EP1708942B1 - Reel changer - Google Patents

Abstract

The drive for the mechanism (01) to change a paper roll (02), at a printing press, has at least one electromotor (03) to rotate the roll in its holder (06). The motor is a synchronous motor, with a direct torque transmission to the paper roll through its hollow drive shaft (04) giving a positive and friction grip on the roll by a radial carrier (11) in one piece with the shaft.

Description

The invention relates to a roll changer of a web-fed rotary printing press with a drive having at least one electric motor according to the preamble of claim 1.

From EP 1 155 987 A2 a reel changer for a printing press is known. To drive the supply rolls in this reel splitter while three-phase asynchronous motors, general three-phase or AC motors, universal motors or DC motors are provided. The drive of the supply rolls can take place according to an embodiment only on one side of the supply roll, whereas the supply roll is mounted on the opposite side without drive in a rotary bearing.

From DE 102 24 839 A1 also a drive for a reel changer on a printing press is known.

DE 94 09 754 U1 discloses a winding machine for bandages and bandages, wherein the winding axis can be driven by a synchronous motor.

DE 41 26 392 C1 and DE 31 11 990 C2 describe that it is known in the field of winding devices to use synchronous motors.

The subsequently published EP 1 460 010 A2 describes a machine having an electric motor preferably designed as a synchronous motor and used for the direct drive of a winding core of a winding roll.

From DE 1 599 036 a winding device with one of segments composite spreading head known. The segments are arranged in a ring around a rotatable winding mandrel provided with cam surfaces and can be moved radially to the axis of the mandrel to or from the mandrel during axial displacement relative to the winding mandrel. The segments are held by an axially acting in one direction spring in its spread position. They are by a pressurized piston, which is effective against the force of the spring in the opposite direction, detachable from the spread position.

EP 0 981 443 B1 discloses a hollow shaft motor of a rotating cylinder or a roll in a rotary printing press.

EP 1 155 987 A2 relates to a drive for a reel changer with at least one motor as the center drive of a paper roll. The torque or the driving force of the motor is transmitted via clamping pins on the core of a paper roll.

WO 02/24564 A1 describes an actuating element for a mandrel in a reel changer. On the mandrel, a sleeve can be fixed. To fix the sleeve on the mandrel are pressed by compression springs toggle lever on provided jaws to the outside. An actuating element can be adjusted axially for actuating the clamping jaws in a hollow shaft by a fluid-driven piston, so that the clamping jaws are pressed outwards and fix the sleeve. For stripping a spent sleeve an ejector device is arranged on the mandrel. The ejector device is mounted axially displaceably on the hollow shaft and rotates together with the hollow shaft about a central axis in a housing.

The subsequently published WO 2005/056195 A1 discloses an electric motor with permanent magnets for a reel changer of a printing press.

WO 99/55533 A shows a roller or cylinder of a printing press, which is driven by an electric motor with permanent magnets.

In known drives that drive directly in a core drive the supply roll without the interposition of a transmission or a torque transmitting means, such as a belt, the torque on cones shape and / or frictionally transferred to the sleeve of a supply roll. The cones can not be stretched. Tensioning cones are known in reel changers with belt drive.

The invention has for its object to provide a reel changer of a web-fed rotary printing press with a drive with at least one electric motor.

The object is achieved by the features of claim 1.

An advantage of the drive is, in particular, that a field-weakenable synchronous motor is provided as the electric motor. Such synchronous motors have an extraordinarily wide power spectrum and can be produced inexpensively. Due to their motor characteristics, they are particularly well suited for driving reelstands on a printing machine.

In known drive means for reel changers drive cones are normally provided, which come to transmit torque on the inside of the sleeve of the supply roll. These cones are driven by the drive shaft of the drive provided for the electric motor. In order to achieve a simplification and thus a cost saving, it is provided according to a preferred embodiment of the drive, that the drive shaft of the synchronous motor itself torque-transmitting to the supply roll, in particular on the sleeve of the supply roll, can be brought into engagement. On the rotor of the synchronous motor of the drive cone is directly, in particular rigid, arranged.

The driver elements on the drive shaft, which are provided for torque transmission, should preferably rigid, in particular in one piece, be connected to the drive shaft. In this way, the otherwise required and extremely expensive adjusting mechanisms for adjusting the Save driver elements.

One advantage of the roll changer, which is driven only on one side by means of an electric motor, lies in particular in that the non-driven pivot bearing can also absorb axial forces along the center axis of the supply roll, in particular during the staking process. As a result, it is thereby possible in particular to dimension the axial bearing on the side of the electric motor correspondingly weaker.

The recordings for storage of the supply roll should preferably be designed to be identical on both sides of the supply roll in order to save costs by using the same common parts. Both recordings should be rotatably mounted, with only one recording is driven by the synchronous motor.

In a further advantageous embodiment, a free beginning of the supply roll can be rewound onto the supply roll with the aid of the synchronous motor.

Another advantage is in particular to combine the previously known advantages of a tensionable mandrel with the advantages of a direct central drive a supply roll. This reduces the component complexity and the complexity of the mechanics. The device is constructed overall more compact and easier with at least as high functionality. On the mandrel, a fixing device can be adjusted in a working position and in a rest position to fix the sleeve of a supply roll on the recording and to solve again. The drive torque is transmitted through a hollow shaft as a motor drive shaft, which is preferably formed integrally with the receptacle, to the supply roll.

The fixing device on the receptacle can be actuated by an axially mounted in the hollow shaft actuator. The hollow shaft has recesses in which a Spring device is arranged. The spring device ensures that a sleeve tension acts on the adjusting element, so that the adjusting element returns the fixing device to a rest position fixing the supply roll. On the adjusting element, an actuating device is arranged on the opposite side of the receptacle in the axial position, which displaces the actuating element into a work position which dissolves the supply roll. It is additionally provided in the rest position, a decoupling between the fixed actuator and the hollow shaft with the rotating actuator by a distance between these two to prevent friction between the fixed actuator and the rotating actuator.

Conveniently, the actuator is a diaphragm cylinder arranged in the extended axial direction of the actuator. In order to make the diaphragm cylinder smaller and make the device more compact, the actuator is a lever mechanism with a lever arm which is actuated by a diaphragm cylinder, which is arranged in a parallel axial direction to the electric motor.

Two mandrels for guiding a supply roll can each have an electric motor drive. As a result, the required power of the torque is distributed from an electric motor to two electric motors, which can be dimensioned correspondingly smaller.

Concentrically in the axial direction for receiving an ejector unit for stripping the roll of material can be arranged by the recording. For actuating the ejector unit, either the actuating element can be used or, preferably, pneumatic cylinders can be provided which are formed parallel to the central axis.

Embodiments of the invention are illustrated in the drawings and will be described in more detail below.

Fig. 1

einen Rollenwechsler im teilweise dargestellten Querschnitt;

Fig. 2

den Elektromotor zum Antrieb des Rollenwechslers gemäß Fig. 1 im Querschnitt;

Fig. 3

die zur Lagerung einer Vorratsrolle vorgesehene Aufnahme des Elektromotors gemäß Fig. 2 in seitlicher Ansicht;

Fig. 4

die Aufnahme gemäß Fig. 3 in Ansicht von vorne;

Fig. 5

eine zweite Ausführungsform eines antriebslosen Drehlagers im Querschnitt;

Fig. 6

einen schematisch dargestellten Rollenwechsler;

Fig. 7

einen Hohlwellenmotor schematisch im Querschnitt;

Fig. 8

einen Querschnitt eines Zentralantriebs mit in Achsrichtung verlängerter Betätigungsvorrichtung;

Fig. 9

einen Querschnitt eines Antriebs mit einem Hebelmechanismus;

Fig. 10

einen Querschnitt eines Antriebs mit einer Auswerfereinheit;

Fig. 11

einen Rollenwechsler in einer seitlichen Ansicht;

Fig.12

eine schematische Darstellung eines Zentralantriebs mit einer Bremse;

Fig. 13

eine grafische Darstellung einer Antriebsregelung.

Show it:

Fig. 1

a reel changer in the partially illustrated cross section;

Fig. 2

the electric motor for driving the roll changer of Figure 1 in cross section.

Fig. 3

the storage of a supply roll provided receptacle of the electric motor of Figure 2 in a side view.

Fig. 4

the recording of Figure 3 in front view.

Fig. 5

a second embodiment of a non-rotating pivot bearing in cross section;

Fig. 6

a roll changer shown schematically;

Fig. 7

a hollow shaft motor schematically in cross section;

Fig. 8

a cross section of a central drive with elongated actuator in the axial direction;

Fig. 9

a cross section of a drive with a lever mechanism;

Fig. 10

a cross section of a drive with an ejector unit;

Fig. 11

a roll changer in a side view;

Figure 12

a schematic representation of a central drive with a brake;

Fig. 13

a graphic representation of a drive control.

In Fig. 1 is a roll changer 01, in particular a web-fed rotary printing press, for supporting a supply roll 02 with a width of z. B. 300 mm to 1000 mm, on which a material web, in particular a printing material web is wound, shown in partial cross-section. For one-sided drive of the supply roll 02 is a motor 03, in particular a synchronous motor 03, is provided. The synchronous motor 03 has a drive shaft 04 which projects beyond the housing of the synchronous motor 03 on the side facing the supply roll 02. This projecting side of the drive shafts 04 serves as a receptacle 06 on which the supply roll 02 can be rotatably mounted.

By means of an axial adjustment 07, which is designed in the manner of a scissor lever mechanism, a pivotally mounted on the roll changer 01 support arm 08 can be adjusted in the direction of the longitudinal axis of the supply roll 02, so that the receptacle 06 of the synchronous motor 03 provided on the inside of the supply roll 02 Sleeve 09 comes into engagement. For torque transmission from the drive shaft 04 to the sleeve 09 radially projecting driver elements 11 are provided on the receptacle 06, which are integrally formed on the material of the drive shaft 04 and a torque form and can be frictionally transmitted to the supply roll 02.

On the opposite side of the roll changer 01, a further support arm 12 is provided, which is also adjustable by means of an axial adjustment 13 in the direction of the longitudinal axis of the supply roll 02. On the support arm 12, a non-driven pivot bearing 14 is provided, which receives the weights of the supply roll 02 on the opposite side of the synchronous motor 03 side. On the supply roll 02 facing side of the pivot bearing 14 is a receptacle 16, which is essentially identical to Recording 06 is formed and also comes on the inside of the sleeve 09 for engagement. On the opposite side of the receptacle 16 of the pivot bearing 14, a drive-less shaft 17 is provided with which the pivot bearing 14 is supported in the direction of the longitudinal axis of the supply roll 02 on the support arm 12, so that larger axial forces can be absorbed by the pivot bearing 14.

At least the distances of the bearings of the two receptacles 06; 16 are the same. In each case a bearing point of the receptacle 06; 16 is on the opposite sides of the support arm 08; 12 arranged. A distance between the two bearing points of the receptacle 06; 16 corresponds approximately to the width of the support arm 08; 12th

In Fig. 2, the structure of the synchronous motor 03 is shown enlarged in cross section. The receptacle 06 with the driver elements 11 is machined out of the drive shaft 04 by correspondingly suitable machining processes. An additional cone between sleeve 09 and drive shaft 04 can thus be omitted.

The synchronous motor 03 is designed in the manner of a field weakening synchronous motor 03, wherein it can be operated with a field weakening up to a ratio of 1:10. The motor 03 has six poles and electrical excitation. In particular, the rotor of the synchronous motor 03 has poles of permanent magnets and the stator of the synchronous motor 03 has an electrical excitation.
The permanent magnets preferably have rare earth materials.

A permanent stall torque of the synchronous motor 03 is in the range of 100 Nm to 200 Nm. A maximum torque is in the range of 600 Nm to 800 Nm, in particular at about 700 Nm. Furthermore, the synchronous motor 03 has a theoretical idling speed in the range of 500 rpm. up to 600 rpm.

The synchronous motor 03 is preceded by a frequency converter for speed control.

In addition, a rotation angle sensor is provided on the motor 03. A rotation axis of this rotation angle sensor is arranged coaxially with the axis of rotation of the rotor of the synchronous motor 03. Furthermore, a rotation axis of the supply roll 02 and a rotation axis of the rotor of the synchronous motor 03 are arranged coaxially with each other.

On the synchronous motor 03, a cooling device is provided, which is designed in the manner of a fan wheel. In generator mode, the synchronous motor 03 itself can be used as a braking device.

Another possibility for cooling the motor 03 is the cooling by means of water or a cooling fluid. Several motors 03 may be connected to a common coolant supply.

In a particular embodiment, the synchronous motor 03 is designed as a plug-on motor.

In a preferred embodiment, a braking device 24, in particular a friction brake, is arranged on the synchronous motor 03 (FIG. 12).

The braking device 24 is preferably designed as a disc brake. The brake 24 on the one hand supports the braking effect of the engine 03, z. B. when braking the roll of material 02 during normal stop, especially during rapid stop or during control operations. On the other hand, the brake 24 serves as a holding brake to z. B. to carry out the adhesive preparation on the roll of material 02. The brake is adjustable, in particular braking force variable, controllable or in another embodiment, it is clocked on and off.

The braking device 24, in particular a disc of a disc brake device, is Preferably arranged concentrically to the rotor of the electric motor 03 and rotatably connected thereto, in particular with the hollow shaft 04, connected.

In Fig. 3 and Fig. 4, the receptacle 06 is shown enlarged with the driver elements 11.

5 shows a second embodiment of a non-driven pivot bearing 18 which can be used on a roll changer 01. Again, a trailing shaft 19 is provided for the interception of axial forces, with which the pivot bearing 18 is supported on the opposite side of the receptacle 16.

Fig. 6 shows a roll splicer 01 shown schematically in cross section. The drive shaft 04 is on the supply roll 02 side directed over the housing of the synchronous motor 03, not shown, and serves as a receptacle 06; 16 for the supply roll 02. The two receptacles 06; 16 of the roll changer 01 each have their own servomotor 21 for adjusting the recording 06; 16 in the axial direction of the supply roll 02. It is advantageous if the servomotors 21 with the receptacles 06; 16 are movable. This is z. B. a rack on the carrier of the roll changer 01, engage in each of the servomotors 21 driven gears.

In Fig. 7 is a further embodiment of a reel changer 01 with a motor 03, preferably a synchronous motor 03, as already described, schematically simplified in cross section.

The electric motor 03, as a drive shaft 04, a hollow shaft 04, which is connected to a receptacle 05, preferably in one piece, and at the same time rotor of the electric motor 03 is. The mandrel 05 is a mandrel 05 and has as a fixing device 26 adjustable clamping jaws 26, which abstracted in Fig. 7 and symbolized are shown as a cone. With the jaws 26, the sleeve 27 of a supply roll 02 fix. In the hollow shaft 04 is an actuator 29. The actuator 29 is a to the central axis of the electric motor 03 axially arranged actuating shaft 29 on the side of the mandrel 05 with the clamping jaws 26 by a known from the prior art mechanism, such as in WO 02/24564 A1 discloses is connected.

By displacement of the actuating shaft 29, the clamping jaws 26 are either pressed outwardly against the sleeve 27 or retracted inwardly to the central axis. The jaws 26 are retracted when a new supply roll 02 is to be received or the sleeve 27 of the supply roll 02 is to be released from the mandrel 05 again.

The actuating shaft 29 is adjusted by an actuator 30 at the end facing away from the mandrel 05. The actuator 30 may be any device known in the art that can displace a body under pressure and / or tension in at least two positions. The actuating device 30 may be a fluid-driven piston known from the prior art, which applies its pressure forces in the axial direction to the actuating shaft 29 and is therefore shown symbolically as an arrow in FIG.

The hollow shaft 04 has recesses 31 in the form of an axial cylinder, in which disk springs 32 are arranged as a spring device 32, from the side facing away from the receiving mandrel 05. The plate springs 32 are bounded by a piston 33 which is fixedly connected to the actuating shaft 29. The disc springs 32 are thus in a sleeve-shaped intermediate space 31, which is formed on the side facing the mandrel 05 by a fixed stop in the hollow shaft 04 and the movable piston 33 on the opposite side. If the disc springs 32 are in a relaxed resting state, then the clamping jaws 26 in the receiving mandrel 05 are pressed outwards to the maximum. If the piston 33 in a working state of the actuator 30th pressed in the direction of mandrel 05, so move the jaws 26 to the central axis inwards. The sleeve 27 of a supply roll 02 can then be released from the mandrel 05 and a new sleeve 27 can be added. The hollow shaft 04 is rotatably mounted in the electric motor 03 via roller bearings 34.

FIG. 8 shows a further embodiment of the central drive, which is provided in at least one of two receiving mandrels 05 arranged to receive a roll of material 02 in a known roll changer 01. 8 shows a partially cutaway cross section of the electric motor 03 with the hollow shaft 04. The hollow shaft 04 is rotatably supported by roller bearings 34 and simultaneously forms the drive shaft 04 of the electric motor 03 from. For reasons of simplification of the known mandrel 05 is not shown. On the adjusting element 29, the piston 33 is screwed. The hollow shaft 04 forms with the actuating shaft 29 and the piston 33 has a sleeve-shaped cavity 31, in which the disc springs 32 are arranged. It has proven to be practical to use preferably 45-57 disc springs 32. The piston 33 is pressed by an actuating device 30 in the direction of the mandrel 05, not shown, in a working position to pivot the clamping jaws 26 shown in Fig. 7 inwardly. The actuating device 30 is arranged axially in the extended direction of the actuating shaft 29 in this particular embodiment. The actuating device 30 comprises a diaphragm cylinder 35, which is pneumatically controlled. This is advantageous because compressed air is usually present in a manufacturing environment. In the rest position, in the relaxed state of the plate springs 32, the piston 33 and a stopper plunger 36 of the diaphragm cylinder 35 do not touch. Thus, a friction between the stationary stopper plunger 36 and the rotating piston 33 is avoided.

To control the synchronous motor 03, a so-called encoder 37 is coupled to the drive shaft 04 via belts or a toothed chain. With the encoder 37, the exact position and the speed of the electric motor 03 is detected and the electric motor 03 controlled accordingly. Incidentally, reference is expressly made to the specifically shown arrangement, to the drawings thereof as essential.

FIG. 9 shows the central drive from FIG. 8. The essential difference here is that the actuating device 30 is designed as a lever mechanism. A lever arm 38 is actuated by a diaphragm cylinder 35. The diaphragm cylinder 35 is arranged with a parallel axis to the central axis of the electric motor 03. The lever arm 38 extends across the radius of the electric motor 03 with an extended end. At the outer radius of the electric motor 03 at the shorter end of the lever arm 38, a fixed pivot point is arranged. At the opposite end of the lever arm 38 is movable in the axial direction and is adjusted by the diaphragm cylinder 35. In height of the movable piston 33 is a ring or a ball which presses on the piston 33 for actuating the actuating element 29 when the lever arm 38 is pivoted by the diaphragm cylinder 35 in the axial direction to the mandrel 05. The lever or gear ratio of the lever arm 38 is here preferably i = 3.4, d. H. the actuated by the diaphragm cylinder 35 lever arm 38 preferably corresponds to 440 units of length, wherein the pressure on the piston 33 lever arm 38 preferably corresponds to 130 units of length. Thus, the diaphragm cylinder 35 can be dimensioned correspondingly smaller than in the embodiment of FIG. 8. This reduces the manufacturing costs and the required fluid pressure for the cylinder 35. Such an arrangement makes the central drive more compact than the embodiment according to FIG. 2.

Fig. 10 shows a third embodiment of the central drive. In this embodiment, two pneumatic cylinders 39, with a stroke of preferably 125 mm, are arranged parallel to the center axis of the electric motor 03 to form an ejector unit 40. The ejector unit 40 pushes the sleeve 27 of the supply roll 02 from the mandrel 05 when the supply roll 02 is to be replaced. The ejector unit 40 is stationarily concentric with the mandrel 05 positioned on the central drive and thus does not move with the supply roll 02 with. Fig. 10 shows in cross section clearly the jaws 26 of the mandrel 05, which press the sleeve 27 of the supply roll 02 for better fixation radially slightly apart. Such a fixed fixation is important because a supply roll 02 can have a weight of over 1000 kg and thus large torques can occur. The associated mechanism for such jaws 26 is known from the prior art and therefore not shown. The central drive is further constructed as described in FIGS. 7 to 9.

In Fig. 11, a paster with two synchronous motors 03 is shown. The paster 01 has two pairs of receptacles 05; 06; 16 for receiving 05; 06; 16 each have a supply roll 02. The drive is advantageously carried out here by synchronous motors 03rd

Both pairs of shots 05; 06; 16 are pivotable with two aufgeachsten supply rollers 02 and residual rollers about a common pivot axis. This pivoting movement is made possible by a servomotor 22. Each pair of shots 05; 06; 16 is driven only on one side by means of a drive motor 03. It is also possible, the two drive motors 03 of the two pairs of receptacles 05; 06; 16 to arrange on the same side of the roll changer 01. The adjustment of the recording 05; 06; 16 in the axial direction of the supply roll 02 via its own servomotor 21st

The constantly changing diameter of the roll (d _roll ) and the constant web tension (F _web ) bring about the relationship M _roll = F _web * d _roll / 2 the need for a wide range of the braking torque (M _roll ) of the roll, the diameter must be controlled accordingly or controlled by a draft regulator.

To keep the tension of the web at a high accuracy at the desired set point, it is necessary to determine the exact diameter of the roll. Since roles are used with different initial radii, it makes sense that Determine the roll diameter automatically using the machine master. If the diameter is known, the desired force setpoint on the path is controlled via the relationship M _roller = F _path * d _roller / 2. Speed-dependent nonlinearities are compensated, as is the friction of the roller. An optional, superimposed PID controller additionally compensates unknown disturbance variables as well as changes in the system variables with the aid of the web tension actual value.

The torque control of the motors is realized by a digital speed controller with limiter. This speed controller with the setpoint 0 prevents in the event of a web break that the roller accelerates uncontrollably by braking the roller in this case to a standstill and holding it electrically.

In addition, the web tension can be lowered to a predefined value at standstill.

FIG. 13 shows an example of a drive control diagram.

LIST OF REFERENCE NUMBERS

01

reelstands

02

Supply roll, roll of material

03

Motor, electric motor, synchronous motor, drive motor

04

Drive shaft, hollow shaft

05

Recording, mandrel, mandrel

06

admission

07

axial adjustment

08

Beam

09

shell

10

-

11

dogging

12

Beam

13

axial adjustment

14

pivot bearing

15

-

16

admission

17

wave

18

pivot bearing

19

wave

20

-

21

servomotor

22

servomotor

23

-

24

Brake device, brake

25

-

26

Fixing device, clamping jaws

27

shell

28

-

29

Control element, actuating shaft

30

Actuator, ejector unit

31

Recesses, space, cavity

32

Spring device, disc springs

33

piston

34

roller bearing

35

Cylinder, diaphragm cylinder

36

stop plunger

37

giver

38

lever arm

39

pneumatic cylinder

40

ejector

Claims (57)

1. A roll changer of a web-fed rotary printing press with a drive with at least one electric motor (03) by which a roll of material (02), which is held on a receiving means (06) in the roll changer (01) and onto which the web of material is wound, is capable of being driven in a rotating manner, wherein the electric motor (03) is constructed in the form of a synchronous motor (03), characterized in that the rotor of the synchronous motor (03) has poles comprising permanent magnets.
2. A roll changer according to Claim 1, characterized in that a drive shaft (04) of the synchronous motor (03) is capable of being brought into engagement on the roll of material (02) so as to transmit torque in a direct manner.
3. A roll changer according to Claim 2, characterized in that the drive shaft (04) has radially projecting entrainment elements (11) which transmit a torque to the roll of material (02) in a positively locking and friction-locking manner.
4. A roll changer according to Claim 3, characterized in that the entrainment elements (11) are connected to the drive shaft (04) in a rigid manner, in particular in an integral manner.
5. A roll changer according to Claim 1, characterized in that a drive shaft (04) of the synchronous motor (03) is constructed in the form of a hollow shaft (04).
6. A roll changer according to Claim 5, characterized in that a displaceable setting element (29) is arranged in the hollow shaft (04).
7. A roll changer according to Claim 6, characterized in that the setting element (29) is an actuating shaft (29).
8. A roll changer according to Claim 6 or 7, characterized in that the hollow shaft (04) has recesses (31) in which is arranged a springing apparatus (32) which presses the setting element (29) back into a rest position.
9. A roll changer according to Claim 8, characterized in that the springing apparatus (32) is in the form of cup springs.
10. A roll changer according to any one of Claims 6 to 9, characterized in that an actuating apparatus (30), which displaces the setting element (29) into an operative position, is arranged in an axial position on the setting element (29) on the side opposite the receiving means (05).
11. A roll changer according to Claim 10, characterized in that the actuating apparatus (30) has a diaphragm cylinder (35).
12. A roll changer according to Claim 10, characterized in that the actuating apparatus (30) has a lever mechanism.
13. A roll changer according to Claim 12, characterized in that the lever mechanism is capable of being actuated by a diaphragm cylinder (35) in an axial direction parallel to the electric motor (03).
14. A roll changer according to any one of Claims 6 to 8 or 10, characterized in that the roll of material (02) is fixed on the receiving means (05) by means of a fixing device (26) by the displacement of the setting element (29).
15. A roll changer according to one of Claims 1 or 10, characterized in that an ejector unit (30) for sweeping the roll of material (02) off from the receiving means (05; 06) is formed in the axial direction concentrically to the receiving means (05; 06).
16. A roll changer according to Claim 15, characterized in that the ejector unit (30) is capable of being actuated by the displacement of the setting element (29).
17. A roll changer according to Claim 16, characterized in that the ejector unit (30) is capable of being actuated by means of pneumatic cylinders arranged in the axial direction with respect to the receiving means (05; 06).
18. A roll changer according to Claim 5, characterized in that the hollow shaft (04) is made in one piece with the receiving means (05).
19. A roll changer according to Claim 1, characterized in that the synchronous motor (03) is constructed in the form of a synchronous motor (03) with a field capable of being weakened.
20. A roll changer according to Claim 19, characterized in that the weakening of the field of the synchronous motor (03) to a ratio of 1 : 10 is provided.
21. A roll changer according to Claim 1, characterized in that the electric motor (03) has six poles.
22. A roll changer according to any one of Claims 1, 19 or 20, characterized in that the synchronous motor (03) has an electric excitation.
23. A roll changer according to any one of Claims 1 or 19 to 22, characterized in that the synchronous motor (03) has a permanent excitation.
24. A roll changer according to any one of Claims 1 or 19 to 23, characterized in that the synchronous motor (03) has a continuous stoppage moment in the range of from 100 Nm to 200 Nm.
25. A roll changer according to any one of Claims 1 or 19 to 24, characterized in that the synchronous motor (03) has a maximum torque in the range of from 600 to 800 Nm, in particular approximately 700 Nm.
26. A roll changer according to any one of Claims 1 or 19 to 25, characterized in that the synchronous motor (03) has a theoretical idling rotational speed in the range of from 500 r.p.m. to 600 r.p.m.
27. A roll changer according to any one of Claims 1 or 19 to 26, characterized in that a frequency converter for regulating the rotational speed is arranged upstream of the synchronous motor (03).
28. A roll changer according to any one of Claims 1 or 19 to 27, characterized in that a rotational-angle sensor is provided on the synchronous motor (03).
29. A roll changer according to any one of Claims 1 or 19 to 28, characterized in that a cooling device, in particular a fan wheel, is provided on the synchronous motor (03).
30. A roll changer according to any one of Claims 1 or 19 to 29, characterized in that a braking device (24) is provided on the electric motor (03).
31. A roll changer according to any one of Claims 1 or 19 to 30, characterized in that the electric motor (03) is capable of being used as a braking device (24) in the generator operation.
32. A roll changer according to Claim 1, characterized in that a rotating axle of a rotational-angle sensor is arranged coaxially to the rotating axle of a rotor of the electric motor (03).
33. A roll changer according to Claim 1, characterized in that a rotating axle of the roll of material (02) and a rotating axle of a rotor of the electric motor (03) are arranged coaxially to each other.
34. A roll changer according to Claim 1, characterized in that a rotating axle of the roll of material (02) and a rotating axle of a rotor of the electric motor (03) have the same rotational speed.
35. A roll changer according to Claim 1, characterized in that the roll of material (02) has a sleeve (09; 27).
36. A roll changer according to Claim 1 or 35, characterized in that a receiving means (05; 06; 16) engages in each end of the two ends of the roll of material (02).
37. A roll changer according to Claim 1 or 36, characterized in that two receiving means (05; 06; 16) are provided for mounting the roll of material (02), the two receiving means (05; 06; 16) are mounted so as to be rotatable, and only one of the two receiving means (05; 16) is driven by the electric motor (03).
38. A roll changer according to Claim 36, characterized in that the receiving means (06; 16) have radially immovable entrainment means, and the receiving means (06; 16) are pressed in a positively locking manner into a sleeve (09) of the roll of material (02) mounted on an axle.
39. A roll changer according to Claim 36 or 38, characterized in that axial forces can be absorbed along the centre axis of the roll of material (02) during the procedure of mounting on an axle in a rotary bearing (14; 18) without a drive.
40. A roll changer according to Claim 37, characterized in that the receiving means (06), in particular a cone, for mounting the roll of material (02) is formed, on the side driven by the electric motor (03), in a structurally similar manner to the receiving means (16) on the side without a drive.
41. A roll changer according to Claim 39, characterized in that the rotary bearing (14, 18) is capable of being displaced axially in the direction of the centre axis of the roll of material (02) by an axial displacement means (07; 13) relative to the roll changer (01).
42. A roll changer according to Claim 41, characterized in that the axial displacement means (07; 13) is designed in the manner of a scissor-type lever mechanism.
43. A roll changer according to Claim 36, characterized in that at least the intervals of the bearing points of the two receiving means (06; 16) are equal in each case.
44. A roll changer according to Claim 36, characterized in that one bearing point of the receiving means (06; 16) is arranged in each case on the opposite sides of the support arm (08; 12).
45. A roll changer according to Claim 36, characterized in that an interval of the two bearing points of the receiving means (06; 16) corresponds approximately to the width of the support arm (08; 12).
46. A roll changer according to Claim 36, characterized in that the receiving means (06; 16) have structurally similar mountings.
47. A roll changer according to Claim 36, characterized in that two pairs of receiving means (05; 06; 16) are provided for receiving one roll of material (02) or one empty roll in each case.
48. A roll changer according to Claim 47, characterized in that the two pairs of receiving means (05; 06; 16) are pivotable about a common pivot axis.
49. A roll changer according to Claim 48, characterized in that a servo-motor (22) is provided for the pivoting movement of the two pairs of receiving means (05; 06; 16).
50. A roll changer according to Claim 48, characterized in that each pair of receiving means (05; 06) is driven by means of an electric motor (03) on only one side.
51. A roll changer according to Claim 50, characterized in that the two drive motors (03) of the two pairs of receiving means (05; 06) are arranged on the same side of the roll changer (01).
52. A roll changer according to Claim 47, characterized in that each receiving means (05; 06; 16) has an electric motor (03).
53. A roll changer according to Claim 47, characterized in that each of the receiving means (05; 06; 16) of the roll changer (01) has a separate servo-motor (21) for the displacement of the receiving means (05; 06; 16) in the axial direction of the roll of material (02).
54. A roll changer according to Claim 53, characterized in that the servo-motors (21) are movable with the receiving means (05; 06; 16).
55. A roll changer according to Claim 54, characterized in that power components or electronic control means associated with the servo-motors (21) are movable with the receiving means (05; 06; 16).
56. A roll changer according to Claim 1, characterized in that the drive motor (03) winds a free start of the roll of material (02) back onto the roll of material (02).
57. A roll changer according to Claim 5, characterized in that the drive shaft (04) is the rotor of the electric motor (03).

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