Methods for carrying out a flying reel change

Abstract

A flying reel change is accomplished by joining an exhausting web of a first reel that is to be replaced to a web of a fresh or replacement reel. The fresh reel is caused to run at the speed of the exhausting reel to be replaced prior to such joining. The exhausting web is joined to the fresh web once the diameter of the reel to be replaced has reached a set minimum. This minimum diameter may be fixed by the characteristics of a core for this exhausting reel.

Description

CROSS-REFERENCE TO RELATED APPLICATIONS

This patent application is the U.S. national phase, under 35 USC 371, of PCT/EP2005/052543, filed Jun. 2, 2005; published as WO 2006/029911 A1 on Mar. 23, 2006, and claiming priority to PCT/EP2004/052176, filed Sep. 15, 2004, the disclosures of which are expressly incorporated herein by reference.

FIELD OF THE INVENTION

The present invention is directed to methods for carrying out a flying roll change. An exhausting first web from a first roll of material is connected with a replacement, second web from a second roll of material. The first web is connected with the second web when the first roll of material reaches a minimum diameter.

BACKGROUND OF THE INVENTION

Roll changers are generally known in the art and are used in connection with printing presses for feeding-in the web of material which is employed as the material to be imprinted. Paper webs are used, as a rule, as the material to be imprinted. In this case, the web of material has been wound into a roll of material and is unwound from this roll of material.

So that the entire printing press need not be stopped when the web of material has run out, it is generally known to perform a so-called flying roll change. A fresh roll of material, on which appropriate web splice connections, such as, for example, adhesive spots, have been prepared, for use in the connection of the web of the fresh roll with the web of the roll of material which is running out, is clamped in the roll changer to accomplish this flying roll change. Then, in the course of the flying roll change, the fresh roll of material is accelerated to a circumferential speed which corresponds to the web speed of the drawn-in web of material being supplied from the exhausting roll of material. In the course of the actual roll change, the start of the web of the fresh roll of material is connected with the web of the running-out roll of material, and the running-out web of material is severed at essentially the same time. In this way, the start of the web of the fresh web of material is drawn into the printing press by the old web of material and a stoppage of the press is avoided.

The roll of material which is running out has a continuously changing, inherent critical resonant rpm which is a function of the remaining thickness of the running-out roll of material and of the geometric parameters of the running-out roll of material, and in particular of its width and of the diameter of the core on which the web of material has been wound.

With relatively large web widths, and in particular, with web widths of, for example, greater than 3,600 mm, and with very high web draw-off speeds, such as, for example, with web draw-off speeds of 15 m/s, and because of the generation of vibrations in the range of the inherent critical resonant rpm, it is possible for critical vibration conditions to arise in the running-off roll of material, when its remaining thickness falls below a defined value. To avoid these critical vibration states, it is therefore often necessary to reduce the web speed when the remaining thickness of the exhausting roll of material falls below a defined value. Under such conditions, this results in either that the exhausting roll of material cannot be completely used up, in order to avoid critical vibration conditions, or that the web draw-off speed must be reduced during the flying roll change roll change. Printing costs are increased, in an undesired manner, by both of these occurrences.

FR 2 076 474 shows a single receptacle for rolls of material, in which two rows of clamping jaws are arranged one behind the other.

DE 36 27 533 A1 describes a roll changer in which a support device is placed against a used-up roll.

DE 100 56 274 A1 discloses a clamping mandrel with two rows of clamping jaws arranged one behind the other. A diameter of the one row can be changed from 150 to 160 mm, and a diameter of the other row can be changed from 70 to 80 mm.

Arrangements for unwinding rolls are known from EP 0 441 152 A, EP 0 708 047 A and EP 0 413 890 A, each of which has support journals with movable clamping jaws.

U.S. Pat. No. 3,881,158 A, U.S. Pat. No. 5,360,502, U.S. Pat. No. 5,316,230, U.S. Pat. No. 3,836,089 and U.S. Pat. No. 4,100,012 describe methods for roll changing.

U.S. Pat. No. 3,516,517 A and U.S. Pat. No. 4,173,314 A describe methods in connection with a flying roll change. A roll change is performed at a remaining roll size that is fixed for a core diameter.

SUMMARY OF THE INVENTION

The present invention is directed to the object of providing methods for a flying roll change.

In accordance with the present invention, this object is attained by the provision of a first, exhausting roll of material, having a first web being withdrawn from it, and a second, fresh roll of material whose web is to be joined with the first, exhausting web, during a flying roll change. The second web is connected with the first web when the diameter of the exhausting roll of material has reached a pre-set minimum. This minimum diameter is set as a function of the properties of the roll core or as a function of properties of a receptacle of a roll changer that is intended to receive rolls of material.

The present invention relies on the basic principle of reducing a free vibration length of the unwinding roll of material in order to affect, in this way, the inherent critical resonant rpm of the unwinding roll of material in the desired manner.

In the course of the employment of a roll changer, a reduction of the free vibration length between the clamping points of the unwinding roll of material at the roll changer takes place because a support device is provided, which support device is placed against the circumferential surface of the unwinding roll of material. The free vibration length of the unwinding roll can be considerably reduced by the use of this additional support of the roll of material between the clamping points for the roll of material. If, for example, the support device is brought to rest against the circumferential surface of the roll of material exactly in the center of the roll between the clamping points, the free vibration length of the roll is halved, and the critical inherent resonant rpm is correspondingly upwardly shifted. In this case, the support device is arranged in such a way that it can be placed against the circumferential surface of the unwinding roll of material when the unwinding roll of material is arranged in the position which is provided for accomplishing the flying roll change. The critical vibrating conditions of the unwinding roll of material occur, in particular, at a relatively small remaining web thickness or roll diameter, and shortly before the exhaustion of the roll of material. A support of the unwinding roll is thus necessary, in particular, in the phase of operation which directly precedes the roll change.

It is not a significant aspect of the present invention how the support device is structurally embodied, so long as a sufficient support of the unwinding roll of material, for the reduction of the free vibration length, is assured. In accordance with a preferred embodiment of the present invention, the support device has at least one rotatably seated support belt which can be pressed against the circumferential surface of the unwinding roll of material. For example, this support belt can be seated on rollers and rotates at a velocity which is corresponding to the circumferential velocity of the unwinding roll of material.

Depending on the type of application, it can make sense to greatly reduce the free vibration length of the unwinding roll of material. This length reduction can be achieved in that several support devices can be provided, all of which are placed against the circumferential surface of the unwinding roll of material and are spaced apart and located next to each other. In this case, the free vibration length of the roll of material then corresponds only to the respective distance between two adjacent support devices, or to the distance of the first or last support device from the clamping points of the unwinding roll of material. As a result, it is therefore possible to affect the free vibration length of the unwinding roll of material in any desired way.

The support device can be provided, in a particularly easy way, if it does not have its own drive mechanism. In this case, the support device can be driven by the unwinding roll of material itself by the transfer of frictional forces from the roll of material to the support device. To the extent that frictional forces are employed for driving the support device, the support device should preferably be made of a wear-resistant material and with a relatively large coefficient of friction in the area of the contact surface between the roll of material and the support device.

Alternatively, it is also conceivable to provide a drive mechanism for the support device, by the use of which drive mechanism the support device is driven. For example, an electrical motor can be provided as this drive mechanism, by the use of which, one of the support rollers for seating the support belt is driven. It is possible, by an appropriate control of the drive mechanism, that prior to the support belt being brought into contact with the roll of material, the support belt is accelerated to a velocity which is synchronized with the circumferential velocity of the unwinding roll of material. In this case, it it possible to avoid an undesirable slippage between the support device and the circumferential surface of the unwinding roll of material, or an undesirable tearing of the web, when the belt is placed against the roll of material.

Often, the employment of the support device is desirable only during defined phases of the operation of the roll changer, and in particular, is desirable during the phase of operation of the roll changer directly prior to the flying roll change. For this reason, it is particularly advantageous if the support device is supported so that it is movable between at least two functional positions. A first functional position corresponds to an actual position of employment of the support device, in which first functional position the support device is placed against the circumferential surface of the unwinding roll of material and thus appropriately supports the roll of material. A second functional position of the support device corresponds to a position of rest, in which second functional position the support device is not in contact with the unwinding roll of material.

In principle, it makes no difference with respect to what way the support device is fixed in place, relative to the roll changer. In accordance with a first preferred embodiment of the present invention, the support device is fastened on a roll stand of the roll changer. This has the advantage that, when the roll stand is pivoted, the support device is moved along with it. The result is that no relative movement between the support device and the respectively assigned roll of material occurs, in the course of pivoting the roll stand. With this embodiment in particular, it is possible for the support device to be brought against the unwinding roll of material prior to the placement of the unwinding roll of material into the position provided for the flying roll change. During the pivoting of the roll stand, the unwinding roll of material is also supported by the support device, preferably even before the roll of material is accelerated from the stopped state. Placement of the roll of material into contact with the support belt occurs simultaneously.

To realize this embodiment of the present invention, the support device can be fastened between two support arms of the roll stand. These support arms also support the respectively assigned roll of material.

As an alternative to this first embodiment of the present invention, the support device can also be fastened on a base underneath the position of the unwinding roll of material provided for flying roll change. As a result, the support device is not an integral part of the roll changer. This alternative embodiment is of particular advantage when the support device can be lowered into the base, so that in the position of rest, in which the support device has been lowered into the base, it does not constitute an obstacle.

To be able to control or to regulate the support process of the unwinding roll of material, by employing the support device, at least one sensor, for use in measuring a support parameter, such as, for example, the actually provided support force or the belt tension of the support belt, can be provided on the support device, if required. A control device, or a control circuit can be provided, and can process the results of the measurement provided by the sensor and can control or can regulate the support device in accordance with a predetermined desired value.

The employment of the support device offers particularly beneficial advantages for use in roll changers in which rolls of material of a width of greater than or equal to 3,600 mm are processed. Such webs of material to be imprinted are used, in particular, in the course of web-fed rotogravure printing, with the use of web-fed rotogravure printing presses. The high printing speeds, which are used during such rotogravure printing, lead to the previously mentioned problems with regard to critical inherent resonant rpm.

In accordance with the method for operating the roll changer in accordance with the present invention, the support device is brought to rest against the unwinding roll of material prior to an arranging of the unwinding roll of material in a position which is suitable for a flying roll change. During the pivoting of the roll stand, for placing the roll of material into a position which is suitable for a flying roll change, the support device remains in engagement with the unwinding roll of material. This engagement assures that the unwinding roll of material is also supported during the roll stand pivoting process. As soon as the roll changer has reached its end position, in which the unwinding roll of material is placed in a position which is suitable for a flying roll change, the support device continues to remain in engagement with the unwinding roll of material until the flying roll change has been terminated and the old, exhausted roll of material can be appropriately braked.

To the free vibration lengths, or preferably in connection therewith, it is possible, in the alternative discussed above, to employ a support device. The prevention of inherently critical resonant rpm can also be improved, in a second alternative, in that the free vibration length of the unwinding roll of material can be reduced by employing longer clamping mandrels which support the roll of material.

To insure that such longer clamping mandrels provide a sufficient clamping force against the inner diameter of the core of the unwinding roll of material, at least two clamping jaws are proposed to be arranged, one behind the other, on the clamping mandrel and parallel with the longitudinal axis of the support journal. It is possible to provide a greater clamping force by the provision of this increase in the number of clamping jaws so that, in addition to a reduction in the clamping length, the quality of clamping is also achieved by increasing the clamping stiffness, due to an increase of the clamping factor, or chuck factor.

In the absence of a center support, paper widths of greater than 4,000 mm, and in particular of a width of 4,300 mm, and wound on cores or sleeves of a diameter of 150 mm, do not allow for an assured roll change at velocities of the roll of material greater than 15 m/s in connection with core constructions that are currently customary in the industry. In this case, it is possible, by using long sleeves, to achieve maximum velocities of the roll of material of 12 m/s, without the provision of a suitable support.

Several clamping jaws are preferably distributed, adjoining each other, in a row of clamping jaws, and in particular are distributed evenly spaced apart from each other, around a circumference of the support journal. In accordance with a preferred embodiment of the present invention, two rows of clamping jaws, spaced from each other in the axial direction, and with each row respectively including eight clamping jaws, are arranged in the circumferential direction on the clamping mandrel. This arrangement of clamping jaws leads to the highly secure clamping of the roll of material on the clamping mandrel.

BRIEF DESCRIPTION OF THE DRAWINGS

Preferred embodiments of the present invention are represented in the drawings and will be described in greater detail in what follows.

Shown are in:

FIG. 1, a side elevation view of a first preferred embodiment of a roll changer with a support device in accordance with the present invention, in

FIG. 2, a side elevation view of a second preferred embodiment of a roll changer with a support device in accordance with the present invention, in

FIG. 3, a perspective view of a clamping mandrel for use in a roll changer, in

FIG. 4, a cross-sectional view of a support journal, in

FIG. 5, a cross-sectional view through a roll of material with support journals, in

FIG. 6, a schematic side elevation view of a scissor-type lifting table supporting a fresh roll of material, in

FIG. 7, a schematic side elevation view of a scissor-type lifting table with a support device supporting an unwinding roll of material, and in

FIG. 8, a schematic plan view of a roll changer in accordance with the present invention.

DESCRIPTION OF THE PREFERRED EMBODIMENTS

A first preferred embodiment of a roll changer 01 for use in supplying a web 02 of material, and in particular for use in supplying a paper web, and which is usable in a non-represented printing press, is schematically represented in FIG. 1. A roll stand 04, which can be pivoted around a pivot shaft 03, is provided on the roll changer 01. Roll stand 04 is constituted by two spaced support arms, which are located one behind the other in the drawing plane shown in FIG. 1. Receptacles or roll end support journals 05, which may be for example configured as clamping mandrels 05, and which are located opposite each other, are fastened to the free ends of the respective two spaced support arms of the roll stand 04, and between which clamping mandrels or roll end support journals 05, rolls 06, 07 can be clamped to the roll changer 01, as is depicted in FIG. 5.

In the operational configuration represented in FIG. 1, an unwinding or exhausting, first roll 06 of material and a fresh or second roll 07 of material, which has been prepared for a flying roll change, are clamped to the roll changer 01. The roll stand 04 had previously been pivoted into the position represented in FIG. 1, so that the unwinding or exhausting, first roll of material 06 takes up a position that is required for accomplishing a flying roll change. For use in supporting the fresh roll 07 of material and for transmitting the pressure forces, such as acceleration and braking stop forces to the fresh roll 07 in the loading position, a first or fresh roll support belt 08 is pushed, from below, against the circumference of the fresh roll 07 of material.

As soon as the roll stand 04 has reached the position represented in FIG. 1, and in preparation for a roll change, an exhausting roll support device 11, which is fastened on a base 09 underneath the unwinding or exhausting roll 06 of material, is extended upward until a second or exhausting roll support belt 12, which is seated on rollers 13, comes into contact with the circumference of the unwinding or exhausting, first roll 06 of material. Pneumatic actuating cylinders 14 are provided for use in extending and retracting the support device 11 with respect to the exhausting roll of material 06. The second, exhausting roll support belt 12 is synchronized with the velocity of the paper web by the use of a frequency-regulated rotary current motor which is not specifically depicted in the drawings. Tearing of the web 02, during contact between the web 02 and the belt 12 is avoided by the provision of this frequency-regulated rotary current motor.

The free vibration length of the exhausting roll 06 of material, between the receptacles 05, is reduced by the pressure of the support belt 12 which is exerted against the circumference of the unwinding, exhausting roll 06 of material. The result is that the critical inherent resonant rpm of the roll 06 of material are shifted into a non-critical rpm range.

A second preferred embodiment of a roll changer 16, in accordance with the present invention, is represented in FIG. 2. As previously described in connection with FIG. 1, a web 02 of material, a pivot shaft 03, a roll stand 04, the receptacles or support journals 05, the unwinding or exhausting roll 06 of material, the fresh roll 07 of material and a support belt 08 for support and for transfer of the driving forces of the fresh roll 07 of material are again provided on the roll changer 16.

In a structure which is different from the roll changer 01 depicted in FIG. 1, two spaced support devices 17 and 18 have been provided on the roll changer 16 and are assigned to the left, or to the right clamping location, respectively at the roll stand 04. As indicated in dashed lines in FIG. 2, by the alternative depictions of the support device 17, the support devices 17 and 18 can each be displaced in linear guides 19 and can each be matched in this way to the changing diameters of the rolls 06, 07, respectively of material and can track their positions.

Support belts 22 are provided on each of the respective support devices 17 and 18, which support belts can be brought to rest against the circumference of the respective roll 06, 07 to be supported. Pneumatic actuating cylinders 21 are provided for use in bringing the support belts 22 into and out of contact with their respective rolls 06, 07, and by whose extension and retraction the seating structure of the support belts 22 can be pivoted.

The following procedure is followed prior to a flying roll change by the roll changer 16. Initially, the unwinding, exhausting first roll 06 of material is in its so-called run-off position and is located on the right side of the pivot shaft 03, which positioning is not represented in FIG. 2. In the course of the continuing printing process, the unwinding roll 06 of material is unwound in this position until its diameter falls below a defined roll diameter, or falls below a defined remaining minimum thickness of the roll 06 of material 02. When this defined remaining minimum thickness is reached or is exceeded, the actuating cylinder 21 is extended and the support belt 22 of the support device 17 is brought into contact with the circumference of the roll 06 of material 02. In this process the inherent critical resonant rpm of the roll 06 of material are shifted into a non-critical rpm range, so that the web 02 of material can be pulled off the exhausting roll 06 at an unchanged speed.

As soon as the exhausting roll 06 of material has been unwound to a remaining thickness, which remaining thickness makes a roll change unavoidable, the exhausting roll 06 of material 02 is pivoted into the position to the left of the pivot shaft 03 by pivoting the roll stand 04, such as is represented in FIG. 2. The support belt 22 continues to rest against the circumference of the roll 06 of material 02 even during the pivot movement, and supports the exhausting roll 06 of material 02 in this way.

After the exhausting roll 06 of material 02 has reached a gluing position, or loading position, to the left of the pivot shaft 03, as represented in FIG. 2, and the fresh roll 07 of material, which has previously been prepared for the roll change, has been clamped in the roll changer 16, a flying roll change between the exhausting roll 06 of material and the fresh roll 07 of material can be performed in a generally known manner. A reduction of the draw-off speed of the web 02 of material is not required in this process, because the critical resonant rpm of the roll 06 of material have been shifted into a non-critical range as a result of the employment of the support device 17.

Because the support belt 22 of the respective support device 17, 18 can be placed against the fresh roll 07 of material while it is still stopped, and therefore rests against it during acceleration of the fresh roll 07, the support device 17, 18 can be embodied without a drive motor.

FIG. 3 shows a material roll, end-receiving receptacle 05 which may be configured, for example, as a clamping mandrel 05, in connection with the roll changers 01 or 16 shown in FIGS. 1 and 21, respectively. A support journal 24 is provided on the clamping mandrel 05, and whose exterior circumference comes into contact with the interior circumference of a roll 06, 07 of material, and in particular with an inner circumference of a core 10, such as, for example, a paper core 10, as shown in FIG. 5. To provide a connection, which is fixed against relative rotation, of the roll 06, 07 of material with the clamping mandrels 15 by the provision of a positive and non-positive connection, a plurality of clamping jaws 26, with there being at least four such clamping jaws 26 in particular, are provided in the circumferential direction of the support journals 24. Since each of the support journals 24 has a large insertion depth, by the use of which large insertion depth the free vibration length between the clamping points can be reduced, at least two clamping jaws 26 are arranged one behind the other and are aligned with each other in the direction of the axial or the longitudinal direction of the support journals 24 as seen in FIGS. 3, 4 and 5. Several adjoining clamping jaws 26 are distributed along the circumference of the support journal 24, and are evenly spaced apart, in particular. In this case, the clamping jaws 26 which are arranged next to each other, form ring-shaped rows 27 or 28 of clamping jaws, with each such row 27 or 28 containing eight such clamping jaws 26. The support journal 24 of the clamping mandrel 05 has an exterior diameter D24, as shown in FIG. 4, of approximately 150 mm.

A clamping mandrel 05, including the support journal 24, is shown in cross section in FIG. 4. A length l24 of the support journal 24 is at least 250 mm in the axial direction of the support journal 24. Lengths l24 of the support journal 24 of at least 300 mm, and in particular of at least 330 mm, are advantageous. A length l26 of each of the clamping jaws 26, in the axial direction of the support journal 24, is at least 80 mm, and in particular is at least 95 mm. A sum of the lengths l26 of the clamping jaws 26 in the axial direction of the support journals 24 is preferably at least 300 mm, and in particular is 340 mm. In a further embodiment of the present invention, the sum of the lengths l26 of the clamping jaws 26 is 380 mm. A diameter D24 of the support journal 24 is greater than 140 mm, and in particular it is between 145 mm and 155 mm. A diameter D24 between 148 mm and 152 mm is particularly advantageous.

FIG. 5 shows a roll 06, 07 supported by the two axially spaced clamping mandrels or receptacles 05, with each such roll 06, 07 having a core 10, such as is preferably used in the described roll changer.

In the depiction of FIG. 5, the length l10 of the core 10 of the roll 06, 07 resting on the clamping jaws 26 of the support journal 24 is more than 4000 mm, and in particular is more than 4200 mm. A wall thickness b10 of the core 10 is more than 10 mm, and in particular, it is greater than 15 mm. A thickness b10 of the core wall of greater than 17 mm, and in particular of greater than 20 mm, is particularly advantageous. An interior diameter d10 of the core 10 is 150.2+0.2 mm.

Alternatively, or as an aid to the previously discussed steps for reducing the free clamping length of the roll of material, a setting of the web speed and/or of the diameter of the remaining or exhausting roll 06 during the flying roll change can take place for performing the flying roll change.

As previously described, in the course of a flying roll change, a first web 02 of material of a roll 06, of material, which first web 02 of material runs at a first web speed, is connected with a second web 29 of material of a fresh roll 07 of material, which second web 29 of material runs at a second web speed. Prior to connecting the first web 02 of material with the second web 29 of material, the first web speed can be reduced to a second web speed, so that during the connection of the first web 02 to the second web 29, during the flying roll change, the first web 02 of material has a first web speed which is the same as the second web speed.

Prior to connecting the webs 02, 29 of material, it is possible to set a minimum diameter of the remaining or exhausting roll 06 as a function of the width bO2 of the web 02, 29 of material, which minimum diameter of the exhausting roll 06 determines the latest time at what time the two webs 02, 29 are connected with each other.

In another embodiment of the present invention, the second web speed, which is predetermined during the connecting process, or the minimum diameter of the remaining roll 06, is set as a function of properties of the material of the core 10 of a web 06, 07 of material.

In another embodiment of the present invention, geometric dimensions relating to the core 10 of the web 06, 07 of material, such as, for example, the size of the interior diameter d10 of the core 10, or the wall thickness b10 of the core 10, or the modulus of elasticity of the material which constitutes the core 10, determine the reduced web speed or the minimum diameter of the remaining roll 06 of the first roll 02 of material during connection.

In a further preferred embodiment of the present invention, the second web speed, which is predetermined during the connecting process, or by the minimum diameter of the remaining roll 06, is set by the use of the geometric dimensions of the receptacle 10, and in particular of the support journal 24. The reduced web speed can also be set as a function of the length l26 of the clamping jaws 26 of the support journal 24.

The reduction of the web speed and/or the setting of the minimal diameter of the remaining roll 06 is controlled, together with the connecting process, by the use of a suitable program.

Equipping the roll stand 04 with the roll 06, 07 of material can take place with the aid of a wheeled cart 31, such as, for example, with the aid of a scissor-type lifting table 31, as is represented in FIGS. 6 and 7. Wheels 33 have been attached to the wheeled cart 31, by the use of which a horizontal movement of the wheeled cart 31 is possible. A vertical movement is also possible. A support device 11, with a support belt 12, which support device 11 is pivotably fastened on the scissor-type lifting table 31, is arranged on the wheeled cart 31, as seen in FIG. 7. This support device 11 shown in FIG. 7 is substantially the same as the previously described support device 11 shown in FIG. 1. The support device 11 is motor-driven, such as, for example, by the utilization of an AC motor, which AC motor accelerates the support belt 12 of the support device 11 to the web speed. The support device 11 then places belt 12 against the unwinding roll 07 of material by the of a hydraulic device, such as depicted schematically at 14. Braking of the roll 07 of material is also aided by this motor which drives the support belt 12, because the motor of the support belt 12 of the support device 11, together with the shaft motor of the roll stand 04, both brake along the same torque curve until the remaining roll 07 comes to a stop.

The roll 06, 07 of material is transported to the roll changer 01 by a transport carriage 32 which may be pulled by a chain. The transport carriage 32, with the roll 06 of material, enters the scissor-type lifting table 31 at ground level. Wheels 34 have been attached to the transport carriage 32, by the use of which, a movement of the transport carriage 32 inside the scissor-type lifting table 31 is made possible. The scissor-type lifting table 31 moves into a centered position and lifts the roll 06, 07 of material approximately 1600 mm above the ground. The centered roll 06, 07 of material is subsequently placed into a position wherein it can be placed on the shaft of the roll stand 04, as seen in FIG. 6. Upon reaching this position, the signal “advance sleeve” is transmitted to the roll stand 04. The receptacles or clamping mandrels 05, with their associated support journals 24, are moved into the roll 06 of material. Once the receptacles or clamping mandrels 05, with their associated support journals 24, have been moved into the roll 06, 07 of material and specifically into the core 10 of the roll of material 06, 07, and the clamping jaws 26 have been spread open in the interior of the core 10, the scissor-type lifting table 31 is lowered upon the signal “roll placed on the shaft” and is moved into its initial position.

During the roll change, after the rotation of the roll stand 04, the support device 11 moves against the unwinding roll 07 of material, into a support position and stabilizes the unwinding roll 07 at its center. Upon the command “advance cutter” the unwinding web 29 of material is cut off the roll 07 of material and the now exhausted roll 07 of material is stopped via the shaft motor of the roll stand 04. As previously described, the braking process of the now exhausted roll 07 of material is supported by the support device 11 of the scissor-type lifting table 31. The support belt 12 pivots away from the now exhausted roll 07 of material, and the scissor-type lifting table 31 moves into its loading position in order to load a fresh roll 07 of material.

The core 10 of the now exhausted remaining roll 07 is removed by a core crane, and in particular a clamping crane with a trolley. The removed roll 07 is conveyed to a carriage for disposal.

A schematic plan view of the roll changer with various stages of the roll supply is represented in FIG. 8.

While preferred embodiments of methods for carrying out a flying reel change, in accordance with the present invention have been set forth fully and completely hereinabove, it will be apparent to one of skill in the art that various changes in, for example, the specific structure of the printing press, the type of printing being accomplished, and the like could be made without departing from the true spirit and scope of the present invention which is accordingly to be limited only by the appended claims.

Claims

1-49. (canceled)

50. A method for performing a flying roll change including:

providing a first, exhausting roll of material having a first web of material;

providing a second, fresh roll of material having a second web of material;

supporting said first roll of material for rotation at a first web speed;

supporting said second roll of material for rotation at a second web speed;

determining a minimum diameter of said first roll of material; and

connecting said first web and said second web of material when said first roll of material reaches said minimum diameter.

51. The method of claim 50 further including providing a material core for at least said first roll of material and determining said minimum diameter as a function of properties of said material core.

52. The method of claim 50 further including providing a roll changer having material roll clamping mandrels for supporting said first and second rolls of material and determining said minimum diameter as a function of properties of said roll clamping mandrels for said first roll of material.

53. The method of claim 50 further including determining said minimum diameter of said first roll as a function of a width of said first web of material.

54. The method of claim 50 further including providing said first web speed greater than said second web speed, reducing said first web speed to said second web speed and connecting said first web and said second web at said reduced first web speed.

55. The method of claim 54 further including providing a program and using said program for reducing said first web speed and connecting said first web to said second web.

56. The method of claim 50 further including providing a program and using said program for connecting said first web and said second web.

57. The method of claim 54 further including setting said second web speed as a function of a width of said first and second webs of material.

58. The method of claim 51 further including setting said second web speed during said connecting of said first and second webs of material as a function of said properties of said material core.

59. The method of claim 52 further including providing a material core for at least said first roll of material and determining said minimum diameter also as a function of properties of said material core.

60. The method of claim 54 further including providing a material core for at least said first roll of material and setting said second web speed during said connecting process as a function of geometric dimensions of said core.

61. The method of claim 51 further including determining said minimum diameter of said first roll of material as a function of geometric properties of said material core.

62. The method of claim 60 further including setting said second web speed as a function of an interior diameter of said material core.

63. The method of claim 61 further including determining said minimum diameter as a function of an interior diameter of said core.

64. The method of claim 60 further including setting said second web speed as a function of a wall thickness of said core.

65. The method of claim 61 further including determining said minimum diameter as a function of a wall thickness of said material core.

66. The method of claim 51 further including determining said minimum diameter as a function of a modulus of elasticity of said material core.

67. The method of claim 52 further including setting said second web speed during said connecting of said first web and said second web as a function of geometric characteristics of said roll clamping mandrels.

68. The method of claim 52 further including determining said minimum diameter as a function of lengths of clamping jaws on said clamping mandrels.

69. A roll changer usable for feeding a web of material comprising:

a first roll support usable to rotatably support a first, exhausting roll of material having a first web of material;

a second roll support usable to rotatably support a second, fresh roll of material having a second web of material;

first and second roll support receptacles on said first roll support;

third and fourth roll support receptacles on said second roll support;

a support journal on each said support receptacle; and

clamping jaws on each said support journal.

70. The roll changer of claim 69 wherein said support journals on each of said first and second roll supports have four of said clamping jaws arranged in an axial direction of said support journals.

71. The roll changer of claim 69 wherein an axial length of each said support journal is at least 250 mm.

72. The roll changer of claim 69 wherein a sum of lengths of said clamping jaws on each said support journal, in an axial direction of said support journals is at least 300 mm.

73. The roll changer of claim 69 wherein each said support journal has at least two of said clamping jaws arranged in an axial direction of each said support journal.

74. The roll changer of claim 71 wherein said support journals have at least four of said clamping jaws arranged in an axial direction of said support journals.

75. The roll changer of claim 71 wherein said axial length of each said support journal is at least 300 mm.

76. The roll changer of claim 75 wherein said length of each said support journal is at least 330 mm.

77. The roll changer of claim 69 wherein a length of each said clamping jaw, in an axial direction of each said support journal is at least 80 mm.

78. The roll changer of claim 77 wherein said length of each said clamping jaw is at least 95 mm.

79. The roll changer of claim 69 wherein an axial length of said clamping jaws in an axial direction of each said support journal is at least 340 mm.

80. The roll changer of claim 79 wherein said axial length of said clamping jaws is at least 380 mm.

81. The roll changer of claim 69 further including a plurality of said clamping jaws on each said support journal and defining a circumferential, evenly spaced row on a circumference of said support journal.

82. The roll changer of claim 69 wherein ones of said clamping jaws on each said support journal are axially aligned.

83. The roll changer of claim 81 further including two rows of said clamping jaws on each said support journal.

84. The roll changer of claim 69 wherein said clamping jaws on each said support journal are adapted to receive a core of one of said first and second rolls of material.

85. The roll changer of claim 84 wherein a length of each said core is greater than 4000 mm.

86. The roll changer of claim 85 wherein said length of each said core is greater than 4200 mm.

87. The roll changer of claim 84 wherein each said core has a wall thickness greater than 10 mm.

88. The roll changer of claim 87 wherein said core wall thickness is greater than 15 mm.

89. The roll changer of claim 87 wherein said core wall thickness is greater than 17 mm.

90. The roll changer of claim 87 wherein said core wall thickness is greater than 20 mm.

91. The roll changer of claim 84 wherein an interior diameter of said core is 150.2 mm±0.2 mm.

92. The roll changer of claim 69 wherein said roll changer is adapted to perform a flying roll change between said first web of material and said second web of material.

93. The roll changer of claim 69 wherein each of said support journals has a diameter of greater than 140 mm.

94. The roll changer of claim 93 wherein each said support journal diameter is between 145 mm and 155 mm.

95. The roll changer of claim 93 wherein each said support journal diameter is between 148 mm and 152 mm.

96. The roll changer of claim 69 wherein said roll changer is located before, in a direction of web travel, a web-fed rotogravure printing press.