WO2005073114A2

WO2005073114A2 - Drives pertaining to a reel changer

Info

Publication number: WO2005073114A2
Application number: PCT/EP2005/050308
Authority: WO
Inventors: Walter Ritter; Klaus Walter RÖDER; Karl Richard RÖSCH; Hartwig Horst Trutschel
Original assignee: Koenig & Bauer Aktiengesellschaft
Priority date: 2004-01-30
Filing date: 2005-01-25
Publication date: 2005-08-11
Also published as: EP1708942A2; ATE389607T1; EP1708942B1; EP1708942B2; DE502005003377D1; DE502005000503D1; US20070170299A1; EP1790597A1; RU2006131051A; WO2005073114A3; ES2281893T3; EP1790597B1; ATE357393T1

Abstract

The invention relates to a drive pertaining to a reel changer (1), said drive comprising at least one electric motor (3) which is used to rotatably drive a supply roll (2)held in the reel changer and on which the web of material is wound. The electric motor is embodied as a synchronous motor.

Description

description

Drives of a reel changer

The invention relates to drives of a reel changer according to the preamble of claim 1, 6 or 62.

A roll changer for a printing press is known from EP 1 155 987 A2. Three-phase asynchronous motors, general three-phase or AC motors, universal motors or DC motors are provided for driving the supply rolls in this roll changer. According to one embodiment, the supply rolls can only be driven on one side of the supply roll, whereas the supply roll on the opposite side is mounted without a drive in a rotary bearing.

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

DE 94 09754 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.

Post-published EP 1 460 010 A2 describes a machine with an electric motor, which is preferably designed as a synchronous motor and is used to directly drive a winding core of a winding roll.

DE 1 599 036 describes a winding device with a segment compound expansion head known. The segments are arranged in a ring around a rotatable mandrel provided with cam surfaces and can be moved radially towards or away from the mandrel axis when axially adjusted relative to the mandrel. The segments are held in their spread position by a spring acting axially in one direction. They can be released from the spreading position by a piston which is pressurized with pressure medium and which acts against the force of the spring in the opposite direction.

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

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

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

In known drives, which drive the supply roll directly in a core drive without the interposition of a transmission or a torque transmission means, such as a belt, the torque is shaped via cones and / or transfer frictionally to the sleeve of a supply roll. The cones cannot be tightened. Clampable cones are known for reel changers with belt drives.

The invention has for its object to provide drives for a reel changer of a printing press.

The object is achieved by the features of claim 1, 6 or 62.

One advantage of the drive according to the invention is in particular that a field-weakenable synchronous motor is provided as the electric motor. Such synchronous motors have an extremely wide range of performance and can be manufactured inexpensively. Because of their motor characteristics, they are particularly well suited for driving reelstands on a printing press.

In the case of known drive devices for roll changers, drive cones are normally provided, which engage in a torque-transmitting manner on the inside of the sleeve of the supply roll. These cones are driven by the drive shaft of the electric motor provided for the drive. In order to achieve simplification and thus cost savings, it is provided according to a preferred embodiment of the drive that the drive shaft of the synchronous motor itself can be brought into engagement with the supply roll, in particular on the sleeve of the supply roll, in a torque-transmitting manner. The drive cone is arranged directly, in particular rigidly, on the rotor of the synchronous motor.

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

An advantage of the reel changer, which is only driven on one side by means of an electric motor, lies in particular in the fact that the non-driven rotary bearing can also absorb axial forces along the central axis of the supply reel, in particular during the waxing-up process. As a result, it is possible in particular to dimension the axial bearing correspondingly weaker on the side of the electric motor.

The receptacles for storing the supply roll should preferably be constructed identically on both sides of the supply roll in order to be able to save costs by using corresponding identical parts. Both receptacles should be rotatably supported, only one receptacle being driven by the synchronous motor.

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

Another advantage is, in particular, combining the previously known advantages of a tensionable recording dome with the advantages of a direct central drive of a supply roll. This reduces the component effort and the complexity of the mechanics. Overall, the device is more compact and simpler with functionality that is at least as high. On the mandrel, a fixing device can be adjusted into a working position and a rest position in order to fix the sleeve of a supply roll on the receptacle and to release it again. The drive torque is transmitted to the supply roll by a hollow shaft as a motor drive shaft, which is preferably formed in one piece with the receptacle.

The fixing device on the receptacle can be actuated by an adjusting element which is axially mounted in the hollow shaft. The hollow shaft has recesses in which one Spring device is arranged. The spring device ensures that a sleeve tension acts on the actuating element, so that the actuating element returns the fixing device to a rest position that fixes the supply roll. An actuating device is arranged on the actuating element on the side opposite the receptacle in an axial position, which displaces the actuating element into a working position which releases the supply roll. In the rest position, a decoupling between the fixed actuating device and the actuating element rotating with the hollow shaft is created by a distance between these two in order to prevent friction between the fixed actuating device and the rotating actuating element.

Conveniently, the actuating device is a membrane cylinder arranged in the extended axial direction of the actuating element. In order to be able to dimension the membrane cylinder smaller and to make the device more compact, the actuation device is a lever mechanism with a lever arm which can be actuated by a membrane cylinder which is arranged in a parallel axial direction to the electric motor.

Two receiving mandrels for guiding a supply roll may have an electric motor as drive ^", respectively. 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.

An ejector unit for stripping the roll of material from the receptacle can be arranged concentrically to the receptacle in the axial direction. To actuate the ejector unit, either the actuating element can be used, or pneumatic cylinders can be provided, which are formed parallel to the central axis. Exemplary embodiments of the invention are shown in the drawings and are described in more detail below.

Show it:

Figure 1 shows a reel changer in a partially shown cross section.

FIG. 2 shows the electric motor for driving the roll changer according to FIG. 1 in cross section;

FIG. 3 shows the side view of the receptacle of the electric motor according to FIG. 2 intended for storing a supply roll;

FIG. 4 shows the receptacle according to FIG. 3 in front view;

Fig. 5 shows a second embodiment of a drive-less rotary bearing in cross section;

6 shows a schematically illustrated reel changer;

Fig. 7 shows a hollow shaft motor schematically in cross section;

8 shows a cross section of a central drive with an actuating device which is elongated in the axial direction;

9 shows a cross section of a drive with a lever mechanism;

10 shows a cross section of a drive with an ejector unit;

11 shows a reel changer in a side view; 12 shows a schematic illustration of a central drive with a brake;

13 is a graphic representation of a drive control.

In Fig. 1, a roll changer 01, in particular a web-fed rotary printing press, for storing 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. A motor 03, in particular a synchronous motor 03, is provided for unilaterally driving the supply roll 02. 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 protruding 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 support arm 08 pivotably mounted on the roll changer 01 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 is provided on the inside of the supply roll 02 Sleeve 09 comes into engagement. For the transmission of torque 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 can transmit a torque to the supply roll 02 in a positive and frictional manner.

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. A drive-less rotary bearing 14 is provided on the support arm 12 and absorbs the weight forces of the supply roll 02 on the side opposite the synchronous motor 03. On the side of the rotary bearing 14 facing the supply roll 02, there is a receptacle 16 which is essentially identical to the one Recording 06 is formed and also comes into engagement on the inside of the sleeve 09. On the side of the rotary bearing 14 opposite the receptacle 16, a drive-free shaft 17 is provided, with which the rotary bearing 14 is supported on the support arm 12 in the direction of the longitudinal axis of the supply roll 02, so that larger axial forces can also be absorbed by the rotary bearing 14.

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

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 means of suitable machining processes. An additional cone between the sleeve 09 and the drive shaft 04 can thus be omitted.

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

A continuous standstill torque of the synchronous motor 03 is in the range from 100 Nm to 200 Nm. A maximum torque is in the range from 600 Nm to 800 Nm, in particular around 700 Nm. The synchronous motor 03 also has a theoretical idling speed in the range of 500 rpm. up to 600 rpm.

A frequency converter for speed control is connected upstream of the synchronous motor 03. In addition, a rotation angle sensor is provided on the motor 03. An axis of rotation of this angle of rotation sensor is arranged coaxially to 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 one another.

A cooling device is provided on the synchronous motor 03, 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 cooling by means of water or a cooling fluid. Several motors 03 can be connected to a common coolant supply.

In a special embodiment, the synchronous motor 03 is designed as a slip-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 supports the braking effect of the motor 03, for. B. when braking the roll of material 02 during a normal stop, especially during a quick stop or during control processes. On the other hand, the brake 24 serves as a holding brake by ∑. B. perform the adhesive preparation on the material roll 02. The brake can be regulated, in particular can be changed, controlled or, in another embodiment, can be switched on and off in a clocked manner.

The brake device 24, in particular a disc of a disc brake device, is preferably arranged concentrically to the rotor of the electric motor 03 and non-rotatably connected to it, in particular to the hollow shaft 04.

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

FIG. 5 shows a second embodiment of a drive-less rotary bearing 18 that can be used on a reel changer 01. In turn, a drive-free shaft 9 is provided to absorb axial forces, with which the rotary bearing 18 is supported on the side opposite the receptacle 16.

6 shows a schematically illustrated reel changer 01 in cross section. The drive shaft 04 is on the side facing the supply roll 02 over the housing of the synchronous motor 03, not shown, and serves as a receptacle 06; 16 for the supply roll 02. The two recordings 06; 16 of the roll changer 01 each have their own servomotor 21 for adjusting the receptacle 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. For this purpose, e.g. B. arranged a rack on the carrier of the reel changer 01, engage in each of the actuators 21 driven gears.

7 shows a further exemplary embodiment of a reel changer 01 with a motor 03, preferably a synchronous motor 03, as has already been described, shown schematically in simplified cross section.

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

By moving the actuating shaft 29, the clamping jaws 26 are either pressed outwards against the sleeve 27 or drawn inwards to the central axis. The clamping jaws 26 are retracted when a new supply roll 02 is to be taken up or the sleeve 27 of the supply roll 02 is to be released from the take-up mandrel 05 again.

The actuating shaft 29 is adjusted by an actuating device 30 at the end facing away from the arbor 05. The actuating device 30 can be any device known from the prior art, which can move a body under pressure and / or tension in at least two positions. The actuating device 30 can be a fluid-driven piston known from the prior art, which applies its compressive forces in the axial direction to the actuating shaft 29 and is therefore represented symbolically as an arrow in FIG. 7.

The hollow shaft 04 has recesses 31 in the form of an axial cylinder, on the side facing away from the holding mandrel 05, in which plate springs 32 are arranged as a spring device 32. The plate springs 32 are delimited by a piston 33 which is fixedly connected to the actuating shaft 29. The plate springs 32 are thus located 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 plate springs 32 are in a relaxed idle state, the clamping jaws 26 in the holding mandrel 05 are pushed out as far as possible. If the piston 33 is in a working state by the actuating device 30 pressed in the direction of the mandrel 05, the clamping jaws 26 move inwards to the central axis. The sleeve 27 of a supply roll 02 can then be released from the mandrel 05 and a new sleeve 27 can be received. The hollow shaft 04 is rotatably supported in the electric motor 03 via roller bearings 34.

8 shows a further embodiment of the central drive, which is provided at least on one of two holding mandrels 05 arranged in a known roll changer 01 for holding a material roll 02. 8 shows a partially cut cross section of the electric motor 03 with the hollow shaft 04. The hollow shaft

04 is rotatably supported by means of roller bearings 34 and at the same time forms the drive shaft 04 of the electric motor 03. For the sake of simplicity, the well-known mandrel is

05 not shown. The piston 33 is screwed onto the adjusting element 29. The hollow shaft 04 forms a sleeve-shaped cavity with the actuating shaft 29 and the piston 33

31, in which the plate springs 32 are arranged. It has proven to be practical to preferably use 45-57 disc springs 32. The piston 33 is pressed by an actuating device 30 in the direction of the holding mandrel 05, not shown, into a working position in order to pivot the clamping jaws 26 shown in FIG. 7 inwards. In this particular embodiment, the actuating device 30 is arranged axially in the extended direction of the actuating shaft 29. The actuating device 30 comprises a membrane cylinder 35, which is controlled pneumatically. This is advantageous because compressed air is usually present in a manufacturing environment. In the rest position, in the relaxed state of the plate spring

32, the piston 33 and a stop plunger 36 of the diaphragm cylinder 35 do not touch. Friction between the standing stop plunger 36 and the rotating piston 33 is thus avoided.

To control the synchronous motor 03, a so-called transmitter 37 is coupled to the drive shaft 04 via belts or a toothed chain. The encoder 37 detects the exact position and the speed of the electric motor 03 and the electric motor 03 controlled accordingly. For the rest, reference is expressly made to the specially shown arrangement, to the graphic representation of which it is essential.

FIG. 9 shows the central drive from FIG. 8. The main difference here is that the actuating device 30 is designed as a lever mechanism. A lever arm 38 is actuated by a membrane cylinder 35. The membrane 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. A fixed pivot point is arranged on the outer radius of the electric motor 03 at the shorter end of the lever arm 38. At the opposite end, the lever arm 38 is movable in the axial direction and is adjusted by the diaphragm cylinder 35. At the level of the movable piston 33 there is a ring or a ball which presses on the piston 33 to actuate the actuating element 29 when the lever arm 38 is pivoted from the diaphragm cylinder 35 in the axial direction to the mandrel 05. The lever or transmission ratio of the lever arm 38 here is preferably i = 3.4, d. H. the lever arm 38 actuated by the membrane cylinder 35 preferably corresponds to 440 length units, the lever arm 38 pressing on the piston 33 preferably corresponding to 130 length units. The diaphragm cylinder 35 can thus be dimensioned correspondingly smaller than in the embodiment according to FIG. 8. This lowers 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.

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 central axis of the electric motor 03 in order to form an ejector unit 40. The ejector unit 40 pushes the sleeve 27 of the supply roll 02 off the mandrel 05 when the supply roll 02 is to be replaced. The ejector unit 40 is positioned stationary on the central drive concentrically with the arbor 05 and thus does not move with the supply roll 02. 10 shows in cross section clearly the clamping jaws 26 of the holding mandrel 05, which press the sleeve 27 of the supply roll 02 radially apart slightly for better fixation. Such a firm fixation is important since a supply roll 02 can have a weight of over 1000 kg and thus high torques can occur. The associated mechanism for such clamping jaws 26 is known from the prior art and is therefore not shown. The central drive is also constructed as described in FIGS. 7 to 9.

11 shows a reel changer with two synchronous motors 03. The roll changer 01 has two pairs of receptacles 05; 06; 16 for recording 05; 06; 16 each have a supply roll 02. The drive here is also advantageously carried out by synchronous motors 03.

Both pairs of shots 05; 06; 16 can be swiveled around a common swivel axis using two reel-in supply rolls 02 or residual rolls. This pivoting movement is made possible by a servomotor 22. Each pair of shots 05; 06; 16 is only driven on one side by means of a drive motor 03. It is also possible to drive the two drive motors 03 of the two pairs of receptacles 05; 06; 16 to be arranged on the same side of the reel changer 01. The adjustment of the recording 05; 06; 16 in the axial direction of the supply roll '02 takes place via a separate servomotor 21.

The constantly changing diameter of the roll (d _Ro ιie) and the constant web tension (F _Ba hπ) bring about the relationship M _Rθ ιι _e = F _web ^* _R0 | _le / 2 the need for a wide adjustment range of the braking torque (M _Rθ ιι _e ) of the roller, which must be controlled according to the diameter or regulated via a traction controller.

In order to keep the tension of the web at the desired setpoint with high accuracy, it is necessary to determine the exact diameter of the roll. Since rollers with different starting radii are used, it makes sense to use the Determining the roll diameter automatically using the machine conductance. If the diameter is known, the relationship M _Rθ ιι _θ = Fßa _π ^* d _Rθ || _θ / 2 controlled the desired force setpoint on the web. Speed-dependent non-linearities are compensated for as well as the friction of the roller. An optional, superimposed PID controller also compensates for unknown disturbance variables as well as changes in the system variables with the help of the actual web tension value.

The torque control of the motors is realized by a digital speed controller with limiter. In the event of a web break, this speed controller with the setpoint 0 prevents the roll from accelerating uncontrollably by braking the roll to a standstill and holding it electrically.

In addition, the web tension can be reduced to a predefined value when the machine is at a standstill.

13 shows an example of a diagram for drive control.

LIST OF REFERENCE NUMBERS

01 reel changer

02 Supply roll, material roll

03 Motor, electric motor, synchronous motor, drive motor

04 drive shaft, hollow shaft

05 Pick, mandrel, mandrel

06 recording

07 axial adjustment

08 support arm

09 sleeve

10 -

11 driver element

12 support arm

13 axial adjustment

14 swivel bearings

15 -

16 recording

17 wave

18 swivel bearings

19 wave

20 - 1 servomotor 2 servomotor 3 - 4 brake device, brake 5 - 6 fixing device, clamping jaws 7 sleeve Control element, actuating shaft actuating device, ejector unit recesses, intermediate space, cavity spring device, disc spring piston roller bearing cylinder, diaphragm cylinder stop tappet sender lever arm pneumatic cylinder ejector unit

Claims

Expectations

1. Drive of a roll changer (01) with at least one electric motor (03), by means of which a material roll (02) held in the roll changer (01) on a receptacle (06) and onto which a material web is wound, can be driven in rotation, characterized in that that the electric motor (03) is designed as a synchronous motor (03).

2. Drive according to claim 1, characterized in that a drive shaft (04) of the synchronous motor (03) can be brought directly into engagement with the material roll (02) in a torque-transmitting manner.

3. Drive according to claim 2, characterized in that the drive shaft (04) has radially projecting driver elements (11) which transmit a positive and frictional torque to the material roll (02).

4. Drive according to claim 3, characterized in that the driver elements (11) are rigid, in particular in one piece, connected to the drive shaft (04).

5. Drive according to claim 1, characterized in that a drive shaft (04) of the synchronous motor (03) is designed as a hollow shaft (04).

6. Drive of a roll changer (01) with at least one electric motor (03), which has a drive shaft (04) in a coaxial central position with a receptacle (05; 06; 16) holding a material roll (02), the drive shaft (04) drives the receptacle (05; 06; 16) in rotation, characterized in that the drive shaft (04) is designed as a hollow shaft (04).

7. Drive according to claim 5 or 6, characterized in that an adjustable adjusting element (29) is arranged in the hollow shaft (04).

8. Drive according to claim 7, characterized in that the adjusting element (29) a Actuating shaft (29).

9. Drive according to claim 7 or 8, characterized in that the hollow shaft (04) has recesses (31) in which a spring device (32) is arranged which push the actuating element (29) back into a rest position.

10. Drive according to claim 9, characterized in that the spring device (32) are disc springs (32).

11. Drive according to one of claims 7 to 10, characterized in that an actuating device (30) is arranged on the adjusting element (29) in the axial position on the side opposite the receptacle (05), which displaces the adjusting element (29) into a working position ,

12. Drive according to claim 11, characterized in that the actuating device (30) has a membrane cylinder (35).

13. Drive according to claim 11, characterized in that the actuating device (30) has a lever mechanism.

14. Drive according to claim 13, characterized in that the lever mechanism of a membrane cylinder (35) in the parallel axis direction to the electric motor (03) can be actuated.

15. Drive according to one of claims 7 to 9 or 11, characterized in that the material roll (02) is fixed by adjusting the adjusting element (29) by means of a fixing device (26) on the receptacle (05).

16. Drive according to one of claims 1, 6 or 11, characterized in that in Axial direction concentric to the receptacle (05; 06) is an ejector unit (30) for stripping the material roll (02) from the receptacle (05; 06).

17. Drive according to claim 16, characterized in that the ejector unit (30) can be actuated by adjusting the adjusting element (29).

18. Drive according to claim 17, characterized in that the ejector unit (30) can be actuated by means of pneumatic cylinders arranged in the axial direction for receiving (05; 06).

19. Drive according to one of claims 5 or 6, characterized in that the hollow shaft (04) with the receptacle (05) is integrally formed.

20. Drive according to claim 6, characterized in that the electric motor (03) is a synchronous motor (03).

21. Drive according to claim 1 or 20, characterized in that the synchronous motor (03) is designed as a field-weakenable synchronous motor (03).

22. Drive according to claim 21, characterized in that the field weakening of the synchronous motor (03) is provided up to a ratio of 1:10.

23. Drive according to one of claims 1, 6 or 20, characterized in that the electric motor (03) has six poles.

24. Drive according to one of claims 1 or 20 to 22, characterized in that the synchronous motor (03) has an electrical excitation.

25. Drive according to one of claims 1 or 20 to 24, characterized in that the synchronous motor (03) has permanent excitation.

26. Drive according to one of claims 1 or 20 to 25, characterized in that the rotor of the synchronous motor (03) has poles made of permanent magnets.

27. Drive according to one of claims 1 or 20 to 26, characterized in that the synchronous motor (03) has a permanent standstill torque in the range from 100 Nm to 200 Nm.

28. Drive according to one of claims 1 or 20 to 27, characterized in that the synchronous motor (03) has a maximum torque in the range from 600 to 800 Nm, in particular approximately 700 Nm.

29. Drive according to one of claims 1 or 20 to 28, characterized in that the synchronous motor (03) has a theoretical idling speed in the range from 500 rpm to 600 rpm.

30. Drive according to one of claims 1 or 20 to 29, characterized in that the synchronous motor (03) is preceded by a frequency converter for speed control.

31. Drive according to one of claims 1 or 20 to 30, characterized in that a rotation angle sensor is provided on the synchronous motor (03).

32. Drive according to one of claims 1 or 20 to 31, characterized in that a cooling device, in particular a fan wheel, is provided on the synchronous motor (03).

33. Drive according to one of claims 1, 6 or 20 to 32, characterized in that that a braking device (24) is provided on the electric motor (03).

34. Drive according to one of claims 1, 6 or 20 to 33, characterized in that the electric motor (03) can be used as a braking device (24) in generator operation.

35. Drive according to claim 1 or 6, characterized in that an axis of rotation of a rotation angle sensor is arranged coaxially to the axis of rotation of a rotor of the electric motor (03).

36. Drive according to claim 1 or 6, characterized in that an axis of rotation of the material roll (02) and an axis of rotation of a rotor of the electric motor (03) are arranged coaxially to one another.

37. Drive according to claim 1 or 6, characterized in that an axis of rotation of the material roll (02) and an axis of rotation of a rotor of the electric motor (03) have the same speed.

38. Drive according to claim 1 or 6, characterized in that the material roll - '(02) has a sleeve (09; 27).

39. Drive according to claim 1, 6 or 38, characterized in that a receptacle (05; 06; 16) engages in each end of the two ends of the material roll (02).

40. Drive according to claim 1, 6 or 39, characterized in that two receptacles (05; 06; 16) for mounting the material roll (02) are arranged, that both receptacles (05; 06; 16) are rotatably mounted and that only one of the two receptacles (05; 16) is driven by the electric motor (03).

41. Drive according to claim 39, characterized in that the receptacles (06; 16) have radially immobile drivers, and that the receptacles (06; 16) are positively pressed into a sleeve (09) of the reeled material roll (02).

42. Drive according to claim 39 or 41, characterized in that in a drive-less rotary bearing (14; 18) axial forces along the central axis of the material roll (02) can be absorbed during the waxing-up process.

43. Drive according to claim 40, characterized in that the receptacle (06), in particular a cone, for supporting the material roll (02) on the side driven by the electric motor (03) is constructed identically to the receptacle (16) on the non-drive side.

44. Drive according to claim 42, characterized in that the rotary bearing (14, 18) with an axial adjustment (07; 13) relative to the reel changer (01) is axially adjustable in the direction of the central axis of the material roll (02).

45. Drive according to claim 44, characterized in that the axial adjustment (07; 13) is designed in the manner of a scissor lever mechanism.

46. Drive according to claim 39, characterized in that at least the distances between the bearing points of the two receptacles (06; 16) are each the same.

47. Drive according to claim 39, characterized in that one bearing point of the receptacle (06; 16) is arranged on the opposite sides of the support arm (08; 12).

48. Drive according to claim 39, characterized in that a distance between the two bearing points of the receptacle (06; 16) corresponds to the width of the support arm (08; 12).

49. Drive according to claim 39, characterized in that the receptacles (06; 16) have identical bearings.

50. Drive according to claim 39, characterized in that two pairs of receptacles (05; 06; 16) are arranged for receiving a respective material roll (02) or a residual roll.

51. Drive according to claim 50, characterized in that the two pairs of receptacles (05; 06; 16) are pivotable about a common pivot axis.

52. Drive according to claim 51, characterized in that a servomotor (22) is arranged for the pivoting movement of the two pairs of receptacles (05; 06; 16).

53. Drive according to claim 51, characterized in that each pair of receptacles (05; 06) is driven only on one side by means of an electric motor (03).

54. Drive according to claim 53, characterized in that the two drive motors (03) of the two pairs of receptacles (05; 06) are arranged on the same side of the reel changer (01).

55. Drive according to claim 50, characterized in that each receptacle (05; 06; 16) has an electric motor (03).

56. Drive according to claim 50, characterized in that each of the receptacles (05; 06; 16) of the roll changer (01) has its own servomotor (21) for adjusting the receptacle (05; 06; 16) in the axial direction of the material roll (02 ) having.

57. Drive according to claim 56, characterized in that the servomotors (21) with the receptacles (05; 06; 16) are movable.

58. Drive according to claim 57, characterized in that the servomotors (21) associated power parts or control electronics with the receptacles (05; 06; 16) can be moved.

59. Drive according to claim 1 or 6, characterized in that the drive motor (03) rewinds a free start of the material roll (02) onto the material roll (02).

60. Drive according to claim 1 or 6, characterized in that the roll changer (01) is arranged in a web-fed rotary printing press.

61. Drive according to claim 5 or 6, characterized in that the drive shaft (04) is the rotor of the electric motor (03).

62. Drive of a reel changer (01) with at least one electric motor (03), by means of which a material reel (02) held in the reel changer (01) on a receptacle (06) and onto which a material web is wound, can be driven in rotation, the receptacle has radially movable clamping jaws (26), characterized in that a membrane cylinder (35) actuating the clamping jaws (26) is arranged.

63. Drive according to claim 62, characterized in that the membrane cylinder (35) is arranged at one end of a lever arm (38) pivotably mounted at the other end.

64. Drive according to claim 63, characterized in that between the two ends of the lever arm (38) an actuating element (29) actuating the clamping jaws (26) is arranged engaging the lever arm (38).