JPH05337882A - Rotary blade cutting machine and cutting method for cutting small rolls such as toilet tissue paper from considerably long roll or log - Google Patents

Abstract

PURPOSE: To cut small rolls of paper such as toilet tissue paper by continuous work. CONSTITUTION: A blade 50 has a helicoidal shape with an external cutting edge having increasing radius and developing over a partial sector, the difference between maximum and minimum radius being at least equal to the maximum diameter of the roll or log to be cut. A shaft 45 and the axis of a blade rotor 42 are not displaced during the rotor's revolution and are slightly inclined with respect to the direction of advancement of the log within its carrier. Thus the cut performed on the roll and the cutting edge are on the average perpendicular to the axes of the logs. The advancement of the logs in the carrier is continuous and the cutting is executed during a portion of each revolution of the rotor and dring that portion of the roll's advancement which corresponds to the axial length of the small roll to be produced.

Description

Detailed Description of the Invention

The most common cutting machines for making small rolls of paper, including toilet paper and multipurpose wipes, are equipped with discoidal high speed rotating blades. The axis of rotation of the blade is a reciprocating movement in a direction perpendicular to the log feed movement, or a rotation about an axis parallel to the log feed movement. Whatever the movement of the blade axis, it has the purpose of moving the blade into and out of the product to be cut, where when the blade leaves the product to be cut, the product is the length to which the small roll is cut. You can move forward by the corresponding length. Periodic movements of the cutting element and the product feeder, which are equal to the production of small rolls, give rise to distinct quantitative and qualitative drawbacks and limitations in production.

These and other shortcomings are solved by the cutting machine of the present invention provided for cutting small rolls such as toilet paper from rolls or logs of significant length, which machines have sliding seats or supports. It has a pedestal, a rotor with one or more logs sending devices to be cut and blades. In particular, according to the invention, the blade has a helicoid cone shape with an external cutting edge whose radius varies over a part of the rotation (or over the entire rotation). The difference between the maximum and the minimum radius of the cutting edge is at least equal to the maximum diameter of the roll or log to be cut. The rotary shaft and the blade rotor are slightly displaced with respect to the sliding direction of the log at their seats or bases without displacement during rotation of the rotor. Thus, the cutting performed on the log by the cutting blade cutting edges is, on average, perpendicular to the log axis. The advance of the log (B) on the platform is continuous and the cutting is carried out during a part of the rotor rotation and also during a part of the advance of the log corresponding to the axial length of the small roll to be produced.

The blade polishing apparatus can move periodically with respect to the blade in a radial direction as well as in an axial direction (that is, can move with each rotation of the blade rotor).
Have members. The device for advancing the grinding wheel towards the blade can be obtained in two different ways. Moving the pedestal of the grinding wheel towards the rotor axis, or moving the blade in its seat towards the grinding wheel. The cutting machine of the present invention (like a conventional cutting machine) has a two-part clamp that holds the log and is located upstream and downstream of the cutting zone.
The clamps exert an elastic, constant, adjustable but not necessary high pressure force on the material of each log to continuously advance the logs. In this case, the clamp opposes the lateral thrust produced by the blades and is therefore only for gripping the roll or log during the cutting action.

With continuous polishing, the size of the blade is reduced. .. To compensate for this wear and ensure a complete cut of the roll or log, the machine is equipped with a device that allows the blade and rotor axes to approach the slide of the roll or log.

In view of the above and other objects, a better understanding and a better understanding of the present invention will be explained further below with reference to the drawings. For purposes of illustrating the invention, the presently preferred form is shown in the drawings, although a variety of configurations that facilitate an understanding of the invention can be made and described. It is not limited to the exact same configuration arrangement as the one. Like reference numerals in the drawings denote like parts.

1-6, reference numeral 1 designates the cutting area of a log saw to which is mounted a structure (3) holding a base or seat slidably supporting the log to be cut. In this case there are three pedestals, 4, 4A and 4C, but more or less can be provided if desired. A chain pusher or other type of pusher with a continuous flexible member is provided along the seat, which pushes the pusher 5 along a platform as indicated by 4, 4A, 4C. Chain wheel 9, so that it slides
11 (or a pulley in the case of a toothed chain) having thrust elements 5 engaging along the chain which are driven.
A sleeve 14 is attached to the housing by a ball bearing (not shown), and its axis is slightly inclined with respect to the roll feed direction defined by the slide base. This sleeve lies in a plane parallel to the plane in which the two other slides 4, 4C are. The tables 4 and 4C are slightly higher than the slide table 4. A main shaft 15 is provided in the sleeve 14. On the sleeve 14, 1) a unit 16 capable of vibrating around the axis of the sleeve 14 and supporting a cutting tool described below, 2) a motor 18, and 3) a set of blade polishing devices described below are mounted. .. The drive belt 20 connects the motor 18 and the shaft 15. The drive belt 22 installed outside the housing transmits the movement of the shaft 15 to the reduction gear 24. The reduction gear 24 transmits a continuous motion reduced in speed through a universal joint 26 to a shaft 28, and a chain pulley or wheel 11 is attached to the shaft 28 for moving the pusher 5.

A unit 16 oscillating about the common axis of the sleeve 14 and the shaft 15 has a unit 1 at 32.
6 and 34 at 34 is pivotally mounted to a bracket 36 fixed to the main frame 1. The rod 30 is raised and lowered by a screw-nut device which is actuated by a motor reducer, described below, which appropriately determines the angular displacement of the unit 16 to accommodate the wear of the cutting blade. It Adjustments to this nut (as a result of the action of the abrading device described below) control the slow, continuous lowering of the unit 16 about the sleeve 14 and the shaft 15 to ensure that the cutting blade is abraded. You can A belt 40 connected to the shaft 15 rotates a rotor 42, the hub 44 and extension 45 of which rotate on the shaft 1.
Rotate about an axis coaxial with the 5 axis. It is supported by unit 16 at a position between the pivot point on sleeve 14 and the pivot point of rod 30. A disk 46 is attached to the flange of the hub 44, about the periphery of which is engaged an annular ring 48 having a special shape with a helicoidal path shoulder 48A. A flexible blade 50 is secured to the flanged shoulder 48A, the blade being located on a partial arc around the flanged shoulder 48A (180 ° in the illustrated embodiment).
(Over the range of). A corresponding re-nong sector locking ring 48B cooperates with the blade 50 by means of a tightening screw on the shoulder 48A. The outer cutting edge of blade 50 has a path in which the radius varies approximately linearly between a minimum value and a maximum value between the two ends 50B, 50C of the blade. Prior to installation, the flat blade becomes helicoid when clamped between the flanged shoulder 48A and the retaining ring 48B. The difference between the maximum radius and the minimum radius of the cutting edge 50A corresponds to the maximum diameter of the log (B) cut by the cutting machine.

The maximum radius end 50C of the blade 50 moves along a circular trajectory T. Trajectory T in the lower part
Passes the lower part of the log B in the platforms 4, 4A and 4C.
The inclination of the rotor axis parallel to the axes of the sleeve 14 and the shaft 15 is such that the chord of the blade helix is substantially perpendicular to the axis of the log, ie the axis of the table on which the log slides, within the arc that engages the log B to be cut. Is like. The above geometrical conditions are approximate, but with acceptable error and sufficient accuracy with respect to the cutting plane which is approximately perpendicular to the axis of the log to be cut. The direction of rotation of the rotor is indicated by arrow F, and the outer cutting edge 50A of the blade during each rotation is about half a revolution,
That is, it operates on an arc having an angular shape corresponding to the cutting edge of the blade itself. The cutting edge 50A is gradually located at the position of the blade tip, from the position at the maximum distance from the bases 4, 4A, 4C to the bottom of the base in the area of the maximum radial dimension of the blade, that is, the end of the blade
It goes down to 50C. During part of the rotation of the rotor (in this case about half a revolution), the blade 50 cuts the log, which is displaced in the log feed direction along arrow fB (see FIG. 3) due to the spiral path. This displacement is equal to the fraction of the pitch of the geometric helix in which the cutting blade is present, and in fact the blade or helicoid present therein (typically about half a pitch).

The total pitch of the geometric helix defined by cutting edge 50A corresponds to the axial dimension of the small roll obtained by cutting log B with the blade.
During the working arc of the blade (slightly greater than 180 ° in the figure), the blade carries out the cutting of the logs of the three pedestals 4, 4A, 4C by advancing along the logs pushed by the pusher 5. After the working arc of blade 50A is completed,
That is, when the blade end 50C leaves contact with the log, the roll or log continues to advance along the platform,
Axial equal to the pitch of the geometric helix of the cutting edge 50A, partly actuated during cutting by the blade 50 and partly inactive (slightly less than 180 ° of rotation of the rotor 42) Small roll cutting is performed by the blade 50 having dimensions. With the above-mentioned device, it will be appreciated that a continuous advance of the blade as well as a continuous advance of the log B in the table 4 by the pusher 5 is produced. As far as the description is given, none of the components undergo another movement with a frequency equal to the rotational frequency of the blade. Certain members of the relatively limited weight described below produce a limited reciprocating motion with a frequency corresponding to the rotational frequency of rotation of the rotor 42. These parts are in particular parts of the device for polishing the blade 50, which device has to comply with the periodic changes in the radial dimensions of the helicoid path of the blade and of the cutting edge 50A. The continuous displacement performed by the elements 30-38 is a very slow, continuous and non-reciprocating motion as the blade wear moves the rotational axis of the rotor 42 which continuously approaches the platform 4. As will be appreciated by those familiar with the art, the above arrangement provides clear advantages over conventional cutting machines having a relatively large mass with reciprocating motion at the frequency of the cutting cycle.

According to another embodiment, a device for periodically changing the advancing speed of the roll during each rotation of the rotor may be provided to increase or decrease the advancing speed during the blade inoperative phase. This is a universal joint 26 on the transmission 15-28.
This can be achieved by the device shown in FIG. Such a device is described in US patent application Ser.
7/856443 or corresponding European patent application No. 92 / 830161.3, the contents of which are hereby incorporated by reference. The axial dimension of the small roll increases with acceleration and decreases with deceleration. As mentioned above, the logs in the pedestals 4, 4, 4C move forward (and possibly cyclically) in a continuous motion. The cutting area where the blades 50 act requires a lateral or peripheral support to support the material during the cutting operation. This is usually formed by a so-called "clamp", which in prior art machines periodically applies a temporary pressure to the log when the log is stopped to perform a cut and also allows intermittent advance of the log. Released. In the cutting machine according to the present invention, which continues to move forward during the cutting operation, a pressing tool is provided which works continuously and restrains laterally, but allows the log to slide. The reason is that the outer surface of the log and the pressing tool work. The friction between the concave surfaces of the parts is very small.

According to the structure shown in FIGS. 3, 7 and 8, two elements 54, 56 are provided along each platform 4, 4A, 4C.
Are provided, the concave surfaces of which point towards the arrow F indicating the movement of the blade 50. Therefore, the log pushed by the blade in the direction of arrow F during cutting is gradually changed by the element 5
It contacts the concave surface of 4,56. Further elements 54A and 56A, indicated generally by the reference numerals 54 and 56 and oriented generally symmetrically with respect to the axis of the log platform, provide a relatively limited and adjustable pressure to the advancing log. It is elastically biased to allow continuous advancement of the material. It is thus possible to support the material well in the cutting area and to perform a clean cut on a well-held and well-supported material. The elements 54A, 56A are generally T-shaped and are pivotally mounted at 60 to a fixed point of the housing 1 and further at 62 by a spring or, preferably, an air cylinder.
The bar 64 pushed in the direction of arrow F64 by the spring 66
Pivotally attached to the spring 66, the spring 66 acts on a stem 68 engaged at 70 to the fixed structure of the frame 1. This device as well as changes in air pressure can adjust the sexual thrust of the moving elements 54A and 56A to control the switching pressure of the logs to make them continuously slidable. This elastic deformation element 54
The installation of A, 56A can also accommodate changes in the diameter of the logs sent to the cutting machine, at least within tolerance limits. Elements 54, 56 and 54A, 56A have enlarged or chimney-shaped ends toward the incoming material to fit the blade during cutting.

An apparatus for always properly polishing the cutting edge 50A of the blade 50 will be described below. The polishing machine is equipped with a periodic radial movement corresponding to the change of the radius of the cutting edge 50A, and the cutting edge 50A.
Perform a periodic axial motion according to the helicoidal form of A.
These two periodic movements in synchronization must be carried out during each revolution of the rotor. Each rotation has a working step in which the cutting edge 50A slides in front of the polishing apparatus and a returning step without a cutting edge in an arc. The polisher must be gradually adjusted during the life of the blade to compensate for blade wear and maintain its sharpness. As shown in FIGS. 5 and 10 to 15, the support 74 is fixed on the unit vibrating on the sleeve 14. Two guides 80 are fixed to the extension of the support by blocking devices 76, 78, the guides being in a radial plane passing through the axis 69 and the axis 45 of the rotor 42. The guide 80 is also in a plane inclined with respect to a plane perpendicular to the axis of rotation of the rotor 42. This slope actually corresponds to the slope of the straight line LR which contacts the ends 50B, 50C of the blade 50 when they are in their closest position.

On the support 74 and also in particular the bracket 7
Pins 82 are mounted on 4B and their axes are axis 45.
Parallel to, on which the lever arm 84 can oscillate. A dual tappet roller has two flanks mounted on the arm 84 and acting between two flanks of the grooved cam 88 and flanks of different heights of the groove 88 (see FIGS. 3 and 4). ). The groove 88 is a discoid-shaped body 90 fixed to the blade rotor 42.
Is formed in. The groove cam 88 is formed in an annular shape, and the rotation of the rotor 42 of the blade 50 causes the lever arm 8
4 can be vibrated by the control of the groove cam 88.
The movable end of lever arm 84 engages via a ball joint joint, generally indicated at 92, to a connecting strut 94 having the function described below. A slide 96 is slidably attached to the guide 80, and the slide 96 is reciprocally moved along the guide 80 by a connecting strut 94, and the connecting strut 94 is connected to the slide 96 on the opposite side of the ball joint 92. It has a ball joint 98. Ball joints 92 and 98 are guides 80
The lever arm 84 even if is inclined as described above.
This enables the slide 96 to reciprocate.

The slide 96 supports two parallel guides 100, 102 via an extension 96A. The guide 100 is cylindrical and rotatable in the ball bearing 104 while the guide 102 is the guide shaft, but does not move axially and is provided with a threaded portion 10. On the guides 100 and 102, a skid 106 that can move along the guides 100 and 102 slides in a direction in which the guides 100 and 102 are held substantially at right angles to the axis of the rotor 42 and the shaft 45. The skid 106 carries a grinding wheel that grinds the blade 50 as described below. Slide 9 with polishing wheel
The skid 106 in combination with the reciprocating movement of 6 must gradually and slowly approach the rotor to accommodate the progressive wear of the blade, and precisely grind the blade's cutting edge 50A. The slide 96 is driven at a frequency corresponding to the frequency of the rotor 42, and reciprocates LR in each rotation in order to follow the radial and axial changes in the shape of the cutting edge 50A of the blade 50. At the same time, the grinding wheel supported by the skid 106 must be gradually and slowly displaced relative to the slide 96 by the amount necessary to compensate for the ongoing wear of the blade 50. The progression of the skid 106 is determined by the threaded joint of a cylindrical axial guide with the corresponding nut 106A of the skid 106 and by the rotation of the guide 102.

Above the rotating cylindrical threaded shaft guide 102 is a one-way joint (freewheel) between the shaft and a rocker lever 110 that reciprocates about the shaft 102. The rocker lever 110 preferably oscillates reciprocally around the guide shaft 102 by means of a pneumatic cylinder-piston device 112, and also moves at a frequency according to the wear of the blades. There, positive control in two directions or elastic reaction control ensures that periodic vibrations of the rocker lever 110 over a limited arc are produced. Rocker lever 110 is guide shaft 102
Together with a central member 113 supported by, a freewheeling device with a one-way drive member 110A is formed. This one-way coupling device 110, 110A, 113 achieves slow, intermittent rotation of the guide shaft 102, thereby slow advance of the skid in the direction of arrow F106 during the blade life cycle, replacement of a worn blade with a new blade. In doing so, it allows the blade to return to its starting position (away from the blade cutting edge). The skid 106 protrudes from the opposite side of the skid and has two grinding wheel units 118, 120.
Supporting a pin supporting the unit, the unit is cantilevered to adjust the angular position on the pin. Each of these relative angular positions can be observed by an indexing device 118A, 120A cooperating with an angular scale supported by the skid 106.

On the grinding wheel unit 118, and in particular on its cantilever projection, two leaf springs are provided which are connected to the grinding wheel support 124. The cylinder-piston device 126 operates between the grinding wheel unit 118 and the grinding wheel support 124 to move the grinding wheel support 124 parallel to itself due to the flexibility of the leaf spring 122. The grinding wheel support 124 has a protruding shaft that supports a motor 127 that drives a grinding wheel 128, the grinding wheel supporting a grinding wheel unit 1 on a shaft 116.
It has a tilt corresponding to 18 angle settings, said settings being controlled by the indexing device 118. Abrasive wheel unit 118
Another polishing wheel unit 120, opposite the member supported by the
And a leaf spring 132 supporting a grinding wheel unit 134 configured to be controlled by a cylinder-piston device 136. The grinding wheel unit 134 includes its own motor 137 for driving the grinding wheel 138, which is biased relative to the wheel indicated at 128 and tilted in the opposite direction relative to the surface of the blade 50 being ground. There is.

The arrangement of the skid 106, and everything connected to it, allows the grinding wheel 128 to be accurately positioned and leaf springs at a constant tilt.
122 also cylinder-piston device 126 and 136
Thus, the blade 50 can be elastically pressed against the cutting edge 50A. This causes the polishing wheel to follow a periodic change in the radius of the cutting edge 50A of the blade 50 due to the reciprocating movement of the slide 96 with each revolution of the rotor 42. The grinding wheel is also moved forward in a substantially radial direction, as indicated by arrow F106, following the blade wear by the intermittent feed determined by the cylinder-piston device 112 rotating the guide shaft 102, causing the threaded joint of the skid 106 to move. Move slowly forward through. Blade replacement is accomplished by the rapid return of the wear compensator to the initial position. The grinding wheels follow the blades when they are reciprocally actuated by the alternating motion of the slide 96 along the guides 80 and by the tilting of such guides 80, which means that the blades are helicoidal as well as during each revolution. Allows to follow the radial changes of the blade.

16 to 19 show a second or different embodiment of the polishing apparatus. In the embodiment shown in FIGS. 10-14, the grinding wheels 128 and 138.
Drive 110, 112 acting on the guide 102 threaded by the guide 100 and at 102A by a skid 106 which gradually and radially approaches the axis of the rotor 42.
And supported by 113, advance the skid in the direction of arrow F106. According to the embodiment shown in FIGS. 16-19, the relative angular or tangential advancement of blade 350 (corresponding to blade 50) actuates the reciprocating motion of slide 96 relative to the cam (corresponding to cam 88). Given. In fact, considering the diagram of FIG. 16 which shows the straight path of the arcuate blade in diagram A (corresponding to FIGS. 10-14), not only the reciprocating motion caused by the slide 96 relative to the grinding wheels 128, 138 Blade 50
A device is provided for carrying out the advance according to arrow F106 to. According to diagram B, the grinding wheels 428, 438 do not gradually advance and slide along the guide 80.
It supports only the reciprocating motion of. The groove cam 88 is fixed,
It is a blade that gradually advances in the direction of arrow F406 by the angular movement with respect to the rotor 42.

In FIGS. 17-19, elements corresponding to those already described are designated by the same reference numeral with "300" added. Elements that engage blade 350 348, 34
8B has a disk 246 with a central hole. Inner edge 246A of disk 246
Is slidably engaged between the discoid body 90 of the groove cam 88, the hub 344 and the side member 252 fixed like the body 90 to the periphery of the hub 344. in this way,
Units 246, 348 and 348B are angularly displaced within groove 250 relative to cam 88 which drives slide 396 to reciprocate. The hub 344 has a bushing 211 that can move parallel to, but offset from, the axis of the rotor 42.
Is rotatably mounted. A threaded rod 215 is threadably engaged with a threaded hole 213 extending in the diametrical direction of the bush 211. This rod 215 is rotatably attached to an axis 219 through an articulation joint 217 and to an axis 219 mounted by roll bearings on a support 221 supported by units 246, 348, 348B of blades 250 on an axis 219. Equipment 223
Can drive the shaft 219 and thus the threaded rod 215 at low and intermediate rotational speeds. The device 223 is not described in detail since it is constructed exactly the same as the device 110 which drives the guide shafts 102, 102A in the same way as described in the previous embodiment. The compressed air conduit may, for example, lead to the air actuator of device 223, rotor 4
2 and its shaft are configured to have a joint that rotates inside the axial bore. The threaded rod 215 thus gradually causes angular sliding of the set 348, 348B, 246, 246B of blades 350 relative to the hub 344 and cam 90,
This determines the angular movement of cutting edge 350A of blade 350 in the direction of arrow F406 with respect to the grinding wheel.

In this second embodiment, the following members are removed from slide 96: That is, the actuator devices 112, 110, 113, 110A, the guide shafts 100 and 102, 10
2A and Skid 106. As can be seen in FIG. 17, the same slide 396 is the pin 416 of the two grinding wheel holder units 418 and 420. Furthermore, in this second embodiment, there is no longer a roll or log stand 4,4.
It is not necessary to slowly move the rotor axis near the A and 4C and into the clamps as well because of the 350A cutting edge 350A.
Does not change its distance from the axis of rotation due to wear and polishing, but it does change its angular position in practice slightly. The change occurs in the direction of arrow F406, ie in the direction of the cut line (FIG. 16B), and like the first solution of the polishing apparatus, in the direction of arrow F106, ie in the radial direction (FIG. 16A).
Therefore, the arm 16 no longer needs to move around the shaft 15 and the sleeve 14 and the associated members 32, 30, 3
8 and 36 are not needed. The arm 16 can be replaced by a lever 116 having an inlet-like structure, and its strut 116A is replaced by the adjustable supports 32, 30, 34, 38, 36. The drawings are merely illustrative for the practical disclosure of the invention and can be modified in form and arrangement without departing from the scope of the technical concept to which the invention is based. The existence of the reference signs in the claims is intended to facilitate understanding of the claims with reference to the description and the drawings, and does not limit the protection scope of the claims.

[Brief description of drawings]

FIG. 1 is a schematic plan view of a device of the present invention.

FIG. 2 is a schematic front view taken along the line II-II in FIG.

FIG. 3 is a partial side view taken along the line III-III in FIG.

FIG. 4 is a partial view of FIG.

FIG. 5 is an enlarged view of FIG.

FIG. 6 is a partial cross-sectional view of a blade rotor.

FIG. 7 is a side view showing a set of clamps supporting rolls or logs in the cutting area.

FIG. 8 is a major surface showing a set of clamps supporting rolls or logs in the cutting area.

9 is a plan view seen in the direction of IX-IX in FIG.

FIG. 10 is a diagram showing a first embodiment of an apparatus for periodically polishing a blade.

11 is a plan view taken along line XI-XI of FIG.

12 is an enlarged detail view of the device shown in FIG.

13 is an enlarged detail view of FIG. 10 different from FIG.

FIG. 14 is an enlarged detailed view of FIG. 10 different from FIGS.

FIG. 15 is an enlarged detailed view of FIG. 10 different from FIGS. 12, 13 and 14;

FIG. 16 is a diagram comparing the first and second embodiments of the polishing apparatus.

FIG. 17 is an axial view of a machine equipped with a second embodiment of the polishing apparatus.

FIG. 18 is a side view of a machine including a second embodiment of a polishing device.

FIG. 19 is an exemplary drawing with a portion perpendicular to the plane of FIG. 17;

[Explanation of symbols]

 4 units 5 pusher 14 sleeve 15 main shaft 16 unit 18 motor 24 reduction gear 26 universal joint 28 shaft 30 rod 42 rotor 44 hub 46 disc 48 annular ring 48A shoulder 48B fixing ring 50 blade 54 element 56 element 80 guide 84 arm 88 Groove 94 Strut 96 Slide 100 Guide 105 Skid 110 Rocker lever 112 Cylinder-piston device 118 Abrasive wheel unit 120 Abrasive wheel unit 124 Abrasive wheel support device 128 Abrasive wheel 132 Leaf spring 135 Cylinder-piston device 138 Abrasive wheel 246 Disc 250 Blade 348 Unit 390 Slide 428 Abrasive Wheel 438 Abrasive Wheel

Claims (18)

[Claims] 1. A rotation for cutting a roll of considerable length or a small roll, such as toilet paper, from a roll or log having a slide and feed for one or more logs to be cut and a rotor with blades. In a blade cutting machine, the blades (50; 350) are helicoid-shaped, with increasing radius and the difference between the maximum and minimum radii being at least equal to the maximum diameter of the roll or log (B), the rotor of the blade (50) ( 42) axis of rotation (44, 45, 344, 345)
Is slightly inclined with respect to the sliding direction of the log in its base (4, 4A, 4C), so that the working area of the blade logs a short roll (B).
A rotating blade cutting machine for cutting small rolls such as toilet paper from rolls of significant length or logs characterized by cutting substantially perpendicular to the axis of the log (B) during continuous movement. 2. The cutting edge of the blade (50; 350) is such that the rotary blade has a partial fan shape, the cutting being carried out during a part of the rotor rotation and of the log advance corresponding to the axial dimension of the small rolls to be produced. A rotary blade cutting machine for cutting small rolls, such as toilet paper, from a length of roll or log as claimed in claim 1 implemented in part. 3. A considerable length according to claim 1, characterized in that it comprises a blade-polishing device, said device having a unit which can be moved both radially and axially for each revolution of the blade rotor. A rotating blade cutting machine that cuts small rolls such as toilet paper from rolls or logs. 4. For each log having a clamp acting upstream as well as downstream so that said clamp (56, 56A) pressurizes each log by a constant and sufficiently limited pressure so that the logs can be advanced continuously. 2. An elastically urged member, wherein the adjacent ends of the clamp are shaped to fit the blade during its cutting operation.
Or a rotary blade cutting machine for cutting small rolls such as toilet paper from rolls or logs of considerable length according to 2. 5. A discoid core (46, 48;) in which the blade rotor (42) comprises a helicoid shoulder flange.
246, 348) to which flexible blades (50-35
0) is clamped by a ring (48B-348B) having a complementary shape, said blade having a conical spiral or outer diameter varying profile and extending over the rotating part, the difference between the maximum and minimum radii (D ) Is greater than or equal to the outer diameter of the roll or log (B) to be cut, and the tightening of the blade makes the blade substantially helicoidal. A rotating blade cutting machine that cuts small rolls such as toilet paper from rolls or logs. 6. Blade rotor (42) for rotation and a base
7. A substantial motor according to claim 1, characterized in that it has a single motor (18) with a transmission for advancing the log pushers (7, 8) in (4, 4A, 4C). A rotary blade cutting machine that cuts small rolls such as toilet paper from rolls or logs of length. 7. Blade rotor (42) for rotation and platform
3. A device according to claim 2, characterized in that it has a single motor (18) with a transmission for advancing the log platform (7, 8) in the (4, 4A, 4C). A rotary blade cutting machine that cuts small rolls such as toilet paper from long length rolls or logs. 8. The transmission (22, 24, 26, 28) comprises blades for each revolution of the blades so that the distance of successive cuts is varied.
7. A roll of significant length or log to small roll, such as toilet paper, according to claim 6, characterized in that it comprises a device (200) for accelerating or decelerating the feed rate of the pusher during the inoperative phase of (50). Rotary blade cutting machine to cut the. 9. The transmission (22, 24, 26, 28) comprises blades during each revolution of the blades so that the distance of successive cuts is varied.
8. A roll of significant length or log to small roll, such as toilet paper, according to claim 7, characterized in that it comprises a device (200) for accelerating or decelerating the feed rate of the pusher during the inoperative phase of (50). Rotary blade cutting machine for cutting. 10. A unit (26) for a blade rotor (42).
In the guide (80) installed toward the rotation axis of the rotor (42) and inclined with respect to a plane perpendicular to the axis, the maximum radius of the blade cutting edge in the area of the guide (80) and The orbits of the points of minimum radius (50C, 50B) are parallel to the line of contact, said guide (80), at the same frequency as the rotation of the rotor (42) of the blade on said guide (80) and in synchronization with it. 4. A considerable length according to claim 3, characterized in that it has a slide (96) which reciprocates by means of a wheel and a grinding wheel (128, 138) on the slide (96) for grinding the helicoidal cutting edge of the blade. A rotating blade cutting machine that cuts small rolls such as toilet paper from rolls or logs. 11. A cam, preferably grooved annular cam (88) extending around the axis of rotation on the rotor and for driving a slide (96) of the grinding wheel on the unit (16).
Articulation (8) with tappet (86) actuated by (88)
A rotary blade cutting machine for cutting small rolls, such as toilet paper, from rolls or logs of considerable length according to claim 10, characterized in that they have a length of 4,92,94,98). 12. Guides (100, 102) installed on the slide (96) in a substantially radial direction with respect to the rotor (42) of the blade (50), a motor device on the guides (100, 102). Abrasive wheels (128,138) with (127,137) and elastic suspensions (122,1)
26; 132, 136), a skid (106) for swingably supporting,
And on the guides (100, 102) of the slide (96), slowly advance the skid wheel skid (106),
A device (112; 110; 113; 102) that causes (128, 138) to approach the axis of the rotor (42) as the blade (50) wears due to polishing.
A rotary blade cutting machine for cutting small rolls, such as toilet paper, from a considerable length of roll or log according to claim 10 having A; 106A). 13. A unit for a rotor (42) of a blade (50).
(16) is movable toward the roll or log table (4, 4A, 4C) to be cut, and is provided with a device (30, 38) for moving the unit according to the progressive wear of the blade. A rotary blade cutting machine for cutting small rolls such as toilet paper from rolls or logs of significant length according to claim 12. 14. The displacement device (30, 30) is provided with the unit (16).
A rotary blade cutting machine for cutting small rolls such as toilet paper from a considerable length of roll or log according to claim 12, characterized in that it can be moved angularly by 38). 15. The discoidal core of the blade (350)
(246, 348) is angularly movable with respect to the rotor (42) and the annular cam (88) around the axis of the rotor (42), and is also a screw device (215, 211, 221) equipped with an actuator (223).
12. The substantial amount of claim 11 characterized in that it operates between the rotor (42) and the core (246, 348) to advance in the direction of the cutting edge of the blade (350A) relative to the grinding wheel. A rotary blade cutting machine that cuts small rolls such as toilet paper from rolls or logs of length. 16. The rotor (42) unit comprises a housing (1).
A rotary blade cutting machine for cutting small rolls such as toilet paper from a roll or log of significant length according to claim 15, characterized in that it has a structure (116, 116A) fixed to it. 17. A method for cutting a paper log or the like, which comprises advancing the log to perform a continuous cut by the rotating blade on the log (B), wherein the rotating blade is fixed without periodic translational motion. A method of cutting a paper log or the like, characterized in that it has a spiral blade that rotates around a fixed or substantially fixed axis. 18. The rotation axis of the blade is slightly inclined with respect to the forward direction of the roll.
A method of cutting the paper log or the like described in 7.