EP4059677B1 - Cutting machine with two guide plates for guiding knife and press beams - Google Patents

Description

The invention relates to a cutting machine according to the preamble of claim 1. The material to be cut can be a stack of paper, for example.

Such a cutting machine is, for example, by the GB 566 754 A known.

Today, there are different functional principles for electrically driven cutting machines, both for pressing the cuttings and for driving the cutting knife. Some of these can be assigned to specific machine size groups because they represent the best compromise between function and costs.

The smaller cutting machines occupy a certain special position, since the forces required to actuate the pressing of the cuttings are not as high as in larger machines, so that the operator's muscle strength is often sufficient and no motor support is necessary. These machines are often not production machines that the operator works with all day long. Such machines are typically used in copy shops, for example. Partial or full electrification is often used primarily for increased comfort, since the operator's effort is reduced and work can also be done faster in the long term. Since the segment of small machines is particularly price-sensitive, the focus here is on the manufacturing costs for the respective functional principle and must not be too high in relation to the manual machine variant. Therefore, only simple electrification systems are used here, sometimes only the blade drive is motor-driven. If the clippings pressing device is also driven by a motor, the pressing pressure is generally not adjustable.

Cutting machines of the medium machine group size have a very wide use, starting from the professional copy shop to in-house printers to professional printers. These machines are particularly suitable for small and medium-sized paper formats, which are often used in digital printing processes. For this reason, this medium-sized machine size group has gained in market importance and the required level of professionalism. The market is increasingly demanding equipment features and working speeds that were previously reserved primarily for machines in the large machine size group. However, the equipment features in the medium machine group segment can usually not be realized using the techniques of the large machine group size. Reasons for this are, for example, the size, the complexity and the Price for the realization of the equipment features. Machines in medium-sized machine groups should be able to be operated on the standard secured single-phase power grid, as this is available at almost all desired locations. The energy efficiency of such machines is important for several reasons. One reason is that, as with all electrically operated devices, the required energy consumption should be kept as low as possible from the point of view of environmental protection and operating costs. Another reason is that the desired single-phase domestic installation limits the possible power consumption and thus the performance of the machine. This means that the more energy-efficient the machine works, the more power can be used productively for the actual machine function.

For all machine group sizes described, it is important to implement the functional units for pressing as well as those for cutting the material to be cut in such a way that on the one hand they meet the requirements for stability and precision, which are particularly necessary for a clean cut, and on the other hand they are as efficient as possible in order to to convert the power available from the standard single-phase domestic installation as effectively as possible into a maximum pressing force or a maximum cutting force at the required pressing and cutting speed. Since at the same time a high speed of the pressing/cutting process is desired in the sense of a high working speed with the highest possible pressing and cutting forces, it is not expedient to compensate for a poor efficiency of the pressing/cutting system by means of a slower working speed.

With the functional principles mostly used today, a not inconsiderable part of the energy used is used to overcome the frictional forces in the system. These frictional forces are caused, among other things, by the bearing and guidance of the pressing or cutting unit. It is customary to guide the cutter bar, which supports the cutting blade, in a sliding manner at its two ends between two guide plates, which in turn are partially offset by sliding plates. These guide plates are usually welded to the basic machine construction and are therefore connected as rigidly as possible. In the event of damage to such a guide plate, this makes repairs considerably more difficult or makes them impossible not at all. As an alternative to the system with a total of four guide plates, designs are also known in which the guide of the cutter bar is integrated into a large cast metal frame that extends in a rectangular shape around the entire cutting area. This is helpful for the necessary stability and precision, but increases the overall system costs considerably, does not allow a modular approach for different cutting lengths and, in the event of damage, leads to enormously high repair costs, which are often not economically justifiable. This structural principle is therefore primarily reserved for the very large and very expensive machine group size, since it makes it easier to achieve the necessary rigidity of the overall structure. In the further course, this variant will not be considered further, since it entails the additional disadvantages listed. On the one hand, the sliding guides of the guide plates have to be very precise in order to ensure an exact cut of the material to be cut, on the other hand, there needs to be a certain amount of play between the components sliding towards one another. In order to ensure this in the best possible way, it is usually necessary for the forces required to move the sliding parts to be reduced by lubricating them. At the same time, the lubrication must prevent the sliding surfaces from being destroyed by direct contact between the components. This lubrication must be renewed regularly and is not desirable for reasons of environmental protection, the increased maintenance effort and the risk of contamination of the clippings with excess lubricant.

If, as is generally the case, the knife is to cut the material to be cut with a pulling cut, the knife guide must guide the knife through the material to be cut at an angle (typically 45°) during the downward movement. This is advantageous because a simultaneous horizontal and vertical movement of the knife in relation to the material to be cut during the cutting process leads to better cutting results with reduced cutting forces at the same time. Another important aspect of knife guidance is the required operator safety. In order to minimize the risk of injury, the distance between the knife edge and the press beam arranged directly behind it must be as small as possible. A larger gap carries the risk that the operator could injure himself on the exposed knife edge.

All in all, many cost-intensive components are required for the implementation of the required functions in the hitherto customary designs. As an example here are the four necessary guide plates between which the knife bar is guided (two at each end of the knife bar) and the many additional parts for the implementation of the pressing functionality. In addition to the high production costs of the four necessary guide plates, there are further disadvantages from the previous structures, such as the non-existent or only very difficult to implement adjustment option for the vertical knife alignment in relation to the material to be cut, which is absolutely necessary for an exact cutting result.

In order to achieve the desired pulling cut in the already known machine structure, a motor-driven crank mechanism transmits a tensile force to its connecting rod, which in turn is connected to the cutter bar. During the cut, a downward force acts on the connecting rod and thus on the cutter bar via the crank mechanism. In order to ensure the downward movement of the cutter bar under 45°, the cutter bar must be guided accordingly. For this purpose, so-called guide rails are often additionally attached to the guide plates at the desired angle. In addition, the cutter bar is fitted with appropriate rollers that are forced to roll on the guide rails as it moves up and down. Many additional components are often required for the guidance of the press beam, as well as for the knife guidance, which make the structure complicated, expensive and often also imprecise. If the overall structure of the machine is designed in such a way that abnormal operation, such as the knife jamming due to incorrect depth setting or uncuttable material to be cut, is to be covered, this leads to further disproportionately bulky and therefore expensive machines.

In the cutting machine of the aforementioned GB 566 754 A the cutter bar is mounted in two inclined slotted guides and the press beam in two vertical guides so that it can be adjusted in height. Cutting machines with two inclined slot guides for the cutter bar are also out U.S. 2002/020274 A1 , DE 222 235 C and DE 42 06 338 A1 known. JP 2017 164865 A discloses a cutting machine with an incline-adjustable bottom cutter and a height-adjustable top cutter that interacts with the bottom cutter.

The present invention is therefore based on the object of developing a pressing and knife guide structure which meets the requirements listed above while at the same time largely avoiding the disadvantages.

According to the invention, this object is achieved by a cutting machine having the features of claim 1 .

According to the invention, the number of necessary guide plates is halved from four to two, and the two guide plates that are present not only guide the cutter bars, but also guide the press bars. In order to achieve the desired, pulling cut at the desired angle (e.g. 45°) to the horizontal, the downward force of the cutting drive acting on the cutter bar must be converted into a downward movement of the cutter bar corresponding to the desired angle. For this purpose, the guide plates have the slot guide.

• kostenoptimal durch die Minimierung der für die Gesamtfunktion notwendigen Teileanzahl.
• nur zwei einstückige Führungsplatten notwendig, die alle Führungsaufgaben für die Messer- und Pressbalkenführung übernehmen.
• präzise und leichtgängige Führung der Messer- und Pressbalken durch präzise Führungsflächen, die alle in den beiden einteiligen Führungsplatten vereint sind:
  Erfindungsgemäß weist die Führungseinheit zu beiden Plattenseiten der Führungsplatte jeweils einen Achsträger auf, an dem die Achse befestigt ist. Der Achsträger weist ober- und unterhalb des Langlochs Rollelemente auf, welche außen an der jeweiligen Plattenseite parallel zum Langloch abrollen. Die Führungseinheiten sind funktionell zweitgeteilt und bestehen jeweils aus einer vorderen und einer hinteren Führungsteileinheit. Sowohl an der vorderen wie auch an der hinteren Führungsteileinheit sind Rollen befestigt, welche auf der vorderen bzw. hinteren Plattenseite der Führungsplatte abrollen. Dies ermöglicht ein sehr leichtgängiges Verfahren der Führungseinheiten. Da der Messerbalken direkt mit den beiden Führungseinheiten verbunden ist, lässt sich auch dieser sehr leichtläufig bewegen. Besonders kostengünstig, leichtlaufend und nahezu wartungsfrei lässt sich dies durch den Einsatz von handelsüblichen Radialrillenkugellagern erreichen, die als Rollen dienen. Die Achsträger an der Vorder- und Rückseite der Führungsplatten sind mittels der Achse miteinander verbunden. Die Achsverbindung kann vorteilhaft derart gestaltet sein, dass sich der Abstand der Achsträger zueinander einstellen lässt. Diese Einstellbarkeit erlaubt es, dass sich die Führungseinheiten sehr leicht und exakt, ohne merkliches Spiel zwischen den Führungsplattenseiten, auf die Führungsplattendicke anpassen lassen, so dass eventuelle herstellungsbedingte Dickenschwankungen der Führungsplatten einfach ausgeglichen werden können.

The cutting machine according to the invention offers the following advantages in particular:

• cost-optimized by minimizing the number of parts required for the overall function.
• only two one-piece guide plates are required, which take on all the guiding tasks for guiding the knife and press beam.
• Precise and smooth-running guidance of the knife and press bars through precise guide surfaces, which are all combined in the two one-piece guide plates:
  According to the invention, the guide unit has an axle carrier on each of the two plate sides of the guide plate, to which the axle is fastened. The axle carrier has rolling elements above and below the slot, which roll parallel to the slot on the outside of the respective plate side. The guide units are functionally divided into two and each consist of a front and a rear guide sub-unit. Rollers are fastened both to the front and to the rear guide sub-unit, which roll on the front or rear plate side of the guide plate. This enables the guide units to move very smoothly. Since the cutter bar is directly connected to the two guide units, this can also be very easily adjusted move easily. This can be achieved in a particularly cost-effective, smooth-running and almost maintenance-free manner by using standard radial grooved ball bearings that serve as rollers. The axle carriers on the front and rear of the guide plates are connected to each other by means of the axle. The axle connection can advantageously be designed in such a way that the distance between the axle carriers can be adjusted. This adjustability allows the guide units to be adjusted very easily and precisely to the guide plate thickness without noticeable play between the guide plate sides, so that any production-related thickness fluctuations of the guide plates can be easily compensated for.

According to the invention, the roller axes of the rollers of those two axle carriers to which the cutter bar is attached are slidably mounted in a direction perpendicular to the vertical plane of the two guide plates in order to adjust the inclination of the knife and the gap between the cutter and the press bar. This displaceable mounting of the roller axles can be done in a particularly simple manner by means of a rotatable eccentric sleeve on which the roller is rotatably mounted. In order to be able to ensure the vertical alignment of the cutter bar and thus of the cutter in relation to the material to be cut, the cutter bar fastened to the guide units can be adjusted in its angular position in relation to the guide plates. This is realized, for example, by means of eccentric sleeves, which allow the position of the rollers to be adjusted eccentrically about their central symmetry. This allows the distance between the axle carrier and the guide plate surface on which the rollers rest to be adjusted. If this setting is not made in the same way for the respective upper and lower roller, the result is a change in the angle of the guide unit to the guide plate and thus the desired change in the angle of the blade to the material to be cut. In addition to the adjustment option via the eccentric sleeve on the guide units, the cutting support on which the material to be cut rests can also be adjusted in its angle of inclination, so that here too a simple tolerance compensation of all tolerances to be expected from production is given. The two plate sides of the guide plate preferably have rolling tracks for the rolling elements, for example in the form of guide grooves, above and below the slot, each running parallel to the slot.

The axle particularly preferably has at least one roller, in particular a roller bearing, which rolls in the slot. The elongated hole forms two parallel guide surfaces between which one or more rollers, which are advantageously designed as roller bearings, are arranged and roll. The rollers are received between the front and rear guide sub-units by means of the axle. On the one hand, the axis absorbs the tensile forces that result from the adjustable connection between the associated guide sub-units, but on the other hand, it also absorbs the axial loads that are introduced during the cutting process via the rollers attached to it. The cutter bar fastened to the guide units can therefore only move along the path specified by the parallel guide surfaces of the elongated holes. The main reaction forces that occur when cutting the material to be cut are transferred to the guide plates via the rollers in the elongated holes, which thus serve as a fixed abutment. In the case of a slidably guided axle, the axle can have at least one e.g. specially coated sliding surface element that slides in the slot.

In order to be able to compensate for form errors in the guide plates within the guide surface, a spring pack is also installed on the axle, which is braced when the axle carrier is adjusted and, after the adjustment has been made, still allows a minimal axial movement of the guide sub-units to one another. The spring assembly can, for example, be supported at one end on the axle support and at the other end on one end of the axle.

Particularly preferably, the two guide plates have an opening above or below the slot, for example in the form of a second slot running parallel to the slot. The guide units each have a connecting element, in particular in the form of an axle, which extends through the opening and connects the two axle supports of the guide unit to one another. In order to compensate for form errors in the guide plates within the guide surface a spring pack is also installed on the connecting element, which is braced when the axle carrier is adjusted and, after the adjustment has been made, still allows a minimal axial movement of the guide sub-units to one another.

Since the guide plates for precise knife guidance are constructed precisely and rigidly, it makes sense to use them to guide the press beam as well. For this purpose, the facing faces of the two guide plates have vertical guides, e.g. in the form of longitudinal grooves. The press beam itself forms the counterpart that fits into the guides. In this way, the press beam cannot move further in its longitudinal and transverse directions than the specified play between the guides in the guide plates and the press beam allows. The press beam thus moves exactly along the specified vertical guide grooves.

The cutting drive preferably has an overload safety device in the form of a separable drive connecting rod, the separation of which is monitored electrically.

• Weniger aufwendige und teure Bauteile und damit kostengünstig;
• Präzise Führung von Messerbalken und Pressbalken;
• Leichtgängigkeit des gesamten Systems bestehend aus Messerbalken- und Pressbalkenführung;
• Wartungsarm durch Rollen mit Lebensdauerschmierung;
• Lotrecht einstellbarer Messerbalken;
• Stabile, überlastsichere Ausführung der gesamten Einheit;
• Geringere Gefahr der Schnittgutverschmutzung durch Rollen mit Lebensdauerschmierung;
• Ziehender Schnitt unter einem gewünschten Winkel;
• Sicher zu realisierender, minimaler Spalt zwischen dem Messerbalken und damit dem Messer und dem Pressbalken für eine erhöhte Bedienersicherheit;
• Reparaturfreundlicher Aufbau, der den effektiven Austausch beschädigter Bauteile zulässt.

With the above-described cutting machine according to the invention, all of the requirements mentioned at the outset can be implemented in an optimal manner, viz.

• Less complex and expensive components and therefore inexpensive;
• Precise guidance of cutter bar and press bar;
• Ease of movement of the entire system consisting of cutter bar and press bar guide;
• Low-maintenance thanks to rollers with lifetime lubrication;
• Vertically adjustable cutter bar;
• Stable, overload-proof design of the entire unit;
• Reduced risk of clippings contamination thanks to lubricated for life rollers;
• Drawing cut at a desired angle;
• Minimum gap that can be safely implemented between the knife bar and thus the knife and the press bar for increased operator safety;
• Repair-friendly design that allows effective replacement of damaged components.

Further advantages of the invention result from the description and the drawing. Likewise, the features mentioned above and those detailed below can be used according to the invention individually or collectively in any combination. The embodiments shown and described are not to be understood as an exhaustive list, but rather have an exemplary character for the description of the invention.

Fign. 1a, 1b

die erfindungsgemäße Schneidemaschine mit einem höhenverfahrbaren Messerbalken und einem höhenverfahrbaren Pressbalken in einer Ansicht von vorne (Fig. 1a) und von hinten (Fig. 1b);

Fig. 2

eine in Fig. 1 gezeigte Führungsplatte mit Führungen für den Messerbalken und den Pressbalken;

Fig. 3

eine horizontale Schnittansicht einer in Fig. 1 gezeigten Führungseinheit für den Messerbalken;

Fig. 4

eine Detailansicht der in Fig. 3 gezeigten Führungseinheit; und

Fig. 5

eine Schnittansicht der Schneidemaschine entsprechend V-V in Fig. 1a.

The invention is illustrated in the drawings and is explained in more detail using an exemplary embodiment. It shows:

Figs. 1a, 1b

the cutting machine according to the invention with a height-adjustable knife beam and a height-adjustable press beam in a view from the front ( Fig. 1a ) and from behind ( Fig. 1b );

2

one inside 1 shown guide plate with guides for the cutter bar and the press bar;

3

a horizontal sectional view of a in 1 shown guide unit for the cutter bar;

4

a detailed view of the in 3 shown guide unit; and

figure 5

a sectional view of the cutting machine according to VV in Fig. 1a .

In the Figs. 1a, 1b The cutting machine 1 shown comprises a cutting support 2 for the cuttings to be cut, a cutter bar 3 that can be moved vertically (here diagonally downwards) and carries a cutting blade 4 for cutting the cuttings lying on it, a press beam 5 that can be moved in height to press down the cuttings to be cut, and a cutting drive 6 for Vertical displacement of the cutter bar 3 and a press drive 7 for vertical displacement of the press beam 5. The two drives 6, 7 can each be manually operated or electrically driven.

The cutting machine 1 has a sandwich design and has a machine base body made of two vertical base plates 8 between which two lateral guide plates 9 , which are preferably identical in construction, are fastened by means of screw connections. The two guide plates 9 are arranged parallel to one another in the same vertical plane and, as in 2 is shown in detail, in each case a first linear slot 10 , for example inclined at 45°, in which the cutter bar 3 is guided, and on their mutually facing end faces a vertical guide 11 in which the press bar 5 is guided. In addition, the guide plates 9 below the first elongated hole 10 each have a second inclined linear elongated hole 12 running parallel to the first elongated hole 10 .

The cutter bar 3 is guided in each of the two first elongated holes 10 by means of a guide unit 13 . As in 3 shown, the guide unit 13 has a first axis 14 passing through the first slot 10 with a roller bearing 15 which rolls in the slot guide 10 and a second axis 16 passing through the second slot 12 . On both plate sides 9a, 9b of the guide plate 9, the guide unit 13 has an axle carrier 17a, 17b , to which the axle ends of the first and second axles 14, 16 are fastened. At the two in Fig. 1a The cutter bar 3 is fastened to the front axle carriers 17a, both clamped by means of the first axle 13 and screwed on by means of a screw 18 . The first and the second axle 14, 16 are supported at one end on the cutter bar 3 or on the front axle carrier 17a and at the other end are supported by means of a spring assembly 19 on the rear axle carrier 17b.

The axle supports 17 each have a roller 20 (e.g. in the form of a radial deep groove ball bearing) above the first slot 10 and below the lower slot 12, which roll on the respective plate side 9a, 9b of the guide plate 9 parallel to the first slot 10, specifically on a roller tracks 21 incorporated into the plate sides 9a, 9b. As in 4 shown, the rollers 20 are rotatably mounted on an eccentric sleeve 22 which is screwed to an inclined surface 23 of the axle support 17 by means of a screw 24 . As a result, the distance between the axle carrier 17 and the surface of the guide plate on which the rollers 20 rest can be adjusted. This setting is used for the upper and lower rolls respectively 20 is not carried out in the same way, there is both a change in the angle of the guide unit 13 to the guide plate 9 and thus a desired vertical change in the angle of the knife 4 to the material to be cut, as well as a desired gap distance X between the knife 4 and the press beam 5 ( figure 5 ).

In order to achieve the desired, pulling cut at the desired angle, the downward force of the drive connecting rod acting on cutter bar 3 must be converted into a downward movement of the cutter bar corresponding to the desired angle (45°).

The cutting drive 6 has a motor-driven crank drive 25 in order to transmit a tensile force to a drive connecting rod 26 which in turn is connected to the cutter bar 3 . During the cut, a downward tensile force acts on the drive connecting rod 26 and thus on the cutter bar 3 via the crank drive 25 . A corresponding overload protection 27 is installed so that the machine structure does not have to be dimensioned larger than is necessary for the intended cutting function. This overload protection 27 is part of the drive connecting rod 26. If, due to incorrect operation or other reasons, the blade movement is abruptly blocked and extreme load peaks occur in the entire machine structure, a replaceable safety part 28 is torn off or sheared off in a defined manner. This safety part 28 connects the two halves of the connecting rod, which are each connected at their end points to the cutter bar 3 and the crank mechanism 25, respectively.

In addition, the mechanics are designed in such a way that the drive connecting rod 26 can move apart a little and thus lengthen after the overload protection device 27 has been triggered and thus after the safety part 28 has been destroyed, but it does not separate completely and the knife 4 can therefore move back into its defined safe end position . The fact that the drive connecting rod 26 can lengthen when the safety part 28 is destroyed means that the knife blocking no longer has any further influence on the ongoing movement cycle. After responding, the cutting drive 6 and thus the entire system continue to run without load until the crank mechanism 25 drives the cutter bar 3 as intended via the drive connecting rod 26 in has moved on to the safe upper end position. During the second half of the cutting cycle, ie when returning to the end position, the drive connecting rod 26 is loaded in compression instead of in tension. In the pressure direction, the length of the connecting rod, consisting of the separate halves of the connecting rod, is unchanged even after the overload protection device 27 has responded, which means that the system behaves the same in return with and without an activated overload protection device 27 .

The response of the overload protection 27 and thus also the destroyed safety part 28 should be recognized immediately and not only in the next cutting cycle, in that the material to be cut is not cut, since the drive connecting rod 26 can no longer transmit tensile forces. For this purpose, in the event of an overload, an electrical connection is torn parallel to the mechanical safety part 28, which can be realized, for example, in the form of an electrical monitoring part (eg printed circuit board) 29 , which, like the safety part 28, is destroyed. As a result, a circuit is interrupted, this signal change is recognized by the machine control immediately after the overload has occurred, and the machine does not allow any further cutting cycles after the current cutting cycle has ended. In order to get the machine ready for operation again, the operator must replace the destroyed safety part 28 and the monitoring part 29, which has also been destroyed. The mechanical safety part 28 can also form the electrical monitoring part 29 at the same time. The electrical monitoring can also be carried out by means of a switch, but by means of mechanical destruction, a very high level of functional reliability can be achieved at low costs at the same time.

The press beam 5 should lower itself vertically onto the cut material and fix it in the desired manner so that a clean cut can then be made. For this purpose, a force directed downwards acts on the press beam 5 and is provided by the press drive 7 . As in the present case, this can be done by a motor that pivots a synchronous shaft 30 about its longitudinal axis by a maximum of 180° via a mechanical and/or hydraulic unit. Extension arms 31 are attached to the ends of the synchronizing shaft 30 and are articulated at their outer end to connecting levers 32 which in turn are articulated to the press beam 5 . Now rotates the synchronizing shaft 30, the arms 31 pivot in the same way about the longitudinal axis of the synchronizing shaft 30. At the beginning of the pressing process, the arms 31 and thus the press beam 5 are in an upper position. During the pressing process, the synchronizing shaft 30 rotates in such a way that the arms 31 and with them the press beam 5 connected via the connecting lever 32 move into a lower position. The lowest position is reached when the press beam 5 is seated on the cutting material or, if no such material is inserted, on the cutting support 2. If a torque continues to be applied to the synchronizing shaft 30, this is converted into the desired pressing force, which acts on the material to be cut. In addition to subjecting the press beam 5 to the necessary force directed downwards, it must be moved vertically downwards, parallel to the cutter beam 3 . It is very important here that this is done with a very small distance X between the press beam 5 and the blade 4 . The need for this arises from the already mentioned problem that if the distance is too great, there is a potential risk of injury for the operator on the free-standing knife blade. The blade must therefore be covered by the press beam 5 directly behind it outside of the actual cutting process, which is monitored for safety reasons. However, the protective effect only develops optimally if the gap X between the press beam 5 and the knife 4 is very small and the press beam 5 also protrudes slightly over the edge of the knife. Exact, vertical guidance is necessary for the correct pressing of the clippings, which must not be exposed to any lateral forces during the pressing process, as this could cause the stack of clippings to slip and thus lead to an unwanted cutting result.

Since both the cutter bar 3 and the press bar 5 are mounted on the same guide plates 9, there are no additional tolerances to be taken into account for other components that could negatively influence the precise guidance of the cutter bar 3 and press bar 5 and their distance from one another.

Claims (9)

1. Cutting machine (1) comprising a cutting support (2) for material to be cut, a vertically movable, horizontal blade bar (3) which bears a blade (4) for cutting the cut material located thereon, a vertically movable, horizontal clamping bar (5) for pushing down the material to be cut, and two guide plates (9) which are arranged adjacent to one another, spaced apart in parallel in the same vertical plane, and which in each case have an inclined linear slot (10) in which the blade bar (3) is guided, and on the front faces thereof facing one another in each case have a vertical guide (11) on which the clamping bar (5) is guided, wherein the blade bar (3) is guided in the slots (10) of the two guide plates (9), in each case by means of a guide unit (13) which has an axle (14) which is guided so as to be able to roll or slide in the slot (10), and wherein the guide unit (13) has on both plate sides (9a, 9b) of the guide plate (9) in each case an axle carrier (17a, 17b) on which the axle (14) is fastened,

   characterized in that

   the axle carrier (17a, 17b) has, above and below the slot (10), rolling elements (20) which roll outside on the respective plate side (9a, 9b) parallel to the slot (10),

   the rolling elements are configured as rollers (20), in particular radial deep groove ball bearings, which roll outside on the plate side (9a, 9b) of the guide plate (9), and

   the roller axles of the rollers (20) of those two axle carriers (17a) to which the blade bar (3) is fastened are displaceably mounted in a direction at right angles to the vertical plane of the two guide plates (9), in order to adjust the inclination of the blade (4) and the gap distance (X) between the blade (4) and the clamping bar (5).
2. Cutting machine according to claim 1, characterized in that the axle (14) has at least one roller, in particular a rolling bearing (15), which rolls in the slot (10), or at least one sliding surface element which slides in the slot (10).
3. Cutting machine according to claim 1 or 2, characterized in that the displaceable bearing of the roller axles is formed in each case by a rotatable eccentric sleeve (24), the roller (20) being rotatably mounted thereon.
4. Cutting machine according to one of the preceding claims, characterized in that the two plate sides (9a, 9b) of the guide plate (9) in each case have raceways (21) for the rolling elements (20) running above and below the slot (10), in each case parallel to the slot (10).
5. Cutting machine according to one of the preceding claims, characterized in that at least one of the two axle ends of the axle (14) is fastened on the axle carrier (17b) by means of a spring assembly (19) which is supported at one end on the axle carrier (17b) and at the other end at the axle end.
6. Cutting machine according to one of the preceding claims, characterized in that the two guide plates (9) above or below the slot (10) have a through-hole (12) and the guide units (13) have in each case a connecting element (16), in particular in the form of an axle, which penetrates the through-hole (12) and connects together the two axle carriers (17a, 17b) of the guide unit (13).
7. Cutting machine according to claim 6, characterized in that the through-hole (12) is formed by a second slot (12) running parallel to the slot (10).
8. Cutting machine according to claim 6 or 7, characterized in that at least one of the two ends of the connecting element (16) is fastened to the axle carrier (17b) by means of a spring assembly (19) which is supported at one end on the axle carrier (17b) and at the other end on the end of the connecting element (16).
9. Cutting machine according to one of the preceding claims, characterized in that the vertical guides (11) of the clamping bar (5) are configured in each case as a guide groove in which the clamping bar (5) is guided.

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