EP2603635A1

EP2603635A1 - Wobble apparatus

Info

Publication number: EP2603635A1
Application number: EP11743813.5A
Authority: EP
Inventors: Andreas Schilz; Ralf Schröder; Heinrich Peter Weyermann; Hans-Joachim Bremer
Original assignee: Voith Patent GmbH
Current assignee: Voith Patent GmbH
Priority date: 2010-08-11
Filing date: 2011-08-10
Publication date: 2013-06-19
Also published as: DE102010039200A1; CN202559178U; WO2012020044A1

Abstract

The invention relates to a wobble apparatus (1) for moving a roll (2) to and fro along an axis of the latter, in particular a roll (2) for a machine for producing a fibrous web, in particular a paper web, cardboard web or packaging-paper web, which wobble apparatus (1) has a first eccentric drive (10) which is connected to the roll (2) in the direction of the roll axis (L) and a second eccentric drive (11) which is connected to the roll (2) in the direction of the roll axis (L), wherein the two eccentric drives (10, 11) are driven by at least one motor, preferably by two motors (17, 18), wherein the two eccentric drives (10, 11) are connected to the at least one motor, preferably to the two motors (17, 18), at least by means of two parallel shafts (19, 20; 19.1, 20.1, 19.2, 20.2) and a clutch (21) which is arranged between them for the transmission of rotational movements with an accurate rotary angle, wherein the two eccentric drives (10, 11) are arranged on or in a common and movable displaceable device (6), and wherein the roll (2) and the device (6) are connected to one another directly or indirectly by means of at least one at least single-part wobble rod (9). The wobble apparatus (1) according to the invention is characterized in that the clutch (21) has a variable shaft offset with at least one intermediate element (22, 22.1) which is connected to the two clutch halves (21.1, 21.2) via in each case one mechanism (23) comprising at least three links (24) which are parallel to one another, including journals (25), wherein the intermediate element (22) is formed by an unsupported disc-like body (22.1), and wherein the journals (25) are attached fixedly both in the intermediate element (22, 22.1) and in the two clutch halves (21.1, 21.2) and are mounted in corresponding holes (26) of the links (24), and in that the individual journal (25) is mounted in the corresponding hole (26) of the link (24) by means of at least one needle bearing (27).

Description

shaking

The invention relates to a shaking device for reciprocating a roller along an axis thereof, in particular a roller for a machine for producing a fibrous web, in particular a paper, cardboard or packaging paper web, a first, connected to the roller in the direction of the roll axis Eccentric drive and a second, connected to the roller in the direction of the roller axis eccentric drive, wherein the two eccentric drives are driven by at least one motor, preferably two motors, wherein the two eccentric m er with the at least one motor, preferably with the two Engines are connected at least by means of two parallel shafts and a coupling arranged therebetween for rotational angularly accurate transmission of rotational movements, wherein the two eccentric drives are arranged on or in a common and movable movable device and wherein the roller and the device by means of at least an at least one-part Schüttelstange are directly or indirectly connected.

Such a shaking device is known for example from the document EP 1 624 102 B1.

This largely reaction force-free shaking device is based on directly driven mass pairs by means of highly dynamic three-phase drives m with angular tracking control, the mass pairs in a hydrostatically mounted device, such as a slide, a frame or a cream s, arranged si nd. However, the two mass pairs of such a shaking device can also be achieved by means of only one drive motor be driven drive means. In addition, instead of an electric motor and a hydraulic motor can be used.

The transmission of the rotational energy generated by means of the shaking rod on an exemplary breast roll of a machine ine for the produc- tion of a fibrous web. The unit "carriage with breast roller" is a freely swinging system in a horizontal direction - with a common mechanical zero point. This shaker also has the following properties:

- High frequency shaking

Even at machine speeds of up to 1 .200 m / min, the formation in the fibrous web to be produced can be significantly improved.

- Controllable breaking length ratio

By adjusting the stroke and frequency of shaking that can

Tear length ratio in the fibrous web to be produced are freely selected within wide limits.

There is thus the following general benefit for the operator of the shaking device:

- Best formation in the fibrous web to be produced by a uniform fiber distribution with a significant improvement in paper quality - with advantages in further processing, when painting, impregnating and printing the fibrous web to be produced.

- Improved dimensional stability through targeted fiber orientation in the fibrous web to be produced.

- Reduced maintenance costs due to low stress and reduced wear. And the specific benefit to the shaker operator is:

- Significant improvement of the formation in the fibrous web to be produced. - Reduction of the breaking length ratio in the fibrous web to be produced.

- Improvement of other quality parameters, such as bursting strength, compression resistance (SCT-CD), etc. in the fibrous web to be produced.

- No reaction forces. The foundation must only bear the weight of the shaker, no transmission of disturbing vibrations to other parts of the machine, such as on the headbox and the wire section.

- The design is compact, robust and sealed. The device or the carriage is preferably stored hydrostatically, the lubrication system-integrated ensures according to the circulation principle.

The couplings used hitherto have the disadvantage that their bearings are not or are often supplied insufficiently with lubricants and that the closed bearing housing is very sensitive to axial loads.

As a result of these disadvantages, there is often a premature failure of the bearings of the clutches, in particular due to overheating and pitting formations, that is, dimple formation on running surfaces. In addition, there are often black tarnished surfaces on functional parts.

It is therefore an object of the invention to improve a shaking device of the type mentioned in such a way that the mentioned disadvantages of the prior art are largely reduced, preferably even completely avoided. In particular, the life of the clutch, in particular their bearings increases, ensures better compatibility of the clutch against axial loads and improved lubrication of the bearing of the clutch can be achieved.

This object is achieved according to the invention in a shaking device of the type mentioned in that the clutch has a variable Shaft offset with at least one intermediate member which is connected to the two coupling halves via a respective transmission of at least three mutually parallel arms together with pins, wherein the intermediate member is formed by an uneven disc-like body and wherein the pins in both the intermediate member and in the two coupling halves firmly mounted and are mounted in corresponding holes in the handlebars, and that the storage of the individual pin in the corresponding bore of the handlebar m ittels using at least one needle bearing. The object of the invention is completely solved in this way.

The coupling of the shaking device according to the invention is also characterized in particular by the fact that it enables a transmission of the rotational movement with mutual mobility of the waves to the shortest possible length, is simple and unwanted bearing stresses are avoided.

The storage of the individual pin in the corresponding bore of the handlebar with at least one needle bearing in particular has a positive effect on the service life of the coupling, in particular its bearings.

The intermediate member is formed by an uneven disc-like body and the pins are fixedly mounted both in the intermediate member and in the two coupling halves and stored in corresponding holes in the handlebars. By the handlebars, the intermediate member is always kept parallel to the drive-side first coupling half, so that it rotates with an angle with this first coupling half. In the same way, the intermediate member by parallel link with the output side second coupling half in drive connection, so that in turn follows the intermediate member and thus the first half coupling angle. The length of the link is less than the distance of the articulation points on the coupling halves or the intermediate member, so that the handlebars can rotate past each other in a continuous circulation movement. The two can Coupling halves move in a certain, determined by the length of the handlebars area against each other, without changing the angle-faithful transmission of the rotational movement something. The fact that at least three links are provided, it is ensured that over the handlebars a uniform torque transmission can take place without dead centers.

Furthermore, it is not necessary and even disadvantageous to additionally store the intermediate member. The position of the intermediate member is clearly fixed at a given input and output shaft by the handlebar, and any additional storage of the same leads only to a kinematic over-determination. By this enabled, flat, disk-like design of the intermediate member, it is again possible to make the whole coupling very flat, so that it is possible to transmit the movement of the drive shaft to a very small axial length to a relative to the drive shaft movable output shaft.

In order to allow a larger shaft misalignment, without having to perform the coupling halves and the intermediate member and the handlebars bulky large, a series connection of several intermediate body and Parallellenkergetriebe is possible.

Between the respective coupling half and the at least three adjacent and mutually parallel arms and / or between the intermediate member and the both sides at least three adjacent and mutually parallel arms preferably at least one axial bearing surrounding the respective pin is mounted, so that the Kupp lu ng the According to the invention shaking device has a much better compatibility with axial loads. The thrust bearing is preferably manufactured according to DIN 5405-2. The axial cages are usually made of plastic or metal. In addition, axial needle roller rings have a very low height. They can take in one direction very high axial loads, while radial forces must be absorbed separately. For the use of the wreaths hardened and ground contact surfaces are required as a career. The wreaths with However, plastic cages are only suitable for operating temperatures from -20 ° C to + 120 ° C.

The thrust bearing is preferably an axial needle bearing which acts at least on one side and which preferably has a bearing width in the range of 1 to 5 mm, preferably 1 to 3 mm, in particular 2 mm. The bearing widths lead decisively to achieve the shortest possible length of the coupling of the shaking device according to the invention. Furthermore, the at least unilaterally acting axial needle bearing preferably has at least one of the following properties:

a dynamic axial load capacity of at least 10,000 N, preferably of at least 12,000 N, in particular of at least 14,000 N;

- A static axial load rating of at least 30,000 N, preferably of at least 40,000 N, in particular of at least 50,000 N;

a fatigue limit load of at least 4,000 N, preferably at least 4,500 N, in particular at least 5,000 N; and or

- A limiting speed of at least 5,000 1 / min, preferably of at least 7,500 1 / min, in particular of at least 8,000 1 / min.

These mentioned properties of the axial needle bearing of the coupling of the shaking device according to the invention have been proven to have a positive effect on the life of the coupling, in particular their bearings. They also ensure a smooth and low-maintenance operation of the coupling of the shaking device according to the invention.

On the side facing away from the handlebar of the thrust bearing is preferably at least one thrust washer surrounding the respective pin, which ideally has a slice thickness of at least 2 mm, preferably of at least 3 mm, in particular of at least 5 mm. This thrust washer has an advantageous effect, inter alia, on a low-wear operation of the clutch of the shaker according to the invention with the shortest possible length of the same. Basically serves a thrust washer serves the recording of axial loads when rotating. The occurring axial loads can occur both swelling and permanent. The swelling stress is a challenge especially for plastic thrust washers. Only a few materials withstand fatigue. The load of the thrust washer is mainly characterized by relative speed, pressure and type of compressive stress, as well as the resulting temperature. In addition to the actual function, in many cases the challenge of assembly and the small installation space is added.

Moreover, the needle bearing arranged in the bore of the link preferably has a bearing housing which is provided with an opening on the side facing away from the axial bearing. Through this attached opening the lubrication of the bearing of the clutch can be significantly improved without large additional costs and at the same time the life of the clutch, in particular their bearings can be increased.

Also, the eccentric position of the two eccentric drives is preferably mutually adjustable to adjust the stroke of the reciprocating motion of the roller. By adjusting the angle between the two mass pairs from 0 to 180 ° (in the direction of rotation), a mass force acting on a shaking rod can be adjusted continuously. About the rotational speed of the two mass pairs, the frequency can also be adjusted continuously. The shaking bar preferably has a length in the range from 300 to 3,000 mm, preferably from 600 to 2,500 mm, in particular from 800 to 2,000 mm, because sufficient, preferably optimum strength and buckling resistance are still provided in these longitudinal regions. In this case, the rolls and the iron can be indirectly connected to each other by means of a separate shaking rod. As a rule, a clutch is additionally provided between the roller and the device. A shaking device with a shaking rod, which has at least one such and at least temporarily fixable, in particular clampable ball joint is disclosed in the German patent application with the applicant file number HPB14657 DE - "DS shaking (ball)" and the same filing The present disclosure of this German patent application is hereby made the subject of the present description.

Moreover, the shaking device preferably has a shaking index in the range from 1, 500 to 6,000 [1000 / min], the shaking index being calculated from the following formula:

Shake characteristic = (shaking ² x Orbital) / wire speed The units of the individual variables are as follows: shake characteristic SKZ in [1000 / min], shaking n in [1 / min], Orbital s in [mm] and wire speed v _S ieb in [m / min].

And the respective eccentric drive preferably has a maximum drive torque in the range of 100 to 750 Nm, preferably from 125 to 700 Nm, in particular from 150 to 600 Nm, at a shaking frequency of 100 to 700 1 / min, preferably from 150 to 600 1 / min , and at a Schüttelhub from 0.1 to 30 mm, preferably from 0, 1 to 25 mm, on. These properties are essential for achieving the aforementioned advantages and benefits of the shaker.

The position control of the shaking device can be done, for example, according to the disclosure of the already mentioned document EP 1 624 102 B1. In this case, the device may have a system for centering or for maintaining a common zero point between the roller and the device with respect to external disturbances. As a system can be provided by a control device acted upon motor adjustment device. The shaking device according to the invention can also be used in an excellent manner in a machine for producing a fibrous web, in particular a paper, board or packaging paper web. This then results in the already mentioned above advantages of the invention.

In a first preferred embodiment, the machine can be designed as a fourdrinier machine having a roller, in particular a breast roller. In this case, the shaking device according to the invention moves the roller, in particular the breast roller, back and forth. Such a fourdrinier is for example from the document DE 101 16 867 A1, the relevant content of which is hereby made the subject of the present description.

In a second preferred embodiment, the machine may be designed as a multi-layer machine having at least one roller, in particular a breast roller. In this case, the shaking device according to the invention moves at least one roller, in particular a breast roller, back and forth. Such a multi-layer machine is known for example from the publications DE 4031 038 A1, DE 100 15828 A1 and DE 10223398 A1, the relevant content of which is hereby made the subject of the present description.

Further features and advantages of the invention will become apparent from the following description of a preferred embodiment with reference to the drawings. demonstrate

Figure 1 is a schematic and partially sectioned side view of a known shaking device for reciprocating a roller for a machine for producing a fibrous web;

Figure 2 is a schematic and partially sectioned plan view of the i

1 shaking device for Hin- un Moving a roller for a machine for producing a fibrous web;

Figure 3 is a schematic and partially sectioned plan view of a preferred embodiment of a coupling of the shaking device according to the invention for reciprocating a roller for a machine for producing a fibrous web;

Figure 4 is a partial schematic representation of a preferred

Embodiment of the shaking device according to the invention for reciprocating a roller for a machine for producing a fibrous web;

Figure 5 is a schematic vertical section through a preferred

Embodiment of a thrust bearing of the shaking device according to the invention for reciprocating a roller for a machine for producing a fibrous web; and

Figure 6 is a schematic front view of a preferred

Embodiment of a thrust washer of the shaking device according to the invention for reciprocating a roller for a machine for producing a fibrous web.

1 shows a schematic and partially sectioned side view of a known shaking device 1 for reciprocating a roller 2 for a non-illustrated machine for producing a fibrous web. The roller 2 is thereby reciprocated along its longitudinal axis L.

The fibrous web may in particular be a paper, board or packaging paper web.

The roller 2 is rotatably mounted on schematically indicated roller bearings 3, 4 and movable in the axial direction, ie along its longitudinal axis L. The roller 2 is connected to the shaker 1 via a coupling 5 which is designed to be generally detachable. The shaking device 1 is used for shaking, Thus, for reciprocating the roller 2 along its longitudinal axis L, as indicated by a double arrow A.

The shaking device 1 has a device 6, for example, a carriage, a frame or a frame, which is mounted on Einrichtungslagern 7, 8 in the direction of the double arrow A, ie along the longitudinal axis L of the roller 2 movable or movable.

The device 6 is rigidly provided at one axial end with a shaking rod 9, which merges rigidly into the coupling 5, such that an H reciprocating movement of the device 6 leads to a corresponding reciprocating movement of the roller 2.

For this purpose, a first eccentric drive 10 and a second eccentric drive 11 are provided on the device 6.

The first eccentric 10 is formed by a pair of flywheel masses 13, 14 which are mounted symmetrically to a roll axis 12 of the roller 2 rotatably in the device 6 and which are driven, for example by a first motor, not shown. The second eccentric drive 1 1 is formed by a pair of flywheel masses 15, 16, which are also mounted symmetrically to the roller shaft 12 rotatably in the device 6 and which are driven, for example, by a second motor, not shown. However, it can also only one, a drive motor having drive means for driving the two pairs of flywheel bodies 13, 14; 15, 16 may be provided. The eccentric position of the two eccentric drives 10, 1 1 is mutually adjustable to adjust the stroke of the reciprocating motion of the roller 2.

2 shows a schematic and partially sectioned plan view of the shaking device 1 shown in Figure 1 for reciprocating a roller, not shown for a machine, not shown, for producing a fibrous web. The first eccentric drive 10 is, as already stated, formed by a pair of flywheel mass bodies 13, 14, which are driven by a first motor 17. The second eccentric drive 1 1 is in turn formed by a pair of flywheel masses 1 5, 16, which are driven by a second motor 1 8. The two eccentric drives 1 0, 1 1 are connected to the respective motor 17, 18 at least by means of two parallel shafts 19.1, 20.1, 19.2, 20.2 and a clutch 21 arranged therebetween for the rotationally accurate transmission of rotational movements. Also, the two eccentric drives 10, 1 1 are arranged on or in the common and movable device 6,

FIG. 3 now shows a schematic and partially sectioned plan view of a preferred embodiment of a coupling 21 of the shaking device 1 according to the invention for reciprocating a roller, not shown, for a machine, not shown, for producing a fibrous web.

The clutch 21 has a variable shaft offset with at least one intermediate member 22 which is connected to the two coupling halves 21 .1, 21 .2 via a respective gear 23 of three mutually parallel arms 24 together with pins 25 on. The pins 25 of the three mutually parallel arms 24 are arranged at equal distances from the axes of the two shafts 1 9, 20 and offset by 1 20 ° to each other. The intermediate member 22 is formed by an uneven disc-like body 22.1 and the pins 25 are fixedly mounted both in the intermediate member 22 and in the two coupling halves 21 .1, 21 .2 and mounted in corresponding holes 26 of the handlebars 24.

The bearing of the individual pin 25 in the corresponding bore 26 of the link 24 by means of a respective needle bearing 27, which has a bearing housing 28. And between the respective coupling half 21 .1, 21 .2 and the at least three adjacent and mutually parallel arms 24 each one surrounding the respective pin 25 thrust bearing 29 is mounted. Furthermore, between the Intermediate member 22 and the two adjacent three adjacent and mutually parallel arms 24 m at least one of the respective pin 25 surrounding thrust bearing 29 is mounted. And on the side facing away from the handlebar 24 side of the thrust bearing 29 a the respective pin 25 surrounding thrust washer 30 is arranged.

Thus, between the respective coupling half 21 .1, 21 .2 and the at least three adjacent and mutually parallel links 24 each a respective journal 25 surrounding thrust bearing 29 is mounted. Also, between the Zwischeng song 22 and on both sides wen at least three adjacent and mutually parallel arms 25 each a respective journal 25 surrounding thrust bearing 29 is mounted (see Figure 4). The thrust bearing 29 is an at least unilaterally acting thrust needle bearing.

FIG. 3 shows an embodiment with a single intermediate member 22, which is in drive connection with the drive and driven side coupling halves 21, 1, 21, 2 via a respective gear 23. But you can build the shaft coupling described also with two or more disk-shaped pontics to change the shaft offset in a correspondingly larger area.

FIG. 4 shows a schematic partial representation of a preferred embodiment of the shaking device 1 according to the invention for reciprocating a roller, not shown, for a machine (not shown) for producing a fibrous web.

The arranged in the bore 26 of the arm 24 needle bearing 27 for the pin 25 has the aforementioned bearing housing 28, which is also provided on the axial bearing 29 and the thrust washer 30 side facing away with an opening 31. The thrust bearing 29 is preferably in turn an at least single-acting axial needle bearing.

FIG. 5 shows a schematic vertical section through a preferred embodiment of a thrust bearing 29 of the shaker device according to the invention

1 for reciprocating a roller, not shown, for a machine, not shown, for producing a fibrous web.

The illustrated axial bearing 29 is an at least unilaterally acting axial needle bearing, which preferably has a bearing width 29 B in the range of 1 to 5 m m, preferably from 1 to 3 m m, in particular of 2 m m. In addition, the axial cantilever bearing 29, which acts on at least one side, has at least one of the following properties:

a dynamic axial load capacity C _a of at least 10,000 N, preferably of at least 12,000 N, in particular of at least 14,000 N;

a static axial load rating Co _a of at least 30,000 N, preferably of at least 40,000 N, in particular of at least 50,000 N;

a fatigue limit load C _ia of at least 4,000 N, preferably of at least 4,500 N, in particular of at least 5,000 N; and or

a limiting speed n _G of at least 5,000 l / m in, preferably of at least 7,500 l / min, in particular of at least 8,000 l / min.

6 shows a schematic front view of a preferred embodiment of a thrust washer 30 of the shaking device 1 according to the invention for reciprocating a roller, not shown, for a machine, not shown, for producing a fibrous web.

The thrust washer 30 shown has a disk thickness 30 d of at least

2 mm, preferably of at least 3 mm, in particular of at least 5 mm, on. Furthermore, the eccentric position of the two eccentric drives 10, 1 1 of the shaking device 1 according to the invention is mutually adjustable to adjust the stroke of the reciprocating motion of the roller (see Figure 2). Furthermore, the shaking device 1 according to the invention, which is shown at least partially in each case in FIGS. 3 to 6, has a shaking characteristic SKZ in the range from 1 .500 to 6,000 [1000 / min], whereby the shaking characteristic SKZ is calculated from the following formula (see FIG.

SKZ = ((shaking n) ² x (Orbital s)) / (wire speed v _S IEB)

The units of the individual variables are as follows: shake characteristic SKZ in [1000 / min], shaking n in [1 / min], Orbital s in [mm] and wire speed v _S ieb in [m / min]. The respective eccentric drive 10, 1 1 has a maximum drive torque M _max in the range of 100 to 750 Nm, preferably from 125 to 700 Nm, in particular from 150 to 600 Nm, at a shaking frequency n of 100 to 700 1 / min, preferably of 150 to 600 1 / min, and at a shaking stroke s from 0 to 30 mm, preferably from 0 to 25 mm, (see Figure 1).

The shaking device 1 according to the invention, which is at least partially illustrated in each case in FIGS. 3 to 6, is outstandingly suitable for use with a machine for producing a first fibrous web, in particular a paper, board or packaging paper web.

This machine can be designed as a roller, in particular a breast roller having a fourdrinier machine and the shaking device according to the invention, the roller, in particular the breast roll back and forth. As an alternative, this machine can also be designed as a multi-layer machine which generates at least one roller, in particular a wall washer, and the inventive machine Shaker can reciprocate at least one roller, in particular a breast roller.

In summary, it should be noted that a shaking device of the aforementioned types is provided by the invention, which reduces the disadvantages of the prior art as far as possible, preferably even completely avoided. In particular, the life of the clutch, in particular their bearings is increased, ensures better compatibility of the clutch against axial loads and achieved improved lubrication of the bearing of the clutch.

LIST OF REFERENCES

1 shaker

2 roller

3 roller bearings

4 roller bearings

5 clutch

6 device

7 furniture store

8 furniture store

9 shaking bar

10 First eccentric drive

1 1 Second eccentric drive

12 roll axis

13 flywheel mass body

14 flywheel mass body

15 flywheel mass body

16 flywheel mass body

17 First engine

18 second engine

19 wave

19.1 wave

19.2 wave

20 wave

20.1 wave

20.2 wave

21 clutch

21 .1 Coupling half

21 .2 Coupling half

22 intermediate link

23 gears

24 handlebars 25 cones

26 hole

27 needle roller bearings

28 bearing housing

29 Thrust bearings, axial needle bearing

29. B bearing width

30 thrust washer

30. d pane thickness

31 opening

Coa static axial load rating

Ca dynamic axial load rating C _U a fatigue limit load

Mmax maximum drive torque

n shaking frequency

n _G limit speed

s shaking stroke

SKZ shaking index

Vsieb screening speed

Claims

claims

Shaking device (1) for reciprocating a roller (2) along an axis thereof, in particular a roller (2) for a machine for producing a fibrous web, in particular a paper, cardboard or packaging paper web, the first, with the roller (2) eccentric drive (10) connected in the direction of the roll axis (L) and a second eccentric drive (11) connected to the roll (2) in the direction of the roll axis (L), the two eccentric drives (10, 11 ) are driven by at least one motor, preferably by two motors (17, 18), wherein the two eccentric drives (10, 1 1) with the at least one motor, preferably with the two motors (17, 18) at least by means of two parallel shafts (19, 20; 19.1, 20.1, 19.2, 20.2) and a coupling (21) arranged therebetween for rotationally true-angle transmission of rotational movements are connected, wherein the two eccentric drives (10, 1 1) on or in a common and movable n are arranged movable means (6) and wherein the roller (2) and the device (6) by means of at least one at least one-part Schüttelstange (9) are connected to each other directly or indirectly,

characterized,

in that the coupling (21) has a variable shaft offset with at least one intermediate element (22, 22.1) which is connected to the two coupling halves (21, 1, 21, 2) via a respective transmission (23) comprising at least three mutually parallel links (24) Pin (25), wherein the intermediate member (22) is formed by an unsupported disk-like body (22.1) and wherein the pins (25) in both the intermediate member (22,

22.1) and in the two coupling halves (21 .1, 21 .2) fixedly mounted and in corresponding holes (26) of the links (24) are mounted, and that the storage of the individual pin (25) in the corresponding bore (26 ) of the handlebar (24) by means of at least one needle bearing (27).

Shaking device (1) according to claim 1,

characterized,

in that at least one axial bearing (29) surrounding the respective pin (25) is mounted between the respective coupling half (21, 1, 21, 2) and the at least three adjacent and mutually parallel links (24).

Shaking device (1) according to claim 1 or 2,

characterized,

that between the intermediate member (22, 22.1) and the at least three adjacent and mutually parallel arms (24) on both sides in each case at least one of the respective pin (25) surrounding thrust bearing (29) is mounted.

Shaking device (1) according to claim 2 or 3,

characterized,

in that the axial bearing is an axial needle bearing (29) which acts at least on one side and preferably has a bearing width (29. B) in the range of 1 to 5 mm, preferably 1 to 3 mm, in particular 2 mm.

Shaking device (1) according to claim 4,

characterized,

in that the at least unilaterally acting axial needle bearing (29) has at least one of the following properties: - A dynamic axial load rating (C _a ) of at least 10,000 N, preferably of at least 12,000 N, in particular of at least 14,000 N;

a static axial load rating (Co _a ) of at least 30,000 N, preferably of at least 40,000 N, in particular of at least 50,000 N;

a fatigue limit load (C _ua ) of at least 4,000 N, preferably of at least 4,500 N, in particular of at least 5,000 N; and or

- A limiting speed (n _G ) of at least 5,000 1 / min, preferably of at least 7,500 1 / min, in particular of at least 8,000 1 / min.

Shaking device (1) according to one of claims 2 to 5,

characterized,

in that at least one thrust washer (30) surrounding the respective journal (25) is arranged on the side of the axial bearing (29) facing away from the handlebar (24).

Shaking device (1) according to claim 6,

characterized,

the stop disk (30) has a disk thickness (30.d) of at least 2 mm, preferably of at least 3 mm, in particular of at least 5 mm.

Shaking device (1) according to one of the preceding claims,

characterized,

in that the needle bearing (27) arranged in the bore (26) of the link (24) has a bearing housing (28) which is provided with an opening (31) on the side facing away from the axial bearing (29).

Shaking device (1) according to one of the preceding claims,

characterized, that the eccentric position of the two eccentric drives (1 0, 1 1) is mutually adjustable to adjust the stroke of the reciprocating motion of the roller (2). 1 0. shaking device (1) according to any one of the preceding claims,

characterized,

it has a Shake Index (SKZ) in the range of 1, 500 to 6,000 [1 000 / min], where the Shake Index (SKZ) is calculated from the formula:

SKZ = ((shaking n) ² x (Orbital s)) / (wire speed v _S IEB)

1 1. Shaking device (1) according to one of the preceding claims,

characterized,

the respective eccentric drive (10, 11) has a maximum drive torque (MMax) in the range from 1 00 to 750 Nm, preferably from 1 25 to 700 Nm, in particular from 1 50 to 600 Nm, at a shaking frequency (n) of 1 00 to 700 1 / min, preferably from 1 50 to 600 1 / min, and at a Schüttelhub (s) of 0, 1 to 30 mm, preferably from 0, 1 to 25 mm. 1 2. Machine for producing a fibrous web, in particular a paper, board or packaging paper web,

characterized,

in that it comprises at least one shaking device (1) according to one of the preceding claims.

1 3. Machine according to claim 1 2,

characterized,

in that it is designed as a fourdrinier machine having a roller (2), in particular a breast roller, and that the shaking device (1) according to one of claims 1 to 11 moves the roller (2), in particular breast roller, back and forth. Machine according to claim 12,

characterized,

in that it is designed as a multi-layer machine having at least one roller, in particular a breast roller, and in that the shaking device according to one of claims 1 to 11 moves at least one roller, in particular breast roller, back and forth.