudinal part of the trajectory defined by pairs 5, 6, 7 and 8.

In figure 3, the rollers 2 of variable diameter pairs 5, 6, 7 and 8 are in their expanded configuration and have an increased diameter, so that the gap between the rollers 2 and 3 pairs 5, 6, 7 and 8 is minimized to provide a clamp, like banknotes 4, and the carrier span 14 of the conveyor belt 11. The conveyor 11 is moving; therefore, the clamped banknote is carried along the trajectory, sequentially guided by pairs of 5, 6, 7 and 8 rollers and the conveyor 11. In the process, the banknote 4 enters the redirection mechanism 1, for example, comes from the upstream mechanism in the banknote manipulation machine. For specialists it should be obvious that the redirection mechanism 1 may contain appropriate guide means for guiding the incoming banknote into the gap between the rollers 2 and 3 of the pair 5. Conveyor belt 11 can also be used as such a guide means. In the first “longitudinal” stage shown in FIG. 3, the rollers 2 of variable diameter pairs 5, 6, 7 and 8 are in their expanded configuration and have an increased diameter, so that the gap between the rollers 2 and 3 of pairs 5, 6, 7 and 8 is minimized to enable clamping of the banknote 4 together with the conveyor 11. The front end of the banknote 4 is inserted into the gap between the carrier span 14 of the conveyor 11 and the rotating roller 3 of the pair 5. In this position, the front end of the banknote 4 is clamped and carried downstream by the conveyor 11 and the roller 3 pairs 5 and then sequentially by conveyor 1 1 and roller 3 pairs 6, 7 and 8. In figure 3, the banknote 4 is shown in the position where its front end passed all pairs 5-8 along the longitudinal part of the trajectory of movement, just before the start of the next stage.

In the next “transverse" stage shown in Fig. 4, the rollers 2 of variable diameter of pairs 5, 6, 7 and 8 are transferred to their reduced configuration in order to have a reduced diameter, thereby increasing the gap between the rollers 2 and 3 and freeing the banknote 4 from the space between the conveyor 11 and the rollers 3 pairs 5, 6, 7 and 8. In contrast, in pairs 9 and 10, the rollers 2 of variable diameter are translated into their expanded configuration to have an enlarged diameter, as shown in FIG. 4.

Figure 4 shows that the gaps between the rollers 2 and 3 of the pairs 9 and 10 are minimized to ensure that the banknote 4 is clamped laterally and frictionally mesh with the bearing spans of the conveyors 16 and 18, respectively. Cross conveyor belts 16, 18 are moving; therefore, the clamped banknote moves laterally, thus making a movement along the L-shaped path in the redirection mechanism 1.

5 is a schematic side view, a top view, and an end view of an exemplary embodiment of a switching mechanism 25 used to selectively direct a sheet, such as a banknote 4, into one of two transport directions. The switching mechanism 25 can be integrated into a machine for manipulating banknotes (not shown in the drawings), for example, following a sensor (not shown) for analyzing banknotes. The switching mechanism 25 includes at least one pair of rollers 26 and 27, made so that the banknote 4 can be filed between the rollers 26 and 27 in pairs. In addition, the switching mechanism 25 includes at least one separation element 28 located downstream of the pair of guide rollers 26 and 27. As an advantage, the separation elements 28 are stationary. The spacer element 28 has two guide sides 29 and 30, with each side defining one of the conveying directions. One direction of transportation is defined by the side 29 of the separation element 28. During operation, the receiving surface 31 of the side 29 of the separation element is located tangentially on the path of the incoming banknote 4, tilted upward by a pair of rollers 26 and 27, so that the banknote engages in a guide mesh with the separation element 28 and then goes its guide surface 32 next to the receiving surface 31 on the side 29, in the first direction of transportation, as seen in the side view in figure 5. The other direction of transportation is set by the side 30 of the separation element 28. During operation, the receiving side 33 on the side 30 of the separation element is located tangentially in the path of the incoming banknote 4, which is deflected downward by a pair of rollers 26 and 27, so that the banknote enters into the guide engagement with the separation element 28 and further is guided by its guide surface 34, following the receiving surface 33 on the side 30, in the other direction of transportation. The guiding surface 32 following the receiving surface 31 and the guiding surface 34 following the receiving surface 33 are of a length and shape that are adapted to fit the conveying portions and downstream devices.

A pair of guide rollers 26 and 27 comprises at least one roller 26 of variable diameter. The guide rollers 26 and 27 and the separation element 28 are made to deflect and direct the banknote 4 to the side 30 of the separation element 28 when the diameter of the roller 26 of variable diameter is increased, and to deviate and direct the banknote 4 to the other side 29 of the separation element 28 when the diameter of the roller 26 variable diameter reduced.

As an advantage, the spacer element 28 in the switching mechanism 25 according to the invention has a fixed position, thereby eliminating the need to rotate the spacer element between its positions in a very short time with high accuracy, as described in US 6,547,241 (Yoshida et al.).

As seen from the end view of FIG. 5, the pair of guide rollers 26 and 27 is further provided with an axially spaced pair of guide rollers 26 ′ and 27 ′, which are laterally arranged parallel to the pair of guide rollers 26 and 27, so that the rollers 26 and 26 'are located on the same axis, and the rollers 27 and 27' are located on another of the same axis. Similarly, a pair of feed rollers 35 'and 36' that are laterally parallel to a pair of feed rollers 35 and 36, so that the rollers 35 and 35 'are located on the same axis, and the rollers 36 and 36' are located on the other one and the same same axis. Preferably, the central part of the banknote 4 is located centrally between respective axially spaced pairs of rollers during movement. For the sake of clarity, the rollers 35, 35 'and 36, 36' in the end view are not shown in FIG. 5.

As can be seen from the end view of Fig. 5, the guide roller 26 is connected together with the guide roller 26 'with a continuously operating drive 37. Thus, the guide rollers 26 and 26' are drive rollers, and the guide rollers 27 and 27 'are freely rotating rollers, as a result of which no additional drive means is required to move the banknote 4 along the motion path.

The guide rollers 26 and 26 'are mounted on a fixed axis, while the guide rollers 27 and 27' are mounted on a movable axis and spring loaded relative to the rollers 26 and 26 'on a fixed axis.

6 shows an alternative embodiment of the switching mechanism 25. In this embodiment, both guide rollers 26 and 27 are mounted on different movable axes, the guide roller 27 being spring loaded relative to the guide roller 26, which is spring loaded relative to the holding roller 38 having a fixed axis. Again, as seen from the end view of FIG. 6, the rollers 26, 27 and 38 are further provided with rollers 26 ', 27' and 38 ', which are laterally arranged parallel to the rollers 26, 27 and 38, so that the rollers 26 and 26 'are located on the same axis, rollers 27 and 27' are located on another of the same axis, and rollers 38 and 38 'are located on the third of the same axis. During operation, the receiving surface 31 on the side 29 of the separation element 28 is located tangentially in the path of the incoming banknote 4, directed upward by the spring-loaded rollers 26 and 27, so that the banknote is in the guide engagement with the separation element 28 and then is guided by its guide surface 32 next to the receiving surface 31 on the side 29, in the first direction of transportation "up", as seen in the side view in Fig.6. When the upper guide roller 26 has an enlarged diameter, the banknote 4 is guided in the lower conveying direction defined by the side 30 of the separation element 28. Thus, during operation, the receiving surface 33 on the side 30 of the separation element is tangentially in the path of the incoming banknote 4 deflected downward by the expanded roller 26, so that the banknote engages in guide engagement with the spacer member 28 and is further guided by its guide surface 34 next to the receiving surface 33 on side 30, in the other direction of transportation "down". In this embodiment, the rotational speeds of the rollers 26 and 27 are determined by the rotation of the holding roller 38, which is connected to the continuously operating drive 37 through the roller 38 '. As an advantage, the constant rotation speed of the drive 37 becomes a constant transportation speed of the banknote 4, regardless of the diameter of the roller 26. In addition, the difference between the maximum and minimum diameters of the roller 26, which is necessary to ensure switching of the direction of transportation, is approximately 2 times less shown in figure 5 and figure 7 options.

7 schematically shows a side view, a top view, and an end view of another exemplary embodiment of a switching mechanism 25 used to selectively direct a sheet, such as a banknote 4, into one of two transport directions. In this embodiment, the switching mechanism 25 comprises at least one upper guide roller 26 with a large coefficient of friction and at least one lower guide roller 27 with a large coefficient of friction. The upper freely rotating roller 21 is located next to the upper guide roller 26, preferably on the same axis with it, and above the lower guide roller 27. The lower freely rotating roller 19 is located next to the lower guide roller 27, preferably on the same axis with it, and under the upper guide roller 26. Banknote 4 can be fed between rollers 26 and 19 defining one pair, and between rollers 27 and 21 defining another pair. In addition, the switching mechanism 25 comprises at least one separation element 28 located downstream of the guide rollers 26 and 27 and the freely rotating rollers 19 and 21. Like the embodiment disclosed with reference to FIG. 5, the separation element 28 has two guides sides 29 and 30, with each side defining one of the transportation directions. One transport direction is defined by the side 29 of the separation element 28. During operation, the receiving surface 31 on the side 29 of the separation element is located tangentially in the path of the incoming banknote 4, tilted upward by the lower guide roller 27, so that the banknote engages in a guide mesh with the separation element 28 and then goes its guide surface 32 next to the receiving surface 31 on the side 29, in the first direction of transportation, as seen in the side view in Fig.7. The other direction of transportation is set by the side 30 of the separation element 28. During operation, the receiving surface 33 on the side 30 of the separation element is located tangentially in the path of the incoming banknote 4, deflected downward by the upper guide roller 26, so that the banknote engages in a guide mesh with the separation element 28 and then goes its guide surface 34 next to the receiving surface 33 on the side 30, in the other direction of transportation. The guiding surface 32 following the receiving surface 31 and the guiding surface 34 following the receiving surface 33 are of a length and shape that are adapted to fit the conveying portions and downstream devices.

The upper and lower guide rollers 26 and 27 are rollers of variable diameter. The guide rollers 26 and 27, the freely rotating rollers 19 and 21 and the separation element 28 are designed to deflect and direct the banknote 4 to the side 30 of the separation element 28 when the diameter of the roller 26 of variable diameter is increased and the diameter of the roller 27 of variable diameter is reduced, and to reject and the direction of the banknote 4 to the other side 29 of the separation element 28, when the diameter of the roller 26 of variable diameter is reduced, and the diameter of the roller 27 of variable diameter is increased.

As an advantage, the spacer element 28 in the switching mechanism 25 according to the invention has a stationary position, thus eliminating the need to rotate the spacer element between its positions in a very short time with high accuracy, as described in US 6,547,241 (Yoshida et al.).

As can be seen from the end view of Fig. 7, the guide rollers 26 and 27 are further provided with axially spaced guide rollers 26 'and 27', which are laterally arranged parallel to the guide rollers 26 and 27, so that the rollers 26 and 26 'are located on of the same axis, and the rollers 27 and 27 'are located on the other of the same axis. Similarly, the freely rotating rollers 19 and 21 are further provided with axially spaced freely rotating rollers 19 'and 21', which are laterally arranged parallel to the freely rotating rollers 19 and 21, so that the rollers 19 and 19 'are located on the same axis , and the rollers 21 and 21 'are located on another of the same axis. Preferably, the rollers 26, 21, 26 ', 21' are located on the same axis, while the rollers 19, 27, 19 ', 27' are located on the other same axis. Similarly, a pair of feed rollers 35 and 36 are further provided with an axially spaced pair of feed rollers 35 'and 36', which are laterally parallel to the pair of feed rollers 35 and 36, so that the rollers 35 and 35 'are located on the same axis and the rollers 36 and 36 'are located on another of the same axis. Preferably, the central part of the banknote 4 is located centrally between the respective axially spaced rollers during movement. For the sake of clarity, the rollers 35, 35 'and 36, 36' are not shown in the end view of FIG. 7.

In the embodiment disclosed with reference to FIG. 7, the guide rollers 26 and 27 are connected together with the guide rollers 26 'and 27' to the continuously operating drive 37. Thus, the guide rollers 26, 26 ', 27 and 27' function as drive rollers, as a result, to move the banknote 4 along the path, no additional drive means are required, and the drive speed is not required to ensure the same speed of the banknote 4 on any of the sides 29 and 30 of the separation element 28.

FIG. 8 shows yet another embodiment of a switching mechanism 25. In this embodiment, both guide rollers 26 and 27 in a pair are rollers of variable diameter, wherein each roller in a pair is configured to reduce its diameter when the diameter of the other roller in a pair increases, and to increase its diameter when the diameter of the other roller in a pair decreases. Fig. 8 shows a configuration in which the upper guide roller 26 has a reduced diameter and the lower guide roller 27 has an increased diameter, thus guiding the banknote 4 in the upper conveying direction defined by the side 29 of the spacer member 28. During operation, the receiving surface 31 on the side 29 of the separating element is located tangentially in the path of the incoming banknote 4, tilted upward by the expanded roller 27 together with the shortened roller 26, so that the banknote is in the guide engagement with p and the separating element 28 is then guided by its guide surface 32 next to the receiving surface 31 on the side 29 in the first conveying direction, as seen from the side view of FIG. It should be apparent to those skilled in the art that when the upper guide roller 26 has an increased diameter and the lower guide roller 27 has a reduced diameter, the banknote 4 is guided in the lower conveying direction defined by the side 30 of the spacer member 28. Thus, during operation, the receiving surface 33 on the side 30 of the separating element is located tangentially in the path of the incoming banknote 4, tilted down by the expanded roller 26 together with the shortened roller 27, so that the banknote enters the guide the joint with the spacer member 28 is further guided by its guide surface 34 next to the receiving surface 33 on the side 30 in the other transport direction. In this embodiment, the rotational speeds of the rollers 26 and 27 are accordingly coordinated with each other, allowing the transport of banknote 4 at a constant speed. Here, the guide roller 26 is located on the axis of the fixed position and is connected together with the guide roller 26 'with a constantly working drive 37, and the guide roller 27 is located on the other axis of the fixed position and connected with the guide roller 27' with a constantly working drive 39.

FIG. 9 shows an alternative embodiment of the switching mechanism 25. In this embodiment, both guide rollers 26 and 27 in a pair are rollers of variable diameter, wherein each roller in a pair is configured to reduce its diameter when the diameter of the other roller in a pair increases, and to increase its diameter when the diameter of the other roller in a pair decreases. The rollers 26 and 27 in this embodiment can have a constant rotation speed, being made with a small gap between the rollers 26 and 27 and the banknote 4 at any time during operation of the switching mechanism 25, and the banknote 4 is moved by the feed rollers 35 and 36 until until it engages with one of at least two transport sections or devices downstream of the switching mechanism 25. Preferably, the rollers 26 and 27 are configured to have their peripheral speeds no lower than the speed of the banknote 4 in the range of the diameter of the rollers 26 and 27. FIG. 9 shows a configuration in which the upper guide roller 26 has a reduced diameter and the lower guide the roller 27 has an enlarged diameter, thus guiding the banknote 4 in the upper transport direction defined by the side 29 of the separation element 28. During the movement, the banknote 4 is released from the feed rollers 35 and 36 only when the banknote 4 is in zat of prisoners with the downstream areas or mechanisms that transport the banknote 4 further. In Fig. 9, such sections or mechanisms include a pair of transport rollers 15 and 151 and a pair of transport rollers 17 and 171. The rollers 15 and 151 are engaged together along the edge to clamp the incoming banknote 4 in the first or upper direction, as can be seen in Fig. 9 . The rollers 17 and 171 are engaged with each other along the edge to clamp the incoming banknote 4 in the second or lower direction, as can be seen in Fig.9. In operation, the receiving surface 31 on the side 29 of the separating element is located tangentially on the path of the incoming banknote 4, deflected upward by the expanded roller 27, so that the banknote is in guide engagement with the separating element 28 and is guided further by its guide surface 32 next to the receiving surface 31 on side 29, in a first conveying direction, as seen in a side view of FIG. 9. In this case, the banknote 4 is clamped by a pair of transport rollers 15 and 151 before being released from the pair of feed rollers 35 and 36. For specialists it should be obvious that when the upper guide roller 26 has an increased diameter and the lower guide roller 27 has a reduced diameter, with a gap between them, the banknote 4 is clamped by a pair of transport rollers 17 and 171 and is sent in the lower transportation direction defined by the lower side of the separation element 28. Thus, in the process, the receiving surface 33 on the lower one of the separating element is located tangentially on the path of the incoming banknote 4, deflected downward by the expanded roller 26, so that the banknote is in the guide engagement with the separating element 28 and is directed further by its guide surface 34 next to the receiving surface 33 on the side 30, in the other direction of transportation as seen in a side view in Fig.9. In this case, the banknote 4 is clamped by a pair of transport rollers 17 and 171 before being released from the pair of feed rollers 35 and 36. As can be clearly seen from the end view of Fig. 9, the pair of guide rollers 26 and 27 is also provided with an axially spaced pair guide rollers 26 'and 27', which are laterally parallel to the pair of guide rollers 26 and 27, so that the rollers 26 and 26 'are located on the same axis, and the rollers 27 and 27' are located on another of the same axis. Similarly, the pair of feed rollers 35 and 36 is further provided with an axially spaced pair of feed rollers 35 'and 36', which are laterally parallel to the pair of feed rollers 35 and 36, so that the rollers 35 and 35 'are located on the same axis and the rollers 36 and 36 'are located on another of the same axis. Similarly, the pair of transport rollers 15 and 151 is further provided with an axially spaced pair of transport rollers 15 'and 151', which are laterally parallel to the pair of transport rollers 15 and 151, so that the rollers 15 and 15 'are located on the same axis and the rollers 151 and 151 'are located on another of the same axis. Similarly, a pair of transport rollers 17 and 171, in addition, is provided with an axially spaced pair of transport rollers 17 'and 171', which are laterally parallel to the pair of transport rollers 17 and 171, so that the rollers 17 and 17 'are located on the same axis, and the rollers 171 and 171 'are located on another of the same axis. Preferably, the central part of the banknote 4 is located centrally between the respective axially spaced pairs of rollers during movement. For the sake of clarity, the rollers 35, 35 ′ and 36, 36 ′ in the end view are not shown in FIG. 9. Here, the guide roller 26 is mounted on the axis of the fixed position and connected together with the guide roller 26 'with the drive 37 operating at a constant speed, and the guide roller 27 is mounted on the other axis of the fixed position and connected together with the guide roller 27' with the drive 37. The advantage of this an implementation option is to eliminate the speed controller for the rollers.

Figure 10-12 shows a cross section of a roller 26 of variable diameter, which could be used in three configurations in the switching mechanism 25. The variable diameter roller 26 comprises a roller housing 49 with a roller axis 40 and a plurality of three partially overlapping segment elements 41, 42, 43. The segment elements 41, 42, 43 are substantially similar to one another and are made of metal and / or plastic to ensure stable forms and minimization of their wear. Each segment element 41, 42, 43 is arranged to move relative to the axis 40 of the roller by means of a drive mechanism. For the sake of clarity, the drive mechanism is not shown in the figures. The contour of each segment element in this embodiment has two lateral parts 45, 46, each having an arc configuration. The radius of the arc in the lateral portion 45 of the segment element 41 is less than the radius of the arc in the lateral portion 46 of the segment element 41, but larger than the radius of the roller body 49. The drive mechanism is arranged to move each segment element 41, 42, 43 to any of the three positions defined by the three configurations of the roller 26 of variable diameter. In the configuration of the roller 26 shown in FIG. 10, the segment elements 41, 42 and 43 are moved to a position where they are completely inside the edge of the roller body 49, as a result of which the roller 26 has a completely reduced configuration with its minimum diameter d1 given by the diameter of the roller body 49 . In the other configurations of the roller 26 shown in FIGS. 11 and 12, the lateral parts 45 or 46 of the segment elements 41, 42 and 43 having the same radius are moved to a position in which they together form a circular edge of the roller 26 having a corresponding diameter, which is equal to the values of the partially reduced or fully expanded configurations of the roller 26. Figure 11 shows the roller 26 in its partially reduced configuration. As can be seen in FIG. 11, the segment elements 41, 42, 43 of the roller 26 are in a second position, so that the lateral parts 45 of all the segment elements form a circular edge of the roller 26 having an intermediate diameter d2. Thus, the roller 26 of variable diameter is brought into its partially reduced configuration, in which the lateral parts 46 of the segment elements 41, 42, 43 remain within the circular edge of the roller 26. FIG. 12 shows the roller 26 in its fully expanded configuration. To change the configuration of the roller 26, the drive mechanism moves each segment element 41, 42, 43 to their third position, so that the lateral parts 46 of the segment elements form a circular edge of the roller 26 having a maximum diameter d3. Thus, the roller 26 of variable diameter is brought into its expanded configuration, in which the lateral parts 45 of the segment elements 41, 42, 43 remain within the circular edge of the roller 26, as can be seen in Fig. 12.

13-16 show a cross section of another embodiment of a roller 26 of variable diameter that can be used in four configurations in the switching mechanism 25. The roller 26 of variable diameter in this embodiment comprises a roller housing 49 with an axis 40 and a plurality of four partially overlapping segment elements 41, 42, 43 and 44. The segment elements 41, 42, 43 and 44 are substantially similar to one another and are made of metal and / or plastic to ensure a stable shape and minimize wear. Each segment element 41, 42, 43 and 44 is arranged to move relative to the axis 40 of the roller by means of a drive mechanism 48. For the sake of clarity, the drive mechanism is not shown in the figures. The contour of each segment element has three lateral parts 45, 46 and 47, each has an arc configuration. The radius of the arc in the lateral part 45 of the segment element 41 is less than the radius of the arc in the lateral parts 46 and 47 of the segment element 41, but larger than the radius of the roller housing 49, and the radius of the arc in the lateral part 46 of the segment element 41 is less than the radius of the arc in the lateral part 47 of the segment element 41. The drive mechanism is arranged to move each segment element 41, 42, 43, and 44 to any of four positions. In one configuration of the roller 26 shown in FIG. 13, the segment elements 41, 42, 43 and 44 are moved to a position where they are completely within the edge of the roller body 49, whereby the roller 46 has a completely reduced configuration with its minimum diameter d1, a given diameter of the roller housing 49. In the other configurations of the roller 26 shown in FIGS. 14-16, the lateral parts 45, 46 or 47 of the segment elements 41, 42, 43 and 44 having the same corresponding radius are moved to a position in which they together form a circular edge of the roller 26 having the corresponding diameter. On Fig shows the roller 26 in its partially reduced configuration. As can be seen in FIG. 14, the segment elements 41, 42, 43 and 44 of the roller 26 are in such a position that the lateral parts 45 of all the segment elements form a circular edge of the roller 26 having a smaller intermediate diameter d2. Thus, the variable diameter roller 26 is brought into its partially reduced configuration in which the lateral parts 46 and 47 of the segment elements 41, 42, 43 and 44 remain within the circular edge of the roller 26.

On Fig shows the roller 26 in its partially expanded configuration. To change the configuration of the roller 26, the drive mechanism moves each segment element 41, 42, 43 and 44 to their third position, so that the lateral parts 46 of all the segment elements form a circular edge of the roller 26 having a larger intermediate diameter d3. Thus, the roller 26 of variable diameter is brought into its partially expanded configuration, in which the lateral parts 45 and 47 of the segment elements 41, 42, 43 and 44 remain within the circular edge of the roller 26, as can be seen in FIG.

On Fig shows the roller 26 in its fully expanded configuration. To change the configuration of the roller 26, the drive mechanism moves each segment element 41, 42, 43 and 44 to their third position, so that the lateral parts 47 of all the segment elements form a circular edge of the roller 26 having an expanded diameter d4. Thus, the roller 26 of variable diameter is brought into its fully expanded configuration, in which the lateral parts 45 and 46 of the segment elements 41, 42, 43 and 44 remain within the circular edge of the roller 26, as can be seen in Fig.16.

In addition, the drive mechanism is configured to move each segment element 41, 42 and 43 in the roller 26 shown in FIGS. 10-12 between three positions, or each segment element 41, 42, 43 and 44 in the FIGS. 13-16 the roller 26 between four positions, so that the circular surface described around the segment element and concentric with the axis of rotation of the roller changes its radius in such a way that it preserves with a given accuracy the specified clearance to the same surface of the second same roller 27 located in position wherein the circular edge of a roller 26 having a maximum diameter has a predetermined clearance to the circular edge of a second same roller 27 having a minimum diameter. In other words, two rollers in a pair, the axes of which are parallel in parallel at a fixed distance from each other, can change their diameters so that the specified clearance can be maintained at any time between surfaces adjacent to each other.

On figa-17G shows the location of the circular housing 49 of the roller and the possible arrangement of the drive mechanism 48 in the roller 26 of variable diameter. The round roller housing 49 is shown with respect to four different positions of the segment elements 41, 42, 43 and 44, that is, the three extended positions shown in FIGS. 17B-17G, in which the segment elements are radially extended outside the round case 49 to define three different diameters 17A, and shown in FIG. 17A in a fully reduced position in which the segment elements are retracted radially to remain within the edge of the round casing 49 to ensure a minimum diameter of the roller. For clarity, only segment element 41 is shown in FIGS. 17A-17G. The round body 49 is concentric with the axis of rotation of the roller. In the shown embodiment, the drive mechanism 48 comprises fixed position wheels 481, 482 and a movable position wheel 483; the wheel 481 is concentric with the roller casing 49, and the wheels 482 and 483 are radially spaced from each other with respect to the wheel 481. The wheels 481 and 482 are called “fixed position” wheels because their rotation axes do not change their positions relative to each other and the roller casing 49. The wheel 483 of the movable position can rotate around its axis of rotation, which is rotationally mounted relative to the axis of rotation of the wheel 481 of the fixed position. For this purpose, the movable position wheel 483 is rotationally mounted on the movable arm 4831 shown by the dashed line in FIGS. 17A-17G. The lever 4831 is mounted so that it rotates around the wheel 481 within a limited angle. The wheels 481, 482 and 483 and the inner edge of the segment element 41 are specially designed to engage with each other. It should be noted that the arrangement of the wheels can be understood in view of the concept of the planetary gear configuration, because the wheels 481, 482 and 483 are mounted in such a way that, in imagination, they could be shifted into the planetary gear configuration without disengaging from each other . Such a planetary gear configuration would consist of a central gear (wheel 481) and planetary gears (wheels 482 and 483). In a planetary gear configuration, the wheel 481 would remain concentric on the inner edge of the segment element 41, and the axles of the wheels 482 and 483 and the wheels 481 would remain in a common plane. However, in the shown embodiment, the wheels cannot actually be located in the configuration of the planetary gear transmission, because the position of the lever 4831 necessary for this is out of the range of its movement. It should be understood that the configuration of the planetary gear transmission can only be realized if the wheel 483 is disconnected from the lever 4831 without disengaging from other wheels. The concept of planetary gearing is mentioned here only in order to specify the idea of the arrangement of the wheels in mutual engagement.

In the embodiment shown, an engine (not shown) rotates the fixed position wheel 481, which then rotates the fixed position wheel 482, the movable position wheel 483, and the segment member 41 until the segment member 41 reaches any of the three shown in Fig.17B-17G provisions. In addition, the position of the lever 4831 and the wheels 483 of the movable position can be controlled by a separate drive (not shown in the drawings) within a predetermined range between the two end positions. 17A, a lever 4831 and a movable position wheel 483 are shown in a first end position; on figb-17G, the lever 4831 and the wheel 483 of the movable position are shown in the second end position. Preferably, the position of the lever 4831 together with the movable position wheel 483 and the rotation of the wheels 481, 482, 483 and the segment element 41 are controlled to sequentially bring the segment element 41 into one of the four positions shown in FIGS. 17A-17G. In this case, the resulting circular surface described around the segment element 41 and concentric with the roller casing 49 sequentially changes its diameter between any two of the four values d1, d2, d3, d4 defined by the four different positions of the segment element 41 shown in FIGS. 17A-17G according to specified rule. Preferably, the axis of rotation of the wheels 481, 482 and 483 are parallel to each other and the axis of rotation of the roller. Wheels 481, 482, and 483 have corresponding outer annular surfaces configured to mesh with outer annular surfaces of adjacent wheels. Preferably, the wheels 481, 482 and 483 are gears. Here, the annular surface of the fixed position wheel 481 is engaged with the annular surfaces of the fixed position wheel 482 and the movable position wheel 483. The segment element 41 has an inner edge adapted to engage with the outer annular surfaces of the wheels 482 and 483. Preferably, the inner edge of the segment element 41 is an internal gear. Here, the inner edge of the segment element 41 is engaged with the annular surfaces of the fixed position wheel 482 and the movable position wheel 483. In the reduced position of segment element 41 shown in FIG. 17A, the movable position wheel 483 is in the first or “shortened” end position to hold the segment element 41 completely within the edge of the roller body 49. In the three extended positions of the segment element 41 shown in FIGS. 17B-17G, the movable position wheel 483 is moved to the second or “extended” end position to push and hold the segment element 41 extended radially beyond the round casing 49. Thus, the drive mechanism 48 rotates and moves the segment element 41 to sequentially position the lateral portions 45, 46 and 47 of the segment element 41, as explained in detail with reference to FIGS.

FIG. 18 shows yet another embodiment of a switching mechanism 25 comprising another separation element 28 ′ arranged parallel to the first separation element 28 with a gap formed therebetween. The roller 26 of variable diameter is configured to have an intermediate diameter between the enlarged diameter and the reduced diameter. The guide rollers and the separation elements 28 and 28 'are designed to guide the banknote 4 into the gap between the two separation elements 28 and 28', when the diameter of at least one roller of variable diameter is intermediate. Thus, three transportation directions are set in the switching mechanism 25. One direction of transportation "up" is defined by the side 29 of the separation element 28. During operation, the receiving surface 31 on the side 29 of the separation element 28 is located tangentially in the path of the incoming banknote 4, directed upward by the spring-loaded rollers 26 and 27, so that the banknote is in the guide engagement with the separation the element 28 is then guided by its guide surface 32 next to the receiving surface 31 on the side 29, in the first "upper" direction of transportation. The second "middle" direction of transportation is defined by the gap formed between the dividing elements 28 and 28 '. In operation, the incoming banknote 4 follows a substantially straight path defined by the guide surface 34 on the side 30 and the guide side 34 'on the side 30', as seen in Fig. 18. The third downward transport direction is defined by the 29 'side of the spacer member 28'. In operation, the receiving surface 31 'on the side 29' of the separating element is located tangentially in the path of the incoming banknote 4, deflected downward by the expanded roller 26, so that the banknote enters into the guide engagement with the separating element 28 'and then is guided by its guide surface 32' following the receiving surface 31 'on the side 29', in the third "lower" direction of transportation.

In Fig.19 and Fig.20 shows a longitudinal section of another embodiment of a roller 2, 26 of variable diameter, which can be used in the redirection mechanism 1 or the switching mechanism 25. The roller of variable diameter contains a pair of sliding disks 50 and 51 mounted and centered on the axis 40 of the roller and configured to move to each other and from each other in the axial direction by means of a drive mechanism 55 (not shown in Fig. 19 and Fig. 20). The flexible rim member 52 is connected to the sliding disc 50, and the flexible rim member 53 is connected to the sliding disc 51. The flexible rim member 52 extends axially from the sliding disc 50 to the flexible rim member 53, and the flexible rim member 53 extends beyond the sliding disc. 51 in the axial direction to the flexible element 52 of the rim. The flexible elements 52 and 53 of the rim are designed so that moving the sliding disks 50 and 51, respectively, towards each other would press the flexible elements of the rim against each other, thus causing a radial expansion of the flexible elements of the rim and as a result leading to an expanded configuration of a roller of variable diameter as shown in FIG.

In addition, the roller 2, 26 of variable diameter contains a roller casing 54 in which a pair of sliding disks 50 and 51 are placed. The edge of the roller casing 54 has two rims 56 and 57 arranged so that between them there is an annular gap 58 open in the radial direction. As can be seen in FIGS. 19 and 20, the flexible elements 52 and 53 of the rim have a bell shape and are located so that they abut one another along the edge and together can pass through the annular gap 58 when the flexible elements 52 and 53 radially expand rim as they move toward each other.

In addition, the roller 2, 26 of variable diameter may include a guide element 59 located between the flexible elements 52 and 53 of the rim to facilitate the conversion of axial deformation of the flexible elements of the rim into their radial expansion and to further facilitate the direction of the flexible elements of the rim through the annular gap 58.

In an unmounted configuration, each flexible rim member 52, 53 is in the form of a flat ring having an inner diameter and an outer diameter. The inner diameter of this ring is smaller than the diameter of the seat 60, 61 on the sliding disk 50, 51 for receiving the flexible element 52, 53 of the rim, respectively.

A fluid channel is provided coaxially with the roller axis 40. One end of the channel is connected to a source of pressurized fluid; the second end of the channel is located inside the roller. At least two openings are provided through the second end of the channel. To bring the roller of variable diameter into an expanded configuration, the liquid is pumped, for example, by means of a pump, through openings into the spaces 62 and 63 between the inner walls of the roller casing 54 and the walls of the sliding discs 50 and 51 facing the adjacent inner walls of the roller casing 54, as shown arrows in FIG. The injected fluid causes the sliding disks 50 and 51 to move towards each other along the axis 40 of the roller, thus causing a radial expansion of the flexible elements 52 and 53 of the rim and as a result leading to an expanded configuration of the roller of variable diameter. Removing fluid from spaces 62 and 63, for example, by a pump, causes the sliding disks 50 and 51 to move apart along the axis 40 of the roller, thereby causing a radial contraction of the flexible elements 52 and 53 of the rim and resulting in a reduced configuration of the roller of variable diameter.

On Fig and 22 shows a longitudinal section of another variant implementation of the roller 2, 26 of variable diameter, which can be used in the redirection mechanism 1 or the switching mechanism 25. A roller of variable diameter in this embodiment is generally similar to that disclosed with reference to FIG. 19 and FIG. 20. However, it is characterized in that its drive mechanism comprises an axial plunger 55 passing through the roller housing 54. In this embodiment, the sliding disks 50 and 51 and the axial plunger 55 are connected to a link mechanism 64 configured to convert the reciprocating movement of the axial plunger 55 into moving the sliding disks 50 and 51, either to each other or from each other, thus causing, respectively, radial expansion or radial contraction of the flexible elements 52 and 53 of the rim and as a result leading, respectively, to the expanded or reduced configuration of the roller of variable diameter.

On Fig and Fig shows a longitudinal section of another embodiment of a roller 2, 26 of variable diameter, which can be used in the redirection mechanism 1 or the switching mechanism 25. Here, the drive mechanism comprises a central component 65 rotationally connected to the roller housing 54. The Central part 65 is made in the form of a rod extending along the axis of rotation of the roller. One end of the central part 65 is located inside the roller housing 54 and has two threaded parts 67 and 68. The threaded part 67 is for the sliding disc 50, and the threaded part 68 is for the sliding disc 51. One of the threaded parts 67 and 68 has a right-hand thread, and the other part has left-hand thread. Each sliding disk 50 and 51 is connected to the Central part 65 by means of means 66, made to convert the rotation of the Central part in the movement of the sliding disks, either to each other or from each other. For this purpose, the tool 66 is made in the form of internal threaded parts of the sliding disks 50 and 51. These internal threaded parts of the sliding disks are located along the axis of rotation of the roller and are engaged with the threaded parts 67 and 68 of the rod. Rotation of the rod in one direction moves the sliding discs 50 and 51 towards each other, thus causing a radial expansion of the flexible elements 52 and 53 of the rim and as a result leading to an expanded configuration of a roller of variable diameter. Rotating the rod in the other direction moves the sliding discs 50 and 51 apart, thereby causing a radial contraction of the flexible elements 52 and 53 of the rim and resulting in a reduced configuration of a roller of variable diameter.

Figures 25-32 illustrate yet another idea for the implementation of a roller 2, 26 of variable diameter, which can be used in the redirection mechanism 1 or the switching mechanism 25. 25, 27, 29, 31 respectively show a roller 2, 26 of variable diameter in an expanded configuration; 26, 28, 30, 32 respectively show a roller 2, 26 of variable diameter in an abbreviated configuration. The variable diameter roller comprises a roller housing 54 and a segmented rim 69. The segmented rim 69 is defined by a plurality of rim segments 71. Each of the rim segments is movably mounted on the roller housing 54. In addition, the roller of variable diameter contains a Central part 70 mounted centrally relative to the housing 54 of the roller.

The central part 70 is arranged to move between at least two positions when displaced by a drive mechanism (not shown in the drawings). The rim segments 71 respectively mesh with the central part 70 in such a way that the movement of the central part is converted to at least the radial movement of the rim segments 71, thereby resulting in a reduced or expanded configuration of a roller of variable diameter.

On Fig and Fig shows a cross section of an embodiment of a roller 2, 26 of variable diameter, characterized in that the Central part 70 is configured to rotate at least between two positions. The central part 70 is located coaxially in the roller housing 54 and has eccentric pivot points 72 spaced around the circumference. In addition, the roller 2, 26 of variable diameter contains levers 73 having their pivot points 75, spaced around the circumference on the housing 54 of the roller. The lever 73 has an inner shoulder 78 and an outer shoulder 77 located around the pivot point 75. Each lever 73 comprises a corresponding rim segment 71 located on the outer shoulder 77 of the lever 73 so as not to interfere with adjacent levers 73 when turning around pivot points 75. The engagement between the segments of the rim 71 and the central part 70 is carried out by rods 74. In each rod 74, one end is pivotally connected to the inner arm 78 of the corresponding lever 73, and the other end is respectively connected to the corresponding pivot point 72 of the central part 70.

When turning counterclockwise to the second position, as shown in FIG. 26 with a large dashed arrow, the central part 70 pulls the rods 74 into the roller housing 54. Therefore, the rods 74 pull the inner shoulders 78 of the levers 73, thus causing the levers 73 to rotate clockwise around their pivot points 75, as shown in FIG. 26 with a small dashed arrow, which results in radial expansion of the outer arms 77 and segments 71 rim.

When turning clockwise to the first position, the central part 70 pushes the rod 74 radially outward. Therefore, the rods 74 push the inner shoulders 78 of the levers 73, thereby causing counter-clockwise rotation of the levers 73 around their pivot points 75, which results in a radial contraction of the outer arms 77 and rim segments 71.

On Fig and Fig shows a cross section of another embodiment of a roller 2, 26 of variable diameter, in which the Central part 70 is made with the possibility of rotation at least between two positions. The central part 70 is coaxially located in the roller housing 54 and has eccentric pivot points 72 spaced around the circumference. Roller 2, 26 of variable diameter in this embodiment is characterized in that, in addition, it contains plungers 79 made with the possibility of reciprocating radially relative to the housing 54 of the roller to the Central part 70 or from the Central part 70. Each plunger 79 is connected to a corresponding segment 71 rims to allow radial movement of the rim segment 71. The engagement between the plungers 79 and the central part 70 is carried out by rods 74. In each rod 74, one end is pivotally connected to the corresponding plunger 79, and the other end is respectively connected to the corresponding pivot point 75 of the central part 70. When turned counterclockwise to the first position, as shown in Fig. 27 with a dashed arrow, the central part 70 pulls the rod 74 into the roller housing 54. Therefore, rods 74 pull the plungers 79 radially toward the central part 70 to move them inward, thereby resulting in a reduced configuration of a roller of variable diameter.

When turning clockwise to the second position, the central part pushes the rod 74 radially outward. Therefore, the rods 74 push the plungers 79 radially from the central part 70 to move them outward, thereby resulting in an expanded configuration of a roller of variable diameter.

In Fig.29 and Fig.30 shows a cross section of another embodiment of a roller 2, 26 of variable diameter, characterized in that the Central part 70 is made in the form of a gear or gear. Each rim segment 71 is pivotally mounted on the roller body 54 and is provided with teeth that engage with the teeth of the central part 70. The roller shown in FIGS. 29 and 30 contains six identical rim segments 71. Each rim segment 71 has a profile shape of the letter “L”. The outer contour of each rim segment 71 has two lateral parts 45, 46, each having an arc configuration. The radius and the length of the arc in the lateral part 45 are less than the radius and the length of the arc in the lateral part 46. One end of the rim segment 71 has teeth, and its axis of rotation is such that the teeth of the rim segment 71 mesh with the teeth of the central part 70. Turn the Central part 70 causes the rotation of each segment 71 of the rim in any of two positions that define two configurations of the roller 2, 26 of variable diameter. In one abbreviated configuration of the roller 2, 26 shown in FIG. 29, the lateral portions 45 of the rim segments 71 having the same radius are moved to the first position to collectively form a circular edge of the variable-diameter roller 2, 26 having a minimum diameter. In a reduced configuration, the lateral parts 46 of the rim segments 71 remain within the circular edge of the roller 2, 26 of variable diameter.

To reconfigure the roller 2, 26, the central part 70 is rotated clockwise, as shown by the larger dashed arrow in FIG. 30, thereby causing each rim segment 71 to rotate to a second position. In this position, the lateral parts 46 collectively form a circular edge of a roller 2, 26 of variable diameter having a maximum diameter. In the second, expanded configuration, the lateral parts of the 45 segments of the rim 71 remain within the circular edge of the roller 2, 26 of variable diameter.

On Fig and Fig. 32 shows a cross section of an embodiment of a roller 2, 26 of variable diameter, characterized in that the central part 70 is made in the form of an axial plunger 80 passing through the housing 54 of the roller, made with the possibility of axial reciprocating motion. Thus, the axial displacement of the plunger 80 leads to the displacement of the Central part 70. In addition, the roller 2, 26 of variable diameter contains radial plungers 81 made with the possibility of radial reciprocating motion relative to the housing 54 of the roller. Each of the radial plungers 81 is connected to the rim segment 71. The engagement between the radial plungers 81 and the central part 70 is carried out by rods 74. In each rod 74, one end is pivotally connected to the corresponding radial plunger 81, and the other end is respectively connected to the corresponding pivot point 72 of the central part 70.

When axially moving in one direction, for example to the right, as shown by a dotted arrow in FIG. 32, the central part 70 pulls the rods 74, which then pull the radial plungers 81 radially inward of the roller body 54, thus causing the rim segments 71 to move radially inward in a shortened configuration of roller 2, 26 of variable diameter.

When axially moving in the other direction, the central part 70 pushes the rods 74, which push the radial plungers 81 radially outward of the roller body 54, thus causing the rim segments 71 to move radially outward into the expanded configuration of the variable diameter roller 2, 26, as shown in FIG. 31 .

LIST OF REFERENCE NUMBERS

one Redirection mechanism 2 Variable Diameter Roller 3 Support roller four Bank note 5 Longitudinally located pair of rollers 6 Longitudinally located pair of rollers 7 Longitudinally located pair of rollers 8 Longitudinally located pair of rollers 9 Cross pair of rollers 10 Cross pair of rollers eleven Longitudinal conveyor belt 12 Return span of the longitudinal conveyor fourteen Span of the longitudinal conveyor 15, 15 ' Top transport rollers for first direction 151, 151 ' Lower transport rollers for the first direction 16 Cross conveyor belt 17, 17 ' Top transport rollers for second direction 171, 171 ' Lower transport rollers for the second direction eighteen Cross conveyor belt 19, 19 ' Lower freely rotating rollers twenty Roller 21, 21 ' Top free rotating rollers 22 Roller 23 Tape 24 Tape 25 Gear mechanism 26, 26 ' Guide rollers 27, 27 ' Guide rollers 28, 28 ' Separator or wedge 29, 29 ' One guide side of the separation element 28, 28 ', respectively

30, 30 ' The other guide side of the separation element 28, 28 ', respectively 31, 31 ' The receiving surface on the side 29, 29 ', respectively, of the separation element 32, 32 ' The guide surface on the side 29, 29 ', respectively, of the separation element 33 The receiving surface on the side 30 of the separation element 34, 34 ' The guide surface on the side 30, 30 ', respectively, of the separation element 35, 35 ' Top feed rollers 36, 36 ' Lower feed rollers 37 Drive unit 38, 38 ' Holding rollers 39 Drive unit 40 Axle roller 41 Segment element 42 Segment element 43 Segment element 44 Segment element 45 One lateral part of a segment element 46 The other lateral part of the segment element 47 The lateral part of the segment element 48 Drive gear 481 Fixed wheel 482 Fixed wheel 483 Rolling wheel 4831 Movable lever 49 Roller housing fifty Sliding disc 51 Sliding disc 52 Flexible rim element 53 Flexible rim element 54 Roller housing

55 Plunger 56 Rim 57 Rim 58 Ring gap 59 Guide element 60 Saddle on a sliding disk 61 Saddle on a sliding disk 62 Space 63 Space 64 Lever mechanism 65 Central part 66 Converting agent 67 Threaded part 68 Threaded part 69 Segmented rim 70 Central part 71 Rim segment 72 Center part pivot point 73 Lever arm 74 Thrust 75 Pivot axis 76 Gap 77 Outer shoulder 78 Inner shoulder 79 Plunger 80 Axial plunger 81 Radial plunger

Claims (26)

1. The redirection mechanism for changing the direction of movement of the sheet containing pairs of rollers, both rollers in each pair being located in the common plane of rotation and having an adjustable gap between them, so that the sheet can be fed through the gap, and the pairs of rollers are arranged in series, each pair sets the direction movement within the path of the sheet,
characterized in that
at least one pair of rollers downstream of the first pair of rollers in the motion path is transverse to the first pair of rollers in the motion path, at least one roller in any pair of rollers is a roller of variable diameter. 2. The redirection mechanism according to claim 1, characterized in that at least one roller in at least one pair of rollers is a drive roller. 3. The redirection mechanism according to claim 1, characterized in that at least one transverse roller in the mechanism is equipped with a similar roller located axially at a distance. 4. The redirection mechanism according to claim 1, characterized in that at least one roller in the mechanism is equipped with a similar roller located axially at a distance. 5. The redirection mechanism according to claim 1, characterized in that the conveyor belt is passed between at least one pair of rollers. 6. The switching mechanism for the selective direction of the sheet in one of at least two directions of transportation, containing at least one pair of guide rollers, made so that the sheet can be fed between the rollers in pairs, and at least one spacer element downstream from at least one pair of guide rollers, wherein at least one spacer element has two sides, each side defining one of the conveying directions,
characterized in that
at least one pair of guide rollers comprises at least one roller of variable diameter, wherein the guide rollers and the separation element are configured to guide the sheet to one side of the separation element when the diameter of the at least one roller of variable diameter is increased, and to direct the sheet to the other side a separating element when the diameter of at least one roller of variable diameter is reduced. 7. The switching mechanism according to claim 6, characterized in that at least one roller in at least one pair of guide rollers is a drive roller. 8. The switching mechanism according to claim 6, characterized in that in each pair of guide rollers, one roller has a fixed axis, the other roller has a movable axis and is spring loaded relative to the fixed axis roller. 9. The switching mechanism according to claim 6, characterized in that in each pair of guide rollers both rollers have movable axes, one guide roller being spring loaded relative to the other guide roller, the latter being spring loaded relative to the holding roller having a fixed axis. 10. The switching mechanism according to claim 6, characterized in that both rollers in each pair of guide rollers are rollers of variable diameter, each roller in a pair configured to reduce its diameter when the diameter of the other roller in the pair increases and increase its diameter, when the diameter of the other roller in the pair decreases. 11. The switching mechanism according to claim 10, characterized in that each roller of variable diameter contains an axis and a plurality of partially overlapping segment elements, each segment element being movable relative to the axis of the roller by means of a drive mechanism, wherein the contour of each segment element has at least two parts, each of which has an arc configuration, the radius of the arc in one part of the segment element being different from the radius of the arc in the other part of the segment element, and the drive anizm movable element of each segment in any of at least two positions, so that in each of at least two parts of segmental positions of elements having the same respective radius together form a circular edge roller having a corresponding diameter. 12. The switching mechanism according to claim 11, characterized in that the drive mechanism, in addition, is arranged to move each segment element between at least two positions so that the circular surface described around the segment element and concentric with the axis of rotation of the roller changes its radius in such a way that with a given accuracy, a gap is maintained relative to the same surface of the second same roller located in a position in which the circular edge of the roller having a maximum diameter has m predetermined gap relative to the circular edge of the same second roller having a minimum diameter. 13. The switching mechanism according to claim 6, characterized in that it has another separation element located parallel to the first with a gap formed between them, and the rollers of variable diameter are made with the possibility of having an intermediate diameter between the increased diameter and the reduced diameter, and the guide rollers and dividing the elements are designed to guide the sheet into the gap between the two spacer elements when the diameter of at least one roller of variable diameter is intermediate. 14. A roller of variable diameter containing a pair of sliding disks mounted and centered on the axis of the roller and configured to move to each other and from each other in the axial direction by means of a drive mechanism,
characterized in that
the flexible element of the rim is connected to each of the sliding disks, each flexible element of the rim extending beyond the sliding disk in the axial direction towards another flexible element of the rim, the flexible elements of the rim being made so that the movement of the sliding disks against each other would compress the flexible elements of the rim to a friend, thus causing a radial expansion of the flexible elements of the rim. 15. A roller according to claim 14, characterized in that it further comprises a roller casing in which a pair of sliding disks is located, wherein the edge of the roller casing has two rims arranged so that they have an annular gap open in the radial direction to each other moreover, the flexible elements of the rim have such a shape and are arranged so that they pass through the annular gap when a radial expansion of the flexible elements of the rim occurs. 16. The roller according to 14, characterized in that the roller further comprises a guide element located between the flexible elements of the rim to facilitate the axial deformation of the flexible elements of the rim in their radial expansion and to facilitate the direction of the flexible elements of the rim through the annular gap. 17. The roller according to 14, characterized in that each flexible element of the rim has the shape of a flat ring, and the inner diameter of the ring is less than the diameter of the saddle on the sliding disk to accommodate the flexible element of the rim. 18. The roller according to claim 15, wherein the drive mechanism comprises an axial plunger passing through the roller body, the sliding disks and the axial plunger being connected to a link mechanism configured to convert the reciprocating movement of the plunger into the movement of the sliding disks. 19. The roller according to claim 15, wherein the drive mechanism comprises a central part rotationally connected to the roller housing, the sliding disks and the central part being connected to means configured to convert the rotation of the central part to moving the sliding disks. 20. A roller of variable diameter comprising a roller casing and a segmented rim, wherein each rim segment is movably mounted on the roller casing,
characterized in that
the roller further comprises a central part mounted centrally relative to the roller housing and configured to move between at least two positions by means of a drive mechanism, the rim segments respectively being engaged with the central part so that the movement of the central part is converted at least least radial movement of rim segments. 21. The roller according to claim 20, characterized in that the central part is rotatable between at least two positions, the central part having eccentric pivot points spaced around the circumference, and the roller further comprises levers having their rotation axes, spaced around the circumference on the roller casing, each lever comprising a rim segment, the engagement between the rim segments and the central part being carried out by rods having their first ends pivotally connected to the shoulders of the respective ychagov, and having their other ends respectively connected with the corresponding points of rotation of the central part. 22. The roller according to claim 20, characterized in that the central part is rotatable between at least two positions, the central part having eccentric pivot points spaced around the circumference, and the roller further comprises plungers configured to radially return translational motion relative to the roller housing, each plunger connected to a rim segment, and the engagement between the plungers and the central part is carried out by rods having their first ends, articulated Din with corresponding plungers, and having their second ends, respectively connected to the corresponding turning points of the Central part. 23. The roller according to claim 20, characterized in that the central part is a gear, each rim segment being rotatably mounted on the roller casing and equipped with teeth that mesh with the teeth of the central part. 24. The roller according to claim 20, characterized in that the Central part is an axial plunger passing through the roller housing and made with the possibility of reciprocating motion, and the roller, in addition, contains made with the possibility of reciprocating motion relative to the roller housing radial plungers moreover, each plunger is connected to the rim segment, and the engagement between the plungers and the Central part is carried out by rods having their first ends, pivotally connected to the corresponding pl nzherami, and having their second ends, respectively connected to the corresponding turning points of the Central part. 25. A roller of variable diameter comprising an axis and a plurality of partially overlapping segment elements, wherein each segment element is movable relative to the axis of the roller by means of a drive mechanism,
characterized in that
the contour of each segment element has at least two parts, each of which has an arc configuration, the radius of the arc in one part of the segment element being different from the radius of the arc in the other part of the segment element, the drive mechanism being configured to move each segment element to any at least of at least two positions, and in each of at least two positions, portions of segment elements having the same corresponding radius together form a circular edge of a roller having a corresponding conductive diameter. 26. The roller according A.25, characterized in that it further comprises a concentric axis of the roller round the housing, and the outer diameter of the housing is less than the diameter of the circular edge of the roller in any specified position of the segment elements, and the drive mechanism, in addition, is made with the possibility of moving each segment element to a position in which the segment element is radially located within the roller casing.

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