EP3243617B1 - Cutting machine - Google Patents

Description

The invention relates to a cutting machine for batchwise cutting of sheet-like material, with a lowerable to the estate pressing beam, the pressing beam is mounted vertically displaceably in a machine frame and means are provided for lowering the press bar on the estate, as well as acting on the press bars a mechanism, which exerts a force directed against the weight of the press beam force on the pressing beam.

Such a cutting machine usually has an operator side of the cutting machine facing cutting blade, which is movable in the so-called swing cut and cuts through the stack-shaped sheet material when driving the cutting blade. This estate is on a table of the slicer. Immediately adjacent to the cutting blade, seen from the operator side, behind the cutting blade of the pressing bars arranged. This can be lowered to the material to be cut and thus clamps this when cutting between himself and the table.

A cutting machine of the type mentioned is from the EP 0 723 842 A1 known. In this, the means for lowering the press beam on the Good hydraulically acting means, specifically a hydraulic cylinder. This is arranged below and next to the pressing beam. On the side of the press beam engage two parallel tie rods, which are pivotally connected to angle levers, which in turn are pivotally mounted in the machine frame. The other end of the respective angle lever is pivotally connected to a connecting rod, which kinematically coupled so that the two tie rods that a synchronized guide of the press bar is created. One of the angle lever has a function of an actuating arm having a third arm, the free end protrudes into the travel of the piston of the hydraulic cylinder, which is mounted in the machine frame is. When the piston is extended so that the voltage applied to this actuating arm of the hydraulic cylinder adjacent angle lever is pivoted and pivoted due to the rigid unit of the angle lever this total, with the result that this angle lever on the one hand pulls the associated tie rod down, on the other hand its movement on the connecting rod is transferred to the other angle lever that pulls the other associated tie rod down. As a consequence, due to the synchronous movement of the two tie rods, the press beam is pulled down, for example, when cutting the stacked sheet material or for Schnittandeutung. Raised is the pressing beam by the pressure cylinder is relieved of pressure and acting on the one hand on the machine frame, on the other hand indirectly acting on the connecting rod return spring acts on the connecting rod, in the sense that the angle levers are pivoted against the loading direction with activated pressure system. The return spring is designed as a tensile force applying spiral spring. It thus represents the mechanism which exerts a force directed against the weight of the press beam force on the pressing beam.

A disadvantage of this compensation of the weight of the press beam by the spring arrangement, that the spring over the stroke has a changing spring characteristic. If the spring lengthens with increasing lowering movement of the press beam, the applied spring force also changes. In contrast, the weight of the press beam is fixed. The consequence is that the overall force of the press beam and spring assembly system varies over the stroke of the press beam. This is in the normal operation of the cutting machine, but especially in the function of Schnittandeutung disadvantage.

In practice cutting machines have the possibility of indicating the respective cut. For this purpose, the operator of the cutting machine, the press bars are slowly lowered in the direction of the material to be cut, which can be optimally aligned with respect to the cutting plane due to the proximity of the press bar to Schneidgutoberfläche and the parallelism of the lower edge of the press beam leading to the cutting blade. During cut indication, it is usually necessary for the operator to manipulate the stack to be cut under the press beam. To preclude a hazard to the operator, especially in terms of crushing the fingers between the press bars and to be cut Good, the pressing force of the press bar is reduced during the Schnittandeutung. According to valid C-standard 1010, this dynamic pressing force in the cutting-edge mode is maximum 300 N for cutting machines with a working width of up to 160 cm, and greater for cutting machines with a working width 160 cm maximum 500 N. This relatively small, limited pressing force is disadvantageously superimposed by the pressing force discussed above due to change in the spring characteristic. Apart from this, there is a risk that the spring bar falls under its considerable weight on the stack to be cut at a fraction of the spring.

Cutting machines for batchwise cutting of sheet material are also described in the publications DE-PS 913 286 , DE-GM 1 651 344 . DT 26 04 212 A1 and EP 0 584 601 A1 described.

The object of the present invention is to provide an alternative drive of the press beam of the cutting machine in a cutting machine of the type mentioned above, in particular to raise the pressing beam and perform a function of Schnittandeutung the cutting machine can.

The object is achieved by a cutting machine which is designed according to the features of patent claim 1.

In the cutting machine according to the invention is provided, the means for lowering the press bar comprise an electric motor, wherein the electric motor also serves to raise the press bar in its fully raised position.

The electric motor is at least intended to move the pressing beam in the functional state of Schnittandeutung in the cutting machine. Accordingly, the electric motor is used in the Schnittandeutung the lowering of the press beam and also the lifting of the press bar in its upper end position. The lowering of the press beam is done on the aligned good. At most, the press beam can be moved downwards by means of the electric motor so that it contacts the table of the cutting machine.

The electric motor may additionally have the function of lifting the press beam also following the cut of the goods. Immediately before the cut of the material, this is pressed by means of the press beam and thus fixed between the press beam and table, so that a displacement of the material during cutting is excluded. In this pressing process of the press beam much higher forces acting on the pressing beam forces are required. As a rule, these forces are applied via hydraulically acting means, in particular a hydraulic cylinder. In particular, the hydraulically acting means are decoupled from the press beam, since it is only necessary that these means, in particular the hydraulic cylinder, when pressing the Guts immediately before the cut with the press beam interact. All other movements of the press bar, thus those in the Schnittandeutung and also the lifting of the press bar after the cut can be accomplished by means of the electric motor.

Depending on the choice of mechanism which acts on the pressing beam and exerts a force directed against the weight of the press beam force on the pressing beam, the weight of the press beam can be balanced, or almost balanced, which on the one hand for moving the press beam only a small driving force required is, on the other hand, particularly advantageous the function of the Schnittandeutung can be displayed.

If the hydraulically acting means for lowering the press beam on the material are decoupled from the press beam, the hydraulically acting means perform only the function of lowering the press beam for the purpose of clamping the sheet-shaped material during the cut. The other movements, thus in particular the lifting of the press bar after the cut and also the lowering and raising of the press bar during Schnittandeutung can then be accomplished by means of the other drive, in this case the electric motor. Accordingly, this electric motor can be made relatively small in size because it only serves for the movement of the balanced system, which comprises the pressing beam and the mechanism which exerts a force directed against the weighting force of the pressing beam on the pressing beam. Much stronger are the hydraulically acting means interpreted as they generate the pressing force when cutting the sheet-shaped Guts.

It is considered to be particularly advantageous if the deliverable torque of the electric motor for lowering and lifting of the press beam is limited. In particular, the deliverable torque of the electric motor is limited such that a compressible force that can be generated between the press beam and the sheet is either 250 N to 300 N, preferably 280 N to 300 N, in particular 300 N or 450 N to 500 N, preferably 480 N. to 500 N, in particular 500 N. This range of press force takes into account the maximum dynamic pressing force provided for in standard cutting in the cutting-edge mode in cutting machines with a working width of up to 160 cm or a working width of more than 160 cm. By this design of the electric motor for driving the press beam this is both suitable for Schnittandeutungsmodus, as well as dimensioned to lower the press beam, without the action of hydraulic means, or lifting the press beam, further in a one-sided hydraulic cylinder for retracting the piston.

It is considered to be particularly advantageous if the pressing beam can be actuated by means of the electrically or hydraulically acting means via a lever arrangement.

It is further considered to be particularly advantageous if the mechanism acting on the press beam, which exerts the force directed against the weight of the press beam on the press beam, is a counterweight arrangement.

Thus, there is no spring arrangement on the pressing beam, but the counterweight arrangement on the pressing beam, in particular on the lever arrangement on the pressing beam. It is thus possible, depending on the choice of the weight of the counterweight assembly to balance the weight of the press beam or almost balanced, which on the one hand for moving the bar only a small driving force is required, on the other hand, the function of Schnittandeutung is particularly advantageous.

In particular, it is provided that the hydraulically acting means for lowering the press beam are decoupled to the material from the press beam, to the effect that via the hydraulically acting means only the function of lowering the press beam for the purpose of clamping the sheet-shaped Guts is performed during the cut. The other movements, thus in particular the lifting of the press bar after the cut and also the lowering and raising of the press bar during Schnittandeutung can then be accomplished by means of the electric motor.

Preferably, the cutting machine is designed such that the lever arrangement has two lever pivotally mounted in the machine frame. The respective lever is in the region of a first lever arm, in particular in the region of a first lever end, in operative connection with the pressing beam and can be acted upon in the region of a second lever arm by means of the hydraulically acting means. This design is structurally particularly simple and allows a power moderately symmetrical connection of the press bar to the lever assembly.

It is considered particularly expedient if the respective lever in the region of the first lever end is pivotally connected to a rod which is pivotally connected in the region of the end facing away from this lever with the pressing beam in the region of a bearing side of the press beam. With this design, a structurally particularly simple connection of the respective lever to the pressing beam is possible.

Preferably, a single hydraulic cylinder is used, by means of which both levers of the lever arrangement can be acted upon. In particular, the hydraulic cylinder is not connected to the levers and deliverable from below against the lever. This allows an opposite synchronous pivoting of the lever by means of a single hydraulic cylinder.

According to a preferred embodiment, it is provided that the levers are pivotable about parallel axes and in a crossing region of the lever have these support means. A free end of a piston of the hydraulic cylinder can be brought into contact with the support means. The respective support means is formed, for example, as a cylinder ring mounted in the lever, for contacting the curved outer surface of the cylinder ring by means of the piston of the hydraulic cylinder. This cylinder ring can also be rotatably mounted.

The counterweight arrangement acts in particular on the lever arrangement. Here, the lever assembly is acted upon against the weight of the press beam.

The counterweight assembly is in particular designed such that it has counterweights, wherein in each lever at least one counterweight, preferably a counterweight, is mounted. As a result of this design of the arrangement of levers and counterweights, it is possible, with a substantially symmetrical arrangement of the counterweights, to achieve the desired balance or essentially balance of the weight of the press beam.

It is preferably provided that the respective lever cooperates in the region of one end of the lever with the pressing beam and the counterweight is mounted in the lever in the region of the other end of the lever.

The counterweights are pivotally mounted in particular in the levers. Here, the respective counterweight is preferably pivotally connected to a coupling rod which is pivotally connected to a stationary relative to the machine frame bearing part. This ensures that the counterweights can not pivot freely, but on the one hand pivotally connected to the lever, on the other hand pivotally connected to the coupling rods or the stationary bearing parts. Preferably, the moments introduced into the lever arrangement via the pressing beam essentially correspond to the moments introduced into the lever arrangement via the counterweight arrangement, in the opposite direction of the torque. In particular, it is provided that these moments correspond exactly.

Because of this at least largely balanced arrangement of the pressing beam and the counterweight arrangement, the pressing beam can be moved by means of the electric motor in those functions which are not the pressing of the material to cut this in this state, both when lifting and lowering the press beam. The electric motor can therefore be dimensioned relatively weak.

It is considered to be particularly advantageous if drivable adjusting means for synchronous pivoting of the lever arrangement are provided by means of the electric motor. About the electric motor, the adjusting means are actuated, which act synchronously on the lever arrangement, whereby this lever arrangement can act synchronously on the pressing beam in the sense of lifting or lowering of the press beam.

The lever arrangement is thus acted upon by means of the adjusting means for the purpose of lifting and / or lowering of the press beam. This is only not the case when the lever assembly by means of the hydraulically acting means, thus the hydraulic cylinder, is acted upon.

Structurally particularly simple, the movement of the electric motor can take place on the pressing beam, when the adjusting means have a stationary mounted drivable constant velocity shaft, the end with this connected cam pieces, as well as with the cam pieces pivotally connected rods which are pivotally connected to the two levers of the lever assembly having. By connecting the respective rod to the cam piece at a distance from the axis of rotation of the synchronizing shaft, the rotational movement of the synchronizing shaft is converted into a substantially rectilinear adjusting movement of the rod, which leads to the adjusting movement of the pressing beam.

In this embodiment with the synchronizing shaft is provided in particular that the electric motor is mounted stationary, and the electric motor is connected via a transmission to the synchronizing shaft, for the purpose of pivoting the synchronizing shaft by a pitch angle. In particular, by means of the electric motor, a pivoting of the synchronizing shaft by an angle of 60 ° to 90 °. This angle is sufficient to achieve via the rods associated with the cam pieces the required movement of the press bar, between the fully raised position of the press bar and its fully lowered position in which the press bar rests on a table of the cutting machine.

Further features of the invention are set forth in the subclaims, the description of the following drawing of the figures and the figures themselves, wherein it is noted that all features and individual features are essential to the invention.

Fig. 1

eine Frontansicht der Schneidemaschine, somit von der Bedienerseite her gesehen, bei abgenommener Frontabdeckung, die unterhalb des Tisches der Schneidemaschine vorgesehen ist,

Fig. 2

in der Frontansicht gemäß Fig. 1 die die Kinematik des Pressbalkens bewirkenden Teile der Schneidemaschine, veranschaulicht bei vollständig angehobener Stellung des Pressbalkens,

Fig. 3

die Anordnung gemäß Fig. 2, veranschaulicht für die vollständig abgesenkte Stellung des Pressbalkens aufgrund Betätigung mittels eines Elektromotors, bei eingefahrener Stellung eines Kolbens eines Hydraulikzylinders,

Fig. 4

eine Ansicht IV der Anordnung gemäß der Fig. 2 und 3, allerdings bei nicht veranschaulichtem Hydraulikzylinder und in etwa in horizontaler Stellung befindlichen Hebeln der Hebelanordnung,

Fig. 5

die Hebelanordnung, die Gegengewichtanordnung, die Stellmittel und den Elektromotor zum Verstellen der beiden Hebel der Hebelanordnung, in einer räumlichen Darstellung,

Fig. 6

die Anordnung gemäß Fig. 5, aus einer anderen Blickrichtung gesehen.

In the figures, the invention is illustrated by means of an embodiment, without being limited thereto. It shows:

Fig. 1

a front view of the cutting machine, thus seen from the operator side, with the front cover removed, which is provided below the table of the cutting machine,

Fig. 2

in the front view according to Fig. 1 the kinematics of the press beam causing parts of the cutting machine, illustrated with fully raised position of the press bar,

Fig. 3

the arrangement according to Fig. 2 , Illustrated for the fully lowered position of the press bar due to actuation by means of an electric motor, in the retracted position of a piston of a hydraulic cylinder,

Fig. 4

a view IV of the arrangement according to the Fig. 2 and 3 , but with not illustrated hydraulic cylinder and in approximately horizontal position levers of the lever assembly,

Fig. 5

the lever arrangement, the counterweight arrangement, the adjusting means and the electric motor for adjusting the two levers of the lever arrangement, in a three-dimensional representation,

Fig. 6

the arrangement according to Fig. 5 , seen from a different angle.

figure description

The cutting machine 1 is used for cutting stacked sheet material, such as paper, cardboard, foil and the like. In a machine frame 2, a cutting blade 3 and a pressing beam 4 are movably mounted. Here, the cutting blade 3 is movable via a guide in a swing section, thus vertically movable with a superimposed horizontal component. Shown is in Fig. 1 the fully lowered position of the cutting blade 3, in which it penetrates slightly into an inserted into a table 5 of the cutting machine 1 cutting bar. The table 5 has a horizontal table surface 6 for receiving the cut material as well as the cut. The cutting blade 3 is driven by means of a hydraulic unit 7, which is arranged in a lateral region of the cutting machine 1. Seen from the operator side, behind the cutting blade 3, adjoining this, the pressing beam 4 is arranged, which faces away from Pages in guides 8 is mounted vertically movable. These guides 8 are connected to the machine frame 2. The pressing bar 4 can be moved in a plane parallel to the cutting blade 3. In the fully raised position of the cutting blade 3, the pressing bar 4 with its lower pressing surface 50 is at a slightly lower level than the cutting blade 3, so that the pressing bar 4 covers the lower cutting edge 51 of the cutting blade 3. The press bar 4 is used for pressing the stacked material against the table 5 during the cut and is thus lowered during the cut, the lowering of the cutting blade 3 leading to the material to be cut. The press bar 4 also serves the Schnittandeutung.

When the cutting blade 3 is raised and the pressing beam 4 is raised, a passage in the machine frame 2 for receiving the material is formed between the latter and the table 5. Above the cutting blade 3 and the press bar 4, the machine frame 2 is provided with a control and display panel 9. On both sides of the cutting blade 3, the cutting machine 1 above the table safety devices 10 with light barriers. When an operator enters the critical area in front of the cutting blade 3 during the cutting process, light rays of the light barrier are interrupted and the safety devices 10 are triggered, in such a way that the movement of the cutting blade 3 is stopped. The triggering of the cut is done by two-handed operation by means of two arranged in the front of the table 5 operating buttons 11th

The pressing beam 4 can be moved in this cutting machine 1 in two different ways:
Thus, a hydraulic means, which is designed as a hydraulic cylinder 12, is provided. The hydraulic cylinder 12 is used to lower the press bar 4 on the estate to press this during cutting by means of the cutting blade 3 against the table 5 and thus to position the good safe to move. Irrespective of this, an electric motor 13 is provided, by means of which the pressing bar 4 can be moved back into its fully raised position and lowered for the purpose of Schnittandeutung both from the fully raised position on the material to be cut and can be fully raised again from this position. In principle, by means of the electric motor 13, the pressing bar 4 can travel up against the table surface 6.

In detail, a lever arrangement 14 is provided for moving the press bar 4. In this acts a counterweight assembly 15, which acts against the weight G of the pressing beam 4, the lever assembly 14. The lever assembly 14 has two largely identically formed lever 16, 17, which are each pivotable about an axis 18 mounted in the machine frame 2. Each lever 16 and 17 has lever arms 48, 49. The two axes 18 are arranged parallel to one another and oriented perpendicular to the travel planes of cutting blade 3 and pressing beam 4. The respective lever 16 or 17 is pivotally connected to a rod 20 in the region of a lever end 19. In this case, passes through a bolt 21, the lever 16 and 17 and the associated rod 20. In the region of the lower end of the press bar 4, adjacent to the associated guide 8 outside the pressing portion of the press bar 4, the respective rod 20 via a pin 22 pivotally connected to the Press bar 4 connected. In substantially horizontal position of the levers 16, 17, in which the axes 18 and bolts 21 are in one plane, the two rods 20 are arranged parallel to each other.

The respective lever 16 or 17, in the region of the other lever end 23, pivotally receives a counterweight 24 or 25 of the counterweight assembly 15. The respective counterweight 24 or 25 is formed as a metal plate which is mounted in the region of its upper end via a pin 26 pivotally in the associated lever 16 and 17 in the region of the lever end 23. The axes of the bolts 26 are arranged parallel to the axes of the bolts 21.

So that the counterweights 24 and 25 can not swing freely, they are pivotally connected to coupling rods 28 in the region of their lower ends about bolts 27. The bolt 27 facing away from the ends of the coupling rods 28 are pivotally mounted about bolts 29 in lower ends of carriers 30, which are oriented vertically and firmly connected to the machine frame 2, thus stationary.

The respective lever 16 or 17 has, in the region of the lever arm 48 between the axis 18 and the bolt 26, closer to the bolt 26 out, a bolt 31 in which a cylindrical ring 32 axially fixed, is rotatably mounted. These bolts 31 are arranged parallel to the bolts 21 and the axes 18. The cylinder rings 32 are positioned facing each other.

The moments introduced via the pressing bars 4, thus via the two bars 20 into the lever arrangement 14 and thus the two levers 16, 17 correspond essentially to the moments introduced via the counterweight arrangement 15, thus the two counterweights 24, 25 into the lever arrangement, by which means these Moments essentially cancel each other out. Since the rods 20 are arranged vertically in a lowered position of the press beam 4, torque ratios on the levers 16, 17 change because of the respective pivot angle of the respective lever 16 or 17 which is possible from this position about ± 20 ° only slightly. Here, the respective levers 16 and 17 and the counterweight 24 and 25 associated coupling rod 28 are formed as a parallel link. Regardless of the respective position of the press beam 4, this can thus be moved under the action of a relatively small force between its raised and lowered position.

The hydraulic cylinder 12 has a piston 33, which is partially movable out of the housing 34 of the hydraulic cylinder 12, starting from the retracted position, as in Fig. 3 is shown, up to a fully extended position with thus completely lowered press bar 4, in which, based on the representation of Fig. 3 , the piston 33, the two levers 16, 17 associated cylinder rings 32 touches. When the piston 33 is extended, it thus abuts against the cylinder rings 32 and transfers the levers 16, 17 from the raised position of the press beam 4 Fig. 2 in the fully lowered position of the press bar 4 according to Fig. 3 if no cutting material rests on the table and thus the pressing bar 4 is lowered completely on this. If, in contrast, cutting material is located on the table 5, the extending piston 3 can only pivot the levers 16, 17 when it contacts the cylindrical rings 32, as it corresponds to the abutment of the pressing bar 4 on the stack to be cut.

After pressing the material to be cut and completion of the cut by means of the cutting blade 3, it is necessary to raise the pressing bar 4 again. Since the piston 3 rests only on the cylinder rings 32, it is not possible, via the hydraulic cylinder 12, the lever assembly 14 in the region of the bolt 21 to pull down and therefore raise the press beams 4. At most, in the design of the hydraulic cylinder 12 as a double-acting cylinder, the piston 33 can be fully retracted into the housing 34. In principle, the hydraulic cylinder 12 can also be designed to be effective only on one side, to the extent that only the extension of the piston 33 for lowering the press beam 4 is possible. In this case, the piston 33 would have to be transferred into its retracted position in the housing 34 by the external force of the electric motor 13 via the cylinder rings 32.

Details of the cutting machine 1 resulting from the operation of the electric motor 13 are described below.
Thus, adjusting means 35, specifically by means of the electric motor 13 drivable adjusting means 35 for synchronous pivoting of the lever assembly 14 and the two levers 16, 17 are provided. By means of these adjusting means 35, the lever assembly 14, in out of contact with this befindlichem hydraulic cylinder 12, for the purpose of lifting and / or lowering of the press bar 4 acted upon. The adjusting means 35 have a stationary mounted, driven by the electric motor 13 synchronizing shaft 36, two ends connected to this cam pieces 37 and the cam pieces 37 pivotally connected rods 38. The synchronizing shaft 36 is axially fixed in the region of opposite ends in receptacles 39, but rotatably supported, wherein the recording 39 associated with the electric motor 13 is mounted via damping elements 40 in a stationary carrier 41, which is thus connected to the machine frame 2, and the synchronizing shaft 36 is mounted in the region of the other end in a directly attached to the machine frame 2 carrier 42. The two cam pieces 37 are non-rotatably connected to the synchronizing shaft 36 and positioned in a middle stroke position of the press bar 4 with its connection line to the axis of the synchronizing shaft 36 to the connection point of the rods 38 substantially horizontally, with substantially vertical orientation of the rods 38. The rods 38 are in the region of their upper ends pivotally mounted in the associated lever 16 and 17 and there pivotable about 16 connected to the levers 16 and 17 bolts. This bolt is arranged on the respective lever 16 or 17 between the axis 18 and the bolt 21, in each case closer to the axis 18. A pivoting of the synchronizing shaft 36 thus leads to a synchronous opposite pivoting of the two levers 16, 17.

For driving the synchronizing shaft 36, the electric motor 13 is provided, which is a DC motor, which cooperates directly with a worm gear 44. This worm gear 44 is flanged to the electric motor 13 facing receptacle 39. An output shaft of the worm gear 44 passes through this receptacle 39 and is there rotatably connected to a pinion 45 which meshes with teeth 46 of a segment disc 47, which extends over a circular sector of about 80 °. By means of this designed as a servomotor electric motor 13 thus the segment disc 47 and thus the constant wave 36 can pivot about the limited angle of the segment disc 47, which allows the balanced on the counterweight assembly 15 Press bar 4 only with relatively low moment of the electric motor can raise and lower. It is thus an electric motor 13 is used, which can deliver only a relatively small moment.

It is envisaged that the deliverable torque of the electric motor 13 is limited. This is such that a producible pressing force between the press bar 4 and table 5 or pressing bar 4 and to be cut Good is limited. Specifically, in the step of the Schnittandeutung for the case of a cutting machine with a maximum working width of 160 cm, the dynamic pressing force in Schnittandeutungsmodus limited by 300 N or limited at a working width of the cutting machine of greater 160 cm to 500 N.

By means of the electromotive drive of the cutting bar 1 is always raised in this cutting machine and also lowered in the case of Schnittandeutung. Optionally, the electric motor 13 may also be operated to transfer the piston 33 of the hydraulic cylinder 12 back to its retracted position. The hydraulic cylinder 12 is activated only when the material is to be pressed by means of the press bar 4, before it is severed by means of the cutting blade 3.

LIST OF REFERENCE NUMBERS

1

cutting machine

2

machine frame

3

cutting blade

4

pressing bars

5

table

6

table top

7

hydraulic unit

8th

guide

9

Operating and display field

10

safety device

11

actuating button

12

hydraulic cylinders

13

electric motor

14

lever assembly

15

Counterweight assembly

16

lever

17

lever

18

axis

19

lever end

20

pole

21

bolt

22

bolt

23

lever end

24

counterweight

25

counterweight

26

bolt

27

bolt

28

coupling rod

29

bolt

30

carrier

31

bolt

32

cylinder ring

33

piston

34

casing

35

actuating means

36

Synchronizing shaft

37

cam piece

38

pole

39

admission

40

damping element

41

carrier

42

carrier

43

bolt

44

worm gear

45

pinion

46

tooth

47

segment disc

48

lever arm

49

lever arm

50

Press area

51

cutting edge

Claims (15)

1. Cutting machine (1) for cutting sheet material in stacks, having a pressure beam (4) that is lowerable onto the material, wherein the pressure beam (4) is mounted so as to be vertically displaceable in a machine frame (2), and means (12, 13) for lowering the pressure beam (4) onto the material are provided, and a mechanism (15) which exerts a force that is directed counter to the weight of the pressure beam (4) acts on the pressure beam (4), characterized in that the means (12, 13) for lowering the pressure beam comprise an electric motor (13), wherein the pressure beam (4) by means of the electric motor (13) is also transferable to the fully lifted position of said pressure beam (4).
2. Cutting machine according to Claim 1, characterized in that the available torque of the electric motor (13) for lowering and lifting the pressure beam (4) is limited.
3. Cutting machine according to Claim 2, characterized in that the available torque of the electric motor (13) for lowering and lifting the pressure beam (4) is limited in such a manner that a compressive force that can be generated between the pressure beam (4) and the sheet material in the case of a cutting machine having a working width of up to 160 cm is 300 N maximum, and in the case of a cutting machine having a working width of more than 160 cm is 500 N maximum.
4. Cutting machine according to one of Claims 1 to 3, characterized by the electric motor (13) for lowering the pressure beam (4) in the case of a cutting indication, and for lifting the pressure beam (4) to the fully lifted position thereof, and by further means (12) for lowering the pressure beam, said means comprising a hydraulic cylinder (12) for compressing the stacked sheet material by means of the hydraulically lowered pressure beam (4) when cutting the material.
5. Cutting machine according to one of Claims 1 to 3, characterized in that the pressure beam (4) is activatable by means of the electric motor (13) or of the hydraulically acting means (12) by way of a lever assembly (14).
6. Cutting machine according to one of Claims 1 to 5, characterized in that the mechanism (15) that acts on the pressure beam (4) is a counterweight assembly (15).
7. Cutting machine according to either of Claims 5 and 6, characterized in that the counterweight assembly (15) which impinges the lever assembly (14) counter to the weight of the pressure beam (4) acts on the lever assembly (14).
8. Cutting machine according to one of Claims 5 to 7, characterized in that the lever assembly (14) has two levers (16, 17) that are mounted so as to be pivotable in the machine frame (2), wherein the respective lever (16 or 17, respectively) in the region of a (first) lever arm (49), in particular in the region of a (first) lever end (19), is operatively connected to the pressure beam (4), and in the region of another (second) lever arm (48), in particular of another (second) lever end (23), at least one counterweight (24 or 25, respectively) of the counterweight assembly (15) is mounted in the lever (16, 17).
9. Cutting machine according to one of Claims 5 to 8, characterized in that the momentums that are introduced by way of the pressure beam (4) into the lever assembly (14) correspond substantially, in particular correspond exactly, to the momentums that are introduced by way of the counterweight assembly (15) into the lever assembly (14), the directions of the momentums being opposed.
10. Cutting machine according to either of Claims 8 and 9, characterized in that the respective lever (16 or 17, respectively) in the region of the first lever end (19) is pivotably connected to a rod (20) which in the region of the end that faces away from said lever (16 or 17, respectively) is pivotably connected to the pressure beam (4) in the region of a bearing side of the pressure beam (4) .
11. Cutting machine according to one of Claims 5 to 10, characterized in that actuation means (35) that are drivable by the electric motor (13) are provided for the synchronous pivoting of the lever assembly (14), in particular for the synchronous pivoting of the levers (16, 17) of the lever assembly (14).
12. Cutting machine according to Claim 11, characterized in that the lever assembly (14), in the case of the hydraulic cylinder (12) not contacting said lever assembly (14), for lifting and/or lowering the pressure beam (4) is impingeable by means of the actuation means (35).
13. Cutting machine according to either of Claims 11 and 12, characterized in that the actuation means (35) have a synchronous shaft (36) that is drivable by the electric motor (13) and that is mounted in a stationary manner, cam pieces (37, 37) that at the end side are connected to said synchronous shaft (36), and rods (38, 38) which are pivotably connected to the cam pieces (37, 37) and are pivotably connected to the two levers (16, 17) of the lever assembly (14).
14. Cutting machine according to Claim 13, characterized in that the electric motor (13) is mounted in a stationary manner, the electric motor (13) by way of a gearbox (44) being linked to the synchronous shaft (36) in order for the synchronous shaft (36) to be pivoted by a part-circle, in particular by an angle of 60° to 90°.
15. Cutting machine according to one of Claims 8 to 14, characterized in that the hydraulic cylinder (12) is not connected to the levers (16, 17), and in a crossing region of the levers (16, 17) is advanceable from below towards the levers (16, 17) .

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