Cutter for cross cutting of webs

Abstract: Cutter for cross cutting of reeled webs (N) comprising a rotary cutting assembly (7) including a blade (16) and a counter blade (28) rotated in synchronism with an advancement assembly (16) of the web (N). The rotation axes (A,B) of the blade (16) and of the counter blade (28) are displaceable relative to each other, perpendicularly to the web (N), and actuator means (18,31,37) are provided to operate mutual approaching thereof when the blade (16) and the counter blade (28) are placed in a mutually facing angular position for cutting the web (N). The blade (16) and the counter blade (28) are rotated only at the time of cutting.

Description: The present invention is related to cutters for cross cutting of reeled webs, and more particularly of paper, aluminium, coupled paper-aluminium and the like webs, according to the preamble of claim 1, defined in view of US-A-5,207,138, 4 th embodiment. In the field of such web cutters three different systems are presently known. A first system consists of a vertically displaceable guillotine knife whose down stroke across the web performs severing thereof. Evidently descent of the guillotine knife requires stopping the web advancement, whereby this systems involves an excessively long operative time. It has also being proposed to make the cutting assembly movable and to displace it along the advancement direction of the web to avoid stop thereof upon severing. However this solution is constructively complicated and thus expensive. A second system employs a rotary knife, constituted by a plate mounted on the generating line of a blade-carrier cylinder, co-operating with a stationary counter blade. At each revolution, the blade projecting from the cylinder encounters the stationary counter blade, grazing it so as to cut the web interposed between the blade and the counter blade. This system is affected by precision problems and above all involves imperfections along the cut edges of the web caused by the fact that the counter blade is stationary and, as a consequence, cutting involves a more or less remarkable web tearing effect. The third system, also of a rotary type, includes a blade and a counter blade which are both rotary. More particularly, the cutters of this type comprise a web advancement assembly, a rotary cutting assembly including a blade and a counter blade arranged at opposite sides of the web advancement path and rotatable around respective rotation axes placed transversely of said advancement path, and motor driven means to operate rotation of the blade and of the counter blade around said rotation axes in synchronism with the advancement of the web and to place said blade and counter blade in a mutually facing angular position for cutting the web. This third system, while overcoming the drawbacks linked to the previous systems, does however not enable to achieve results in terms of cutting precision and production speed which would instead be desirable. Moreover in the case of the second and of the third system the blade and possibly the counter blade are as a rule continuously rotated during advancement of the web, which involves evident limits in connection with the maximum length of the web, deriving from the maximum diameter of the blade cylinder carrier (and possibly of the counter blade cylinder carrier) which can be applied to the cutter. The object of the present invention is to provide a cutter for cross cutting of reeled webs of the above disclosed third type, designed to achieve appreciably improved results both as far as cutting precision, repeatability and uniformity is concerned, and in connection with increased operative speed, and which moreover is not affected by any limits related to the web cutting length. According to the invention, this object is achieved by the features of claim 1. Due to this idea of solution, web cutting carried out between the blade and the counter blade is in practice performed by a shearing action, with a precision which is same and even greater than that afforded by the guillotine systems disclosed in the above, but with an operative speed which is at least same and even greater that that of the rotary systems, without any limits to the cutting length. This result can be achieved not only in connection with cuts perpendicular to the longitudinal edges of the web, but even as far as oblique cuts are concerned, providing a cutting assembly mounting capable to be angularly shifted relative to the web for instance between 0° and 45°. According to a preferred embodiment of the invention, said actuator means comprise a rotary cam system operating against the action of return resilient means. Moreover in the preferred embodiment of the invention the rotation axis of the blade is movable while the rotation axis of the counter blade is stationary. The cutter according to the invention can be advantageously employed for cutting reeled webs made of aluminium, paper, coupled paper-aluminium and the like, and can be installed in lines along with printing machines, spreading apparatus, spraying machines, coupling devices etc. The invention will now be disclosed in detail with reference to the accompanying drawings, in which: Figure 1 is a diagrammatic lateral elevational view of a cutter for cross cutting of reeled webs according to the invention, Figure 2 is a partially cross sectioned and enlarged view along line II-II of figure 1, Figure 3 shows in a larger scale a detail of figure 1, Figure 4 is a cross sectioned and enlarged view along line IV-IV of figure 2, Figure 5 shows in a larger scale a first detail of figure 4, Figure 6 is an enlarged partially sectioned view of a second detail of figure 4, shown in a first operating condition, Figure 7 is a view same as figure 6 in a second operating condition, Figure 8 is a perspective view of a part of figure 6 and Figure 9 is an exploded view of figure 8. Referring initially to figure 1, reference numeral 1 generally designates a cutter according to the invention, designed to be employed in the case of the shown example for cross cutting of a web N made of aluminium. The cutter 1 comprises an unwinding station 2 including in the case of the shown example two reels 3 from which the web N, drawn through a joining unit 4 and a traction control device 5 of the web N, is unwound by a motor-driven drawing assembly 6. Downstream of the drawing assembly 6 the web N advances along a horizontal path, shown by the arrow F, towards a rotary cutting assembly generally designated as 7, followed by an acceleration roller unit 8 and by a guide channel 9 of the cut sheets. Referring now in more detail to figures 2,3 and 4, the rotary cutting assembly 7 comprises a pair of vertical bearing walls 10 supporting for rotation a first shaft 1 rotatable around a horizontal axis A arranged above the advancement path F of the web N, a second shaft 12 rotatable around a horizontal axis B located beneath the advancement path F, and a counter shaft 13 rotatable around a horizontal axis C arranged above the axis A. The shaft 11 carries a radially projecting and axially elongated support 14, to which a blade or knife 16 is releasably secured, for instance by means of screws 15. The conformation of the blade 16, which has a tapered cross section, can be seen in more detail in figures 4 and 5. On the diametrically opposite side to the support 14, the shaft 11 carries a counterweight 17. Reference numerals 18 designate two cylindrical gears fixed in proximity of the ends of the shaft 11, designated as 19a and 19b. These ends 19a, 19b are rotatably mounted through respective sliding blocks 20, in turn slidably guided vertically within respective apertures 21 formed in the bearing walls 10. The sliding blocks 20, and thus the ends 19a and 19b of the shaft 11, are normally placed in a raised position shown in the drawings (and particularly in figure 3), and are capable to move downwardly, such as clarified herebelow, against the action of respective return springs 22. In the case of the shown example the springs 22 consist of helical compression springs: however these springs may be replaced by elastomeric material pads or the like. The lower shaft 12 is actually constituted by two axial shaft portions whose ends, designated as 23a, 23b, are rotatably supported by the vertical bearing walls 10. The two portions of the shaft 12 coaxially support a cylindrical jacket 24 formed with an axial slot 25 in correspondence of which a channel support 26 is fitted, to which a counter blade 28 is secured for instance by means of screws 27 (figures 4 and 5). On the diametrically opposite side to the support 27 with the counter blade 28, the cylinder 24 carries an axial counterweight bar 29. The counter shaft 13 is rotatably supported at its ends 30a, 30b by the vertical bearing walls 10 and carries, near to these ends 30a, 30b, a pair of cylindrical gears 31 whose diameter is same as the diameter of the gears 18 of the shaft 11, and meshing therewith. Referring in more detail to figure 2, a driving unit generally designated as 32 is operatively associated to the rotary cutting assembly 7, which includes an electrical motor 33 conveniently of the brushless type driving in rotation, through a first gear pair 34 and a second gear pair 35, the end 23a of the shaft 12 of the counter blade 28, and the end 19a of the shaft 11 of the blade 16, respectively, via a cardanic shaft 36. The electrical motor 33 is operated by means of an electronic control unit (not shown), in a programmable way and in synchronism with the driving motor of the drawing assembly 6, and rotates the shaft 11 and the shaft 12 not continuously, but instead in an intermittent timed way as a function of the desired cutting length of the web N, which accordingly is not subjected to any limitation. The arrangement is such that the shaft 11 and the shaft 12 are driven in rotation by the motor 33, whenever cutting is to be performed, with same peripheral speed, whereby following each complete revolution the blade 16 and the counter blade 28 are placed in a mutually facing angular position at opposite sides of the web N, such as depicted in figures 2,4 and in better detail in figure 5. According to the fundamental feature of the invention, in correspondence of the above angular positioning the blade 16 is linearly displaced with respect to the counter blade 28 so as to penetrate with its cutting edge, in immediate proximity of the corresponding edge of the counter blade 28, into the cavity of the channel support 26. This displacement, upon which transverse cutting of the web N is carried out, is operated through the counter shaft 13 and the downward motion of the sliding locks 20, against the action of the respective springs 22. To such effect each pair of meshing gears 18,31 is operatively associated to a respective cam system, shown in detail in figures 6 through 9. This cam system simply comprises a shim or bar member 37 fitted within the space between two adjacent teeth of the corresponding gear 18, in an immediately proximal angular position to the counterweight 17 of the shaft 11, i.e. at an almost diametrically opposite position with respect to the blade 16. As shown in detail in figures 8 and 9, the shim member 37 is secured to a pair of mounting plates 38 fitted within corresponding opposite recesses 39 of the gear 18 and fixed to the latter by means of axial screws 40. In operation, the gears 18 and 31 are regularly meshing with one another until the shim members 37 of the gears 18 reach the angular meshing position with the gears 31 (figure 6). Starting from this condition, corresponding to the position in which the blade 16 is facing towards the counter blade 28 (figure 5), meshing of the gears 18 with respect to the gears 31 takes place irregularly owing to the presence of the shim members 38, thus performing downward displacement of the gears 18, and thus of the whole shaft 11 against the action of the return springs 22, and consequently partial penetration of the blade 16 into the cavity of the channel support 26 of the counter blade 28. By virtue of this displacement the web 9 is cut by a shearing action between the blade 16 and the counter blade 28, in a sharp and precise way. While rotation proceeds, the shim members 37 are disengaged from the gears 31, whereby the gears 18 and thus the shaft 11 as a whole can be moved back to the previous raised position, due to the thrust action of the return springs 22. Naturally the details of construction and the embodiments may be widely varied with respect to what has been disclosed and illustrated, without thereby departing from the scope of the present invention such as defined in the appended claims. Thus for example, and as already pointed out in the above, the rotary cutting assembly 7 may be designed to perform a cut oriented obliquely instead of perpendicularly to the longitudinal edges of the web N, providing that mounting thereof enables its angular shifting with respect to the web N for instance between 0° and 45°.

Claims: Cutter for cross cutting of reeled webs (N), comprising a web advancement assembly (6), a rotary cutting assembly (7) including a blade (16) and a counter blade (28) arranged at opposite side of a straight advancement path (F) of the web (N) and rotatable around respective rotation axes (A,B) placed transversely of said advancement path (F), and motor driven means (32) to operate rotation of said blade (16) and of said counter blade (28) around said rotation axes (A,B) in synchronism with the advancement of the web (N) and to place said blade (16) and said counter blade (28) in a mutually facing angular position for cutting the web (N), wherein the rotation axes (A,B) of the blade (16) and of the counter blade (28) are further displaceable relative to each other perpendicularly to the web (N) wherein said blade (16) and said counter blade (28) are rotated only at the time of cutting, and wherein upon cutting said web (N) remains substantially undeviated from said advancement path (F), characterised in that in that gear actuator means connected to the cinematic chain that operates rotation of said blade and counter blade are provided (18,31,37) to operate mutual approaching between said rotation axes (A,B) when said blade (16) and said counter blade (28) are located in correspondence of said angular cutting position. Cutter according to claim 1, characterised in that said actuator means comprise a rotary cam system (18,31,37) operating against the action of return resilient means (22). Cutter according to claim 2, characterised in that the rotation axis (A) of the blade (16) is movable while the rotation axis (B) of the counter blade (28) is stationary. Cutter according to claim 3, characterised in that it comprises: a bearing structure (10), a first shaft (11) carrying a support (14) for the blade (16) and a second shaft (12) carrying a hollow support (26) for the counter blade (28), said first and second shafts (11,12) being rotatably supported at the respective ends (19a,19b; 23a,23b) by said bearing structure (10) around said rotation axes (A,B) and being operated by said motor driven means (32), guide means (20,21) provided between the ends (19a,19b) of said first shaft (11) and said bearing structure (10) to enable said approaching, against the section of said resilient thrust means (22), a counter shaft (13) rotatably supported by said bearing structure (10) parallely to said first shaft (11) and on the opposite side to said second shaft (12), and geared coupling means (18,31) between said first shaft (11) and said counter shaft (13) and incorporating said rotary cam system (37). Cutter according to claim 4, characterised in that said rotary cam system comprises a shim member (37) fitted within the space between two adjacent teeth of one gear (18) of each of said geared coupling means (18,31). Cutter according to claim 4, characterised in that said guide means include sliding blocks (20) rotatably supporting said ends (19a,19b) of the first shaft (11) and vertically slidable along corresponding guides (21) of said bearing structure (10). Cutter according of any of the preceding claims, characterised in that the rotary cutting assembly (7) is mounted so as to allow angular shifting thereof relative to the web (N) between 0° and 45°.

Inventors: TOSATTO GIACOMO, TOSATTO, GIACOMO
Applicants: TEMCO S R L, TEMCO S. R. L.
Application year: 1998
Main classification: B26D1
IPC codes: B26D5, B26D1