EP1218186A1

EP1218186A1 - Cylinder of a rotation printing machine

Info

Publication number: EP1218186A1
Application number: EP00979400A
Authority: EP
Inventors: Bertram Wilhelm-Georg Dauner
Original assignee: Koenig and Bauer AG
Current assignee: Koenig and Bauer AG
Priority date: 1999-10-08
Filing date: 2000-10-05
Publication date: 2002-07-03
Anticipated expiration: 2020-10-05
Also published as: DE50004517D1; US6688223B1; JP2003511278A; ATE234728T1; ES2208436T3; US20040144270A1; EP1295719A3; JP3884957B2; WO2001026903A1; EP1218187A1; US6868782B2; US6810800B1; ATE254536T1; DE50001517D1; EP1218187B1; WO2001026902A1; EP1218186B1; EP1295719A2

Abstract

The cylinder has a base (2) and an external body (3). A tempering medium flows between the two bodies. The circumference of the base body has a multiple helical channel (17). The external body, which feeds the printing ink, is not self-supporting over its length but is supported by the base body. The multiple helical channel is formed in the outside of the base body as a screw-shaped groove with projections (26), which support the external body.

Description

description

Cylinder of a rotary printing press

The invention relates to a cylinder according to the preamble of claims 1 or 3.

DE 197 12 446 A1 discloses a temperature-controllable cylinder for a rotary printing press, in which a heat exchanger consisting of a plurality of tubes is arranged in a cavity of the cylinder and is in turn surrounded by a heat-transferring stationary liquid.

EP 05 57 245 A1 discloses a temperature-controllable forme cylinder with an axially extending clamping channel on the lateral surface, wherein axially extending channels are worked into the cylinder in the vicinity of the periphery, through which coolant flows.

EP 07 33 478 B1 shows a friction roller designed as a tube, with coolant flowing through the entire cavity between a coolant-carrying, axially extending line and the tube.

From DE-PS 929 830 a temperature-controlled double-jacket drying cylinder is known. Steam flows in the space between an outer jacket and an inner jacket, in which helical webs are inserted.

The invention has for its object to provide a cylinder of a rotary printing press.

The object is achieved by the features of claims 1 or 3.

The advantages that can be achieved with the invention consist in particular in that a temperature-controllable cylinder can be produced inexpensively from simple components. Doing so achieves a temperature which can be selected almost uniformly over the entire lateral surface of the cylinder. A temperature profile which fluctuates or is uneven in the circumferential direction, as can occur, for example, in the case of individual axially extending channels and / or in the case of wall thicknesses which are too small in comparison with the distance between the channels, is avoided.

In an advantageous embodiment, a chamber carrying a temperature control medium on the inside of the cylinder jacket is dimensioned in the radial direction of the cylinder such that a forced flow also takes place directly on the jacket surface.

A small wall thickness of an outer body separating the outer surface and the tempering medium, for example for inking rollers, in particular anilox or anilox rollers, or for form, transmission or satellite cylinders without a radially reaching inside of the outer surface is particularly advantageous with regard to the fastest possible reaction time of the temperature control Device for fastening lifts, such as tensioning or clamping channels.

A wall thickness of an outer body for a temperature-controlled forme or transfer cylinder, which has one or more clamping or clamping channels on its outer surface, is so large in a preferred embodiment that the clamping channel comes to lie completely within the wall.

Uniform tempering in the circumferential and axial directions is achieved by means of the tempering medium flowing in the axial direction over the entire circumference through a narrow gap between the outer body and the cylinder base body.

In a further advantageous embodiment, an even more directional flow is generated by means of a helical groove located on the outer surface of the base body.

Cooling by means of is also advantageous, in particular for anilox or anilox rollers an above-mentioned helical channel, the outer body being supported on the webs and thus being made with thin walls.

Embodiments of the invention are shown in the drawings and are described in more detail below.

Show it:

Fig. 1 shows a longitudinal section through a temperature-controlled, a device for

Fastening an elevator cylinder with helical channel;

FIG. 2 shows a cross section through a temperature-controlled cylinder according to FIG. 3;

Fig. 3 shows a longitudinal section through a temperature-controlled, a device for

Fastening an elevator cylinder with a gap between the base body and the outer body;

4 shows a longitudinal section through a temperature-controlled, thin-walled cylinder with a helically extending channel;

FIG. 5 shows a cross section through a temperature-controlled cylinder according to FIG. 4;

Fig. 6 shows a longitudinal section through a temperature-controlled cylinder with a gap between the base body and the outer body.

A temperature-controlled cylinder 01 of a printing press, in particular a rotary printing press, has a z. B. tubular or solid cylinder body 02, which of a cylinder outer body 03 with a circular cross section, for. B. is surrounded by a tube 03. The cylinder base body 02 is in each case with a shaft journal 04; 06 firmly connected, which by means of bearings 07 in side frames 08; 09 are rotatably mounted. It is possible to use one of the shaft journals 04; 06, e.g. B. the right shaft journal 06, with a drive motor, not shown, fixed to the frame or a drive wheel.

The other shaft journal 04 has an axial bore 11, which a pipe 12 as a feed line 12 for a liquid or gaseous temperature control medium, such as. B. CO ₂ , water, oil, etc., takes up. In an advantageous embodiment, the axial bore 11 of the shaft journal 04 has an inner diameter d11, which is larger than an outer diameter d12 of the pipeline 12. Thus, in the area of the shaft journal 04 and around the pipeline 12, a discharge line 13 with an annular cross section remains open, through which the Temperature control medium leaves the cylinder 01 again via the shaft journal 04. The pipeline 12 for supplying the temperature control medium runs from the left shaft journal 04 almost axially through the cylinder body 02 to the right shaft journal 06 and opens into radially extending bores 14. The bores 14 open into a distribution space 16 which extends around the entire circumference on the inside of the outer cylinder body 03 extends. The temperature control medium flows from the distributor space 16 through at least one channel 17 arranged between the cylinder base body 02 and the outer cylinder body 03 in the axial direction A to the left-hand shaft journal 04, where it opens into a collecting space 18 and reaches the annular discharge line 13 via radially extending bores 19.

The supply line 12 and discharge line 13 are connected to the flow and return of a temperature control device, not shown.

In an embodiment variant, not shown, it is provided that the supply and the discharge of the temperature medium are separated from each other via a respective shaft journal 04; 06 to make.

In a first embodiment (Fig. 1), the cylinder 01 is designed as a form 01 or transfer cylinder 01, which on a lateral surface 21 of the Outer cylinder body 03 at least one fastening device 22 extending axially to the cylinder 01 for fastening an elevator, such as a printing form or a rubber blanket, e.g. B. has a clamping channel 22, a near-surface magnet or other means. A wall thickness h03 of the outer cylinder body 03 is greater than a depth h22 of the tensioning channel 22, so that a surface 23 on the inside of the outer cylinder body 03 is undisturbed and circular, which enables a cost-effective design and above all a uniform temperature control. The wall thickness h03 is z. B. between 40 and 70 mm, in particular between 55 and 65 mm, the depth h22 of the tensioning channel 22 being between 20 and 45 mm. 1 and 2, two clamping channels 22 are provided in the circumferential direction of the cylinder 01, but the upper clamping channel 22 is only indicated for the sake of clarity.

In this exemplary embodiment, the channel 17 is designed as a helical groove 17 formed in the axial direction A on a circumference 24 of the cylinder base body 02. This spiral groove 17 of a width b17 and a depth h17 is covered by means of the outer cylinder body 03, for example by shrinking, the surface 23 of the outer cylinder body 03 on a protrusion 26 forming the groove 17, for. B. a web 26 with a width b26 rests.

The groove 17 is at its beginning 27 with the distribution space 16 and at its end 28 with the collecting space 18. Distribution space 16 and collection space 18 are each, for example, as an annular groove 16; 18 executed, each of which has a shoulder on the circumference of the region of the shaft journal 04; 06 and an end face of the cylinder body 02 is formed, and is also covered by the outer cylinder body 03.

In the case of a forme cylinder 01, a diameter of the forme cylinder 01 is twice the circumference, ie two print formats in the circumferential direction, e.g. B. between 320 and 400 mm, in particular 360 to 380 mm. The depth h17 and width b17 of the groove 17 and the width b26 of the web 26 and the number of channels 17 determine the flow rate per unit of time and alternately the required pressure and the slope of the helical groove 17 and thus the temperature control behavior.

The circumference 24 of the cylinder body 02 has several, z. B. four or eight, grooves 17 each offset by 90 ° or 45 ° in the circumferential direction starts 27 and ends 28 in the distribution space 16 and the collecting space 18. A multi-course, e.g. B. a four- or eight-way groove 17 thus has an increased overall cross-section Q, d. H. the sum of the cross sections of the channels 17, and a larger slope S, and thus also a shorter flow path and a smaller pressure loss.

In the example, the circumference 24 of the cylinder base body 02 has a four-course channel 17, the width b17 of the groove 17 in each case between 10 and 20 mm, for. B. 15 mm, and the width b26 of the web 26 each between 3 and 7 mm, z. B. 5 mm. The depth h17 of the channel 17 is in each case 10 to 15 mm, for example 12 mm. The four-speed channel 17 thus has a slope S of z. B. 52 to 108 mm, in particular from 80 mm.

A total cross section Q for the flow of the temperature control medium advantageously results in 600 to 800 mm ² . When increasing the wall thickness h03 of the outer cylinder body 03 while maintaining the cylinder diameter d01 and reducing an inner radius r17 of the helical groove 17, the depth h17 of the groove 17 is to be increased in the same ratio as the inner radius r17 of the groove 17 is reduced, so that the total cross section Q is at least in the order of magnitude, e.g. B. remains greater than or equal to 710 mm ² . A heat supply or dissipation of a constantly large lateral surface 21 of the forme cylinder 01 is thus ensured. To determine the overall cross section Q, the inner radius r17 should be used for depths h17 that are correspondingly small compared to the inner radius r17, otherwise the inner radius r17 plus half the depth h17, as usual. The relationship between tempering jacket surface 21 and the total cross section Q is z. B. between 1000 and 1800 mm ² .

In a second exemplary embodiment (FIG. 3) for a forme cylinder 01, the channel 17 is not designed as a spiral groove 17, but rather as an open gap 17 between the basic cylinder body 02 and the outer cylinder body 03 with an annular, clear profile. The temperature control medium is supplied and removed in the same or a similar manner as in the first exemplary embodiment (FIG. 1). Instead of the radial bores 14, the shaft journal 04; 06 is made in several pieces and thus allows the temperature control medium to pass from the supply line 12 into the distribution space 16 or from the collecting space 18 to the discharge line 13. In the exemplary embodiment, the supply line 12 is made in two or four parts, with a pipe 12 penetrating the shaft journal 04 into a through the pipeline leading to the cylinder body 02 opens.

The clear width h17 of the gap 17 together with an inner radius r17 from the axis of rotation of the cylinder 01 on which the gap 17 is arranged determines the flow conditions and thus also the temperature control behavior. A clearance that is too small increases the required pressure or reduces the flow rate, while a clearance that is too large does not result in a safe directional flow directly on the face 23 of the outer cylinder body 03 due to high centrifugal forces and friction in the area 23 during the rotation of the cylinder can result.

In an advantageous embodiment for a forme cylinder 01, the gap 17 is arranged on the inner radius r17 of 80 to 120 mm, in particular between 100 and 115 mm. The clear width h17 of the gap is 2 to 5 mm, preferably 3 mm. The wall thickness h03 of the outer cylinder body 03 is between h03 = 40 mm and h03 = 70 mm, in particular between 55 and 65 mm. The cylinder outer body 03 is self-supporting in this embodiment of the tempering over a length 101, z. B. 101 = 800 to 1200 mm, the barrel of cylinder 01, or a length 103, e.g. B. 103 = 800 to 1200 mm of the outer cylinder body 03 to be interpreted. With a depth h22 of the tensioning channel 22 between 20 and 45 mm, a sufficient thickness of the outer cylinder body 03 thus remains in the area of the tensioning channel 22. As in the first exemplary embodiment, the clear width h17 of the gap is advantageously increased in order to increase the ratio of a reduction in the inner radius r17 if the wall thickness h03 is increased and the gap 17 is moved further into the interior of the cylinder 01, and vice versa. The total cross section Q is z. B. between 1300 and 3500 mm ² . The ratio between the surface area 21 to be tempered and the total cross section Q of the channel 17 is z for this embodiment. B. between 300 and 900 mm ² , in particular between 500 and 650 mm ² . The remaining preferred dimensions of the forme cylinder 01 set out in the first exemplary embodiment are applicable to the second exemplary embodiment and are not mentioned again.

In a third and a fourth exemplary embodiment (FIGS. 4 and 6), the cylinder 01 is designed as a temperature-controlled roller 01, for. B. an ink roller 01, in particular a screen 01 or anilox roller 01, executed. The supply and discharge of the temperature control medium and the storage in side walls 08; 09 take place in the same or similar manner as in the first or second embodiment.

In the third exemplary embodiment (FIG. 4), as in the first exemplary embodiment, a helical, multi-path, preferably eight-path channel 17 is arranged on the circumference 24 of the cylinder base body 03. The distributor space 16 and the collection space 18 each have eight radial bores 14; 19 and is connected equidistantly with respect to the circumferential direction with eight starts 27 and eight ends 28. In the example, the channels 17 are for the purpose of more favorable mechanical and good flow properties than groove 17 with segment-like, for. B. executed semi-circular profile.

The multi-course channel 17 is advantageously designed with eight courses because, with the same geometry of the channel 17, either twice the amount of the temperature control medium with a constant pressure loss or the same amount of temperature control medium reduced pressure through the channel 17 is feasible.

The groove 17 is, as in the first embodiment, by means of, for. B. shrunk, outer cylinder body 03 covered. The temperature control by means of the helical groove 17 is particularly advantageous when effective and responsive temperature control of the outer cylinder body 03 is required, as shown, for example, by ink-guiding ink rollers 01 and anilox rollers 01. The smaller the wall thickness h03 of the outer cylinder body 03 (FIG. 5), the faster the reaction to the outer surface 21 when the operating temperature changes. In the example, the outer cylinder body 03 is designed with a small wall thickness h03 and is not self-supporting. H. it is supported on the webs 26. The width of the groove 17 determines the mechanically still permissible wall thickness h03 of the outer cylinder body 03 and vice versa. The permissible width b26 of the web 26 and the minimum wall thickness h03 are thermally mutually dependent, since a temperature profile on the outer surface 21 of the outer cylinder body 03 should be avoided as far as possible.

In an advantageous embodiment, the temperature-controlled roller 01 has the diameter d01 between 160 and 200 mm, in particular 180 mm. The wall thickness h03 of the outer cylinder body 03 is 1 to 4 mm, z. B. h03 = 2 mm (a coating of a total of 200 to 400 μm possibly not to be applied), the length I03 of the outer cylinder body 03 is between 800 and 1200 mm. A ratio V between the length I03 and the wall thickness h03 is z. B. between 200 and 1200 mm, in particular between 400 and 1000 mm. The web 26 has a width b26 of 2 to 4 mm, in particular of b26 = 3 mm, on the side interacting with the surface 23 of the outer cylinder body 03. The channel 17 has a width b17 between 8 and 13 mm, in particular 10 to 12 mm, in the area interacting with the surface 23 of the outer cylinder body 03. In the example, the profile of the channel 17 is semicircular, so that a maximum depth h17 of the channel 17 is 4 to 7 mm, in particular h17 = 5 mm. The total cross-section Q of the eight-course channel 17 amounts to 300 to 450 mm ² , and is roughly comparable with the total cross-section Q from the four-course first exemplary embodiment, if that too cooling jacket surface 21 is taken into account. Here, too, an increase in the amount of temperature-control medium flowing per unit of time, and if possible a contact area of the temperature-control medium with the area 23 of the outer cylinder body 03, must be maintained at least in the order of magnitude if the geometries of the roller 01 change while the surface area 21 to be temperature-controlled remains the same , The ratio between the surface area 21 to be tempered and the total cross section Q is z. B. between 1200 and 1600 mm ² .

In the fourth exemplary embodiment (FIG. 6), the cylinder 01 designed as a roller 01 has, as a channel 17, a gap 17 with an annular profile, comparable to that of the second exemplary embodiment. As in the third exemplary embodiment, the roller 01 has a diameter d01 of approximately 160 to 200 mm, the supply and discharge of the temperature control medium being carried out in accordance with one of the preceding exemplary embodiments.

In contrast to the third embodiment, the outer cylinder body 03 is self-supporting on the length 101, z. B. 800 to 1200 mm, and has z. B. a wall thickness h03 of 5 to 20 mm, in particular 5 to 9 mm. The clear width h17 of the gap 17 is 2 to 5 mm, preferably 3 mm, the gap 17 being arranged at an inner radius of 60 to 100 mm, in particular at 80 mm. The flowed through total cross section Q is z. B. between 1000 and 2500 mm ² , in particular at about 1500 mm ² . The relationship between the surface area 21 to be tempered and the total cross section Q of the channel 17 is, for. B. between 200 and 600 mm ² , in particular between 300 and 500 mm ² .

The roller 01 from the third and fourth exemplary embodiments, which is preferably designed as anilox roller 01, can have a profiling, for example ink-guiding cups, on its outer surface 21. It can preferably have a chromium-nickel and a ceramic coating each having a thickness of 100-200 μm on the outer surface 21 of the outer cylinder body 03, the latter having the profile or the cups. It is advantageous for the execution of the temperature control by means of a helical channel 17 that the ratio between the jacket surface 21 to be temperature-controlled and the total cross-section Q of the channel 17 through which flow passes between the basic cylinder body 02 and the outer cylinder body 03 is less than 2000 mm ² , in particular between 1800 and 1000 mm ² choose. The width b26 of the web is advantageously less than or equal to twice, in particular one and a half times the wall thickness h03 of the outer cylinder body 03

Particularly advantageous for cylinder 01 or rollers 01 is the design of the outer cylinder body 03 as a thin-walled tube 03 with a wall thickness d03 of less than or equal to 5 mm, in particular less than 3 mm, which is mechanically supported on the webs 26 spaced in the axial direction A.

In an advantageous further development, the arrangement for the temperature control carried out in the third exemplary embodiment can also be a forme cylinder 01, which has no fastening device, as is the case, for example, when using pressure sleeves instead of pressure plates or with directly imaging surface areas 21 of forme cylinders 01. A directed, responsive temperature control according to the third embodiment is also advantageous here.

LIST OF REFERENCE NUMBERS

01 cylinder, form cylinder, transfer cylinder, roller, dyeing, screen, anilox roller

02 cylinder body (01)

03 outer cylinder body, tube (01)

04 shaft journal (02)

05 -

06 shaft journal (02)

07 warehouse

08 side frame

09 side frame

10 -

11 axial bore

12 supply line, pipeline

13 discharge line

14 bore, radial

15 -

16 ring groove, distribution space

17 channel, groove, gap

18 collecting space, ring groove

19 bore, radial 0 - 1 lateral surface (03) 2 fastening device, clamping channel 3 surface (03) 4 circumference (02) 5 - 6 protrusion, web 7 beginning (17) 8 end (17) b17 width (17) b26 width (26)

d01 diameter (01) d11 inside diameter (11) d12 outside diameter (12)

h02 wall thickness (02) h03 wall thickness (03) h17 depth, clear width (17) h22 depth (22)

101 length (01)

I03 length (03)

r17 inner radius (17)

A axial direction (01)

Q total cross-section

S slope

V ratio (I03, h03)

Claims

Expectations

1. cylinder (01) of a rotary printing press, which has on an outer surface (21) of an outer cylinder body (03) at least one radially into the interior of the cylinder (01) fastening device (22) of an elevator, and which inside can be flowed through by a temperature control medium characterized in that a surface (23) of the outer cylinder body (03) facing the inside of the cylinder (01) and interacting with the temperature control medium is formed with an almost circular profile.

2. Cylinder (01) according to claim 1, characterized in that a wall thickness (h03) of the outer cylinder body (03) is greater than a depth (h22) of the fastening device (22) in a radial direction of the cylinder (01).

3. Cylinder (01) of a rotary printing press, which has at least one axially extending fastening device (22) of an elevator in an outer cylinder body (03) and through which a temperature control medium can flow in its interior, characterized in that a wall thickness (h03) of the outer cylinder body (03) is greater than a depth (h22) of the fastening device (22) in a radial direction of the cylinder (01).

4. Cylinder (01) according to claim 3, characterized in that an inside of the cylinder (01) facing and cooperating with the tempering surface (23) of the outer cylinder body (03) is formed with an almost circular profile.

5. Cylinder (01) according to one of claims 1 or 4, characterized in that along the inside of the cylinder (01) directed surface (23) of the outer cylinder body (03) at least one extending in the axial direction (A), extending helically Channel (17) is arranged.

6. Cylinder (01) according to claim 5, characterized in that the channel (17) is designed as a groove (17) on a circumference (24) of a cylinder base body (02), which is covered by means of the cylinder outer body (03).

7. Cylinder (01) according to claim 5, characterized in that the groove (17) in the circumference (24) has multiple threads, in particular four or eight threads.

8. Cylinder (01) according to claim 5, characterized in that an overall cross section (Q) of the channel (17) in a ratio of 1: 1000 to 1: 2000, in particular 1: 1400 to

1: 1800 to the surface area (21) to be tempered.

9. Cylinder (01) according to one of claims 1 or 3, characterized in that the channel (17) as an extending in the axial direction (A), arranged between the outer cylinder body (03) and a coaxially inside the outer cylinder body (03) Cylinder base body (02) formed gap (17) is formed with an almost circular profile.

10. Cylinder (01) according to claim 9, characterized in that the basic cylinder body (02) and the outer cylinder body (03) are not supported on one another.

11. Cylinder (01) according to claim 9, characterized in that an overall cross section (Q) of the gap (17) in a ratio of 1: 300 to 1: 900, in particular between 1: 500 and 1: 650, to the jacket surface (21 ) is executed.

12. Cylinder (01) according to claim 9, characterized in that the gap (17) has a clear width (h17) of 2 to 5 mm.

13. Cylinder (01) according to one of claims 1 or 3, characterized in that the cylinder (01) has a supply line (12) and a discharge line (13) for the temperature control medium.

14. Cylinder (01) according to claim 13, characterized in that a shaft journal (04; 06) has both the feed line (12) and the discharge line (13) arranged coaxially around the feed line (12).

15. Cylinder (01) according to one of claims 1 or 3, characterized in that the cylinder (01) is designed as a forme cylinder (01).

16. Cylinder (01) according to one of claims 1 or 3, characterized in that the cylinder (01) is designed as a transfer cylinder (01).