EP3124657B1 - Support of a flexible bend in a revolving flat card - Google Patents

Description

The present invention relates to a storage of a flexible bend in a revolving flat card.

In a carding machine, the lid area together with the drum forms the main carding zone and has as function the dissolution of the flakes into single fibers, removal of impurities and dust, elimination of very short fibers, the dissolution of nits and the parallelization of the fibers. Depending on the application of a card, hard covers, revolving lids or a mixture of fixed and revolving lids are used. When using a revolving lids or a mixture of hard covers and revolving lids, one speaks of a revolving flat card. Between the sets of covers and the clothing of the drum forms a narrow gap called the carding nip. It results in the use of revolving lids by the revolving lids, guided by arcuate strips - so-called flexible arch, Regulierbogen, Flexbogen or Gleitbogen - are guided along a predetermined distance by these strips in the circumferential direction of the drum. The size of the carding nip lies with a revolving flat card between 0.10 to 0.30 mm for cotton or up to 0.40 mm for man-made fibers.

1. a) Zur Neueinstellung des Kardierspaltes bei der Herstellung der Karde oder nach einem Ersatz der Trommelgarnitur. Dabei ist eine individuelle Verstellung von einzelnen Lagerstellen notwendig, um eine konzentrische Einstellung der Flexibelbogen gegenüber der Trommeloberfläche zu ermöglichen
2. b) Zur Nachstellung des Kardierspaltes bei Abnutzungserscheinungen der Garnituren, wobei hier eine gleichmässige Verstellung aller Lagerstellen erwünscht ist
3. c) Zur Nachstellung des Kardierspaltes nach einem Schleifen der Garnituren
4. d) Zur Korrektur des Kardierspaltes aufgrund der thermischen Ausdehnung der Trommel
5. e) Zur Einstellung des Kardierspaltes bei unterschiedlichen Trommel- oder Deckel-Garniturhöhen abhängig von der im Einsatz stehenden Garnitur.

It is known that the flexible elbow must be designed to be radially adjustable in order to ensure a consistent over the entire course of the flexible arch carding. The radial adjustability is necessary for various reasons:

1. a) To readjust the carding gap during the production of the card or after a replacement of the drum set. In this case, an individual adjustment of individual bearings is necessary to allow a concentric adjustment of the flexible sheet opposite the drum surface
2. b) For adjustment of the carding gap in case of wear of the trimmings, in which case a uniform adjustment of all bearings is desired
3. c) To re-adjust the carding gap after sanding the sets
4. d) To correct the carding gap due to the thermal expansion of the drum
5. e) To adjust the carding gap at different drum or lid heights depending on the set in use.

In a known device, the flexible bend is secured with adjusting screws on the machine frame. The adjustment screws allow for a concentric adjustment of the flexible arch surface so that the traveling lids can be kept at a constant distance along the drum surface. The setting accuracy depends on the design of the adjusting screws.

In the EP 1 201 797 has proposed a device for adjusting the carding gap, in which the flexible sheet is supported on rotatably mounted rollers. The rollers are designed as rotatable helical cams. Upon rotation of these cams is raised by the worm shape of the flexible bend at the corresponding support point and in the radial direction away from the drum axis or to these. In this way, a coarse adjustment of the carding nip is proposed. For fine adjustment, the flexible sheet itself is moved in the drum rotation direction, which causes the radial distance of the flexible sheet to change from the drum axis.
A disadvantage of the device is that the entire flexible sheet must be moved to adjust the carding gap. In particular, the fine adjustment is provided by the movement of the flexible bend, which is associated with a considerable expenditure of force and thus only jerking can be performed.

In the EP 2 392 703 A1 has been proposed a device for adjusting the carding gap, in which the flexible sheet is held on an eccentrically mounted bolt. The one setting of the carding gap should be made possible without changing the position of the flexible bend in the circumferential direction.
A disadvantage of the disclosed embodiment of the bearing, however, the necessary complex construction for the movement of the bolt via a spaced-apart from the adjusting device which with the bolt via a lever in connection stands. For a simultaneous displacement of all support points of the flexible sheet an additional displacement means is necessary, which further complicates the construction of the adjustment.

The invention of the present application has for its object to provide a storage of a flexible arch which allows an adjustment of the carding at a single bearing point, as well as an adjustment of the carding at all bearing points of the flexible sheet together, both types of adjustment to use the same adjustment and wherein the adjustment of a single bearing should be possible without affecting the common adjustment.

The object is solved by the features in the characterizing part of the independent claim.

To solve the problem, a storage of a flexible sheet is proposed in a revolving flat card with a drum and a drum axis, wherein the bearing comprises at least three bearings, each with a bearing pin and an adjusting lever. The flexible sheet is held at each bearing point on the respective bearing pin, that during a rotational movement of the bearing pin of the flexible sheet is moved radially to the drum axis. The bearing pin has a bearing pin axis, a mounting portion, a movement portion and a support surface for the support of the flexible sheet, while the support surface is formed by a spiral around the bearing pin axis arranged surface. The adjusting levers are connected to a common slider.

For the support of a flexible arch several support points, so-called bearings are provided. The number of bearings depends on the design of the flexible sheet, in particular its length. For stable storage at least three bearings are necessary. The bearings may be arranged symmetrically or asymmetrically with respect to the flexible arch. However, if the flexible sheet is executed in several parts or leads over a larger circumference of the drum, more than three bearing points, for example five or seven bearing points, are necessary. The storage of the flexible sheet is done so that the sliding on it Travel lids are guided in the desired type of drum surface along.

The flexible bend is held by a bolt at each bearing point. The bolt itself is rotatably mounted in the machine frame of Wanderdeckelkarde, this, the bolt on a mounting portion. Advantageously, the attachment portion of the bolt is designed such that adjoins the movement portion on one side of the attachment portion and on the other side of the attachment portion, the support surface for the flexible bend. Thus, the attachment portion is arranged in the direction of the bearing pin axis between the movement portion and the support surface.
In a preferred embodiment, the attachment portion is bisected by the support surface disposed within the attachment portion. The bearing pin is thereby held in two places in the machine frame, wherein between these two points the support surface for the flexible sheet is arranged. This has the advantage that the bearing points of the bearing pin is stressed only by forces in one direction and no torques occur. In a one-sided storage act on the bearing bolt in addition bending forces, which can be avoided by a two-part mounting portion.

The bearing surface is spirally applied around the bearing pin axis. As a result, with a rotation of the bolt by a certain angle, the radial distance of the support surface changes by a certain amount, which is dependent on the spiral shape of the support surface. The usable bearing surface does not extend over the entire circumference of the bearing pin due to the helical design. For the adjustment of the carding gap, it is sufficient if the flexible sheet can be changed in its distance from the drum axis in a range of 2 to 10 mm. This change in the radial distance of the flexible sheet from the drum axis corresponds to the necessary change in the distance of the support surface from the bearing pin axis. As a result of the spiral shape, the distance of the bearing surface from the bearing pin axis likewise changes by 2 to 10 mm. The spiral shape is, for example, created such that the change in the distance during at least half the circumference of the bearing pin results. The radial distance of the bearing surface of the bearing pin axis thus changes, for example, by an amount of 2 to 10 mm with a rotation of the bearing pin by 180 °. Preferably, a change in the distance of 4 to 8 mm is to be striven for, as has shown a particularly advantageous change in the distance of 6 mm.

In order to enable a simple assembly is advantageously to ensure that the bearing surface has a greatest radial distance from the bearing pin axis, which is not greater than half the diameter of the bearing pin at its attachment portion.

In a preferred embodiment, the spiral shape of the support surface is an Archimedean spiral. Thereby, a decrease or an increase of the distance of the bearing surface from the bearing pin axis with a rotation of the bearing pin is linear to the angle of rotation. An Archimedean spiral has a continuous slope. This has the advantage that the rotation of the bearing pin by a certain angle always causes the same change in the radial distance of the support surface, regardless of the position of the bearing pin. The radial distance (B) of the bearing surface of the bearing pin axis thus results in B = k x (α + β), where k is a constant, α is the rotation angle of the bearing pin and β represents the angle between support point and line of movement of the flexible bend. If the support of the flexible arch on the support surface consists of a linear support, the angle β between support point and movement line of the flexible bend becomes zero.

Due to the fact that the flexible sheet on a bearing surface of the bearing pin facing side, however, has a support surface which is formed as a plane, the flexible sheet is located tangentially on the spiral bearing surface of the bearing pin. The line of movement along which the rotation of the bearing pin, the displacement of the flexible sheet is therefore not identical to the perpendicular to the tangent on which the flexible sheet rests. The perpendicular to the tangent of the support point of the flexible bend is at a certain angle to the displacement line along which the flexible bend by the rotation of the bearing pin is moved. In order to take this fact into account, in a particularly preferred embodiment, the spiral shape of the support surface of the bearing pin is provided such that, despite the difference between the support point of the flexible sheet on the bearing pin and the line of movement, a linear dependence between the rotation angle of the bearing pin and the distance ( A) exists between the bearing pin axis and the flexible bend in the direction of movement of the flexible bend. The distance (A) of the support point of the flexible sheet on the support surface of the bearing pin parallel to the line of movement of the flexible bend thus results in A = kx α, where k is a constant and α represents the rotation angle of the bearing pin.

In a preferred embodiment, the adjusting lever is held on the moving portion of the bearing pin. The adjusting lever is rotatably held on the bearing pin with a releasable locking. The lock comprises a locking screw and a two-piece clamping bolt. By contraction of the clamping bolt with the locking screw of the bearing pin is held in the adjusting lever on the clamping bolt frictionally. The clamping bolt is aligned in its shape along its longitudinal axis at least on one side of the shape of the bearing pin. Now, if the two halves of the clamping bolt pulled together, this causes a distortion of the clamping bolt against the bearing pin. It is also conceivable to execute a part of the adjusting lever elastically instead of a clamping bolt. With a locking screw of this elastic part of the adjusting lever can then be pressed against the bearing pin and cause a fixation of the adjusting lever on the bearing pin.

In order to make a basic setting or a change of each bearing of the flexible sheet, a device is provided which allows rotation of the bearing pin independent of the adjusting lever and independently of the other respective bearing points. For this purpose, it is provided in an advantageous embodiment that the movement portion of the bearing pin is provided at least partially with a toothing on its circumference. Next, an adjusting member is provided in the adjusting lever, which forms a reduction stage (such as a worm drive) with the toothing on the circumference of the bearing pin. With the adjustment can thus over the reduction stage of the bearing pin set in rotation and thus the flexible sheet are brought into the desired basic position. Since the displacement of the flexible bend is in a linear relationship to the rotational angle of the bearing pin, and the rotational angle of the bearing pin on the reduction stage with the rotation angle of the adjusting member is also in a predetermined ratio, a precise and predictable displacement of the flexible sheet can take place. For rotation of the adjusting member, this may be provided with a suitable coupling tool for a particular tool, this may for example be a hexagonal head, a hexagon socket or another type of known rotationally fixed coupling when using hand tools. After making an individual default setting of a bearing, the adjusting lever is in turn rotatably connected via the lock with the adjusting lever.

The fact that the bearing surface of the bearing pin causes only dependent on the rotation angle of the bearing pin displacement of the flexible sheet, it does not matter in what moment individual position is the spiral bearing surface of the bearing pin of each bearing. Further rotation of the bearing pin always leads to a linearly acting to the rotation angle displacement of the flexible bend.

The adjusting levers of the individual bearings are connected to a common slider. This connection causes the adjustment lever and the lock and the bearing pin are held against rotation. The holder of the adjusting lever in the slide is designed via a arranged in the slide radially aligned guide. On the adjusting lever a guide pin is provided, which engages in the guide groove. If the slider is now moved tangentially to the drum axis, this movement is transmitted via the guide pins on the adjusting lever and leads to a rotation of the adjusting lever about the bearing pin axis. By locking the adjusting lever on the bearing pin, the rotation of the adjusting lever is transmitted to the bearing pin. As a result, by the rotation of the bearing pin of the flexible bend in all bearings simultaneously and due to the spiral bearing surface of the bearing pin in all bearings shifted by the same amount radially. The shift is independent of the current individual setting of the individual bearings.

In a further embodiment, the slide is provided with a drive. This allows automatic adjustment of the flexible bend by a central control. The tangential movement of the slider is in a fixed relationship to the displacement of the flexible bend. About the lever and the spiral bearing surface of the bearing pin, the movement of the slider is translated, whereby a large movement of the slider leads to a small displacement of the flexible bend. This allows a high accuracy in the adjustment of the flexible sheet in steps of less than 0.01 mm.

If the drive of the slide is connected to a controller, which in turn is connected to a known measuring device for determining the carding gap, a cover actuator can be operated with the aid of the slide. A lid actuator is used for automatic adjustment of the carding gap between the revolving lids and the drum of a card. If the trimmings of the drum or the sets of the revolving cover are reground, for example, this change in the carding gap is detected by the measuring device of the controller and compensated automatically via the slide.

Figur 1

Schematische Darstellung einer Seitenansicht einer Wanderdeckelkarde nach dem Stand der Technik

Figur 2

Schematische Darstellung einer Ausführungsform einer Lagerstelle nach der Erfindung in einer Ansicht

Figur 3

Schematische Schnittdarstellung einer Ausführungsform an der Stelle Z-Z nach der Figur 2

Figur 4

Schematische Schnittdarstellung an der Stelle X nach der Figur 3

Figur 5

Schematische Schnittdarstellung an der Stelle Y nach der Figur 3

Figur 6

Schematische Schnittdarstellung einer weiteren Ausführungsform an der Stelle Z-Z nach der Figur 2

Figur 7

Schematische Darstellung einer Ausführungsform einer Lagerstelle

In the following the invention will be explained with reference to exemplary embodiments and explained in detail by drawings.

FIG. 1

Schematic representation of a side view of a Wanderdeckelkarde according to the prior art

FIG. 2

Schematic representation of an embodiment of a bearing according to the invention in a view

FIG. 3

Schematic sectional view of an embodiment at the point ZZ after the FIG. 2

FIG. 4

Schematic sectional view at the point X after the FIG. 3

FIG. 5

Schematic sectional view at the point Y after the FIG. 3

FIG. 6

Schematic sectional view of another embodiment at the point ZZ after the FIG. 2

FIG. 7

Schematic representation of an embodiment of a bearing

In the FIG. 1 a known revolving flat card 1 is shown, wherein flakes are fed from a hopper 2 a fiber feeding device 3 and a subsequent drum 4. The revolving flat card 1 comprises a single drum 4 (master cylinder or so-called drum), which is rotatably supported in a machine frame 5. The drum 4 works in a known manner with a traveling lid assembly 6, a fiber feeding device 3, and a fiber pickup 8 together, the latter in particular has a so-called takers 9. Carding elements and fiber guiding elements, which are not shown here in detail, can be arranged between the revolving lid arrangement 6, the fiber feeding device 3 and the fiber dispensing system 8. The fiber-receiving system 8 conveys the sliver 10 to a schematically indicated sliver storage 11.

At the aforementioned moving lid assembly 6, a plurality of traveling lids 13 is provided, wherein in the FIG. 1 only individual moving lid 13 are shown schematically. Currently used traveling lid assemblies 6 include closely spaced a plurality of traveling lids 13 that circulate. For this purpose, the moving lid 13 are supported in the vicinity of their respective end faces of endless belts 12 and moved against or with the direction of rotation of the drum 4. The support takes place on flexible sheet 7 on the underside of the revolving cover assembly 6. Sliding on the flexible sheet 7, the moving lid 13 are guided along the drum surface.

FIG. 2 shows a schematic representation of an embodiment of a bearing 20 of a flexible sheet 7 according to the invention. The flexible sheet 7 is shown in sections and stored on a plurality of bearings 20. At the bearing 20 of the flexible sheet 7 is held on a bearing pin 21. The bearing pin 21 is shown in section, so that the support surface 24 is shown on which the flexible sheet 20 rests. The support surface 24 of the bearing pin 21 is arranged spirally around the bearing pin axis 25. The bearing pin axis 25 is the axis of rotation of the bearing pin 21. The bearing pin 21 is rotatably mounted in the machine frame (not shown) so that the axis of rotation, respectively the bearing pin axis 25, is held stationary. On the bearing pin 21 The adjusting lever 26 is in turn held with a guide pin 30 in a guide groove 34 of a slider 35.

In a tangential movement 36 of the slider 35, all the adjusting lever 26 are rotated about the guide pins 34 about the bearing pin axes 25. Since the adjusting lever 26 is also non-rotatably connected to the bearing pin 21, the rotational movement of the adjusting lever 26 transmits to the bearing pin 21. Due to the rotational movement of the bearing pin 21 due to the spiral bearing surface 24 of the bearing pin, the distance A of the flexible sheet 7 from the bearing pin axis 25 changes Since the bearing pin 21 and thus the bearing pin axis 25 are held stationary in the machine frame, the flexible sheet 7 is moved radially away from the bearing pin axis 25 or towards the bearing pin axis 25. The direction of movement 37 of the flexible sheet 7 is dependent on the direction of rotation of the bearing pin 21 and the arrangement of the spiral bearing surface 24th

FIG. 3 shows in a schematic sectional view at the point ZZ after the FIG. 2 an embodiment of a bearing 20 according to the invention in a view. The bearing pin 21 has a movement section 22, a fastening section 23 and a bearing surface 24. On the support surface 24, which has a distance A from the bearing pin axis 25 depending on the position, the flexible sheet 7 is supported. In the mounting portion 23 of the bearing pin 21 is rotatably mounted in the machine frame 5. In the attachment portion 23, the bearing pin 21 has a diameter D which corresponds to at least twice the _maximum possible distance B of the bearing surface 24 from the bearing pin axis 25 (for the largest possible distance B _max see FIG. 7 ). In the movement section 22 of the bearing pin 21, an adjusting lever 26 is arranged. The adjusting lever 26 is rotatably connected via the lock 27 with the bearing pin 21. The bearing pin 21 is at least partially provided with a toothing 28 in the movement section 22. In this toothing 28 engages the adjusting lever 26 mounted adjusting member 29. For rotationally fixed mounting of the adjusting lever 26 is mounted on the adjusting lever 26 guide pin 30 is provided. The guide pin 30 is held by the slider 35 (see FIG FIG. 2 ). When loosening lock 27 can by turning the adjusting member 29 via the teeth 28th After the manual basic adjustment of the bearing 20, the lock 27 is tightened and any further adjustment of the bearing 20 takes place with the rotation of the adjusting lever 26. The rotation of the adjusting lever 26 is transmitted via the lock 27 directly to the bearing pin 21.

FIG. 4 shows a schematic sectional view at the point X after the FIG. 3 , The bearing pin 21 is shown in the movement section 22 at the location with the toothing 28. The toothing 28 is guided only over a part of the circumference of the bearing pin 21, namely over the part of the circumference, which corresponds to the spiral shape of the bearing surface of the bearing pin 21. The adjusting member 29 mounted in the adjusting lever 26 engages with its worm toothing in the toothing 28, which leads to a rotation of the bearing pin 21 upon rotation of the adjusting member 29. The adjusting lever 26 is secured via the guide pin 30 against rotation. The adjusting member 29 is provided with a head, which is designed for the use of a tool or can be operated by hand.

FIG. 5 shows a schematic sectional view at the point Y after the FIG. 3 , The bearing pin 21 is shown in the movement section 22 at the location with the lock 27 of the adjusting lever 26. The lock 27 consists of two clamping bolt halves 31, 32 which are inserted into a bore in the adjusting lever 26. In this case, a first clamping bolt half 31 is introduced from the one side of the bearing pin 21 and a second clamping bolt half 32 from the opposite side of the bearing pin 21 in the bore in the adjusting lever 26. With a locking screw 33, the two clamping bolt halves 31, 32 are pulled together, while the first clamping bolt half 31 is provided with a corresponding internal thread. The two clamping bolt halves 31, 32 are provided in the region of the bearing pin 21 with a corresponding to the bearing pin Anformung, so that by the contraction of the clamping bolt halves 31, 32 of the adjusting lever 26 rotatably supported on the bearing pin 21. The same effect could also be achieved in that one side of the adjusting lever 26 is made elastic and with the locking screw 33 of the elastic region of the adjusting lever 26 are pulled together with the rigid region of the adjusting lever 26 and thereby the adjusting lever 26 is rotatably connected to the bearing pin 21.

FIG. 6 shows a schematic sectional view of another embodiment at the point ZZ after the FIG. 2 a bearing 20. In contrast to the embodiment of the FIG. 3 the bearing surface 24 of the bearing pin 21 is disposed within the mounting portion 23. The attachment portion 23 adjoins the movement portion 22 and is interrupted by the support surface 24. The diameter D of the bearing pin 21 corresponds to the movement section 22 side facing the diameter D of the FIG. 3 , On the side facing away from the movement portion 22 of the mounting portion, however, the bearing pin 21 has a smaller diameter d, which is smaller than twice the minimum distance B _{min of} the bearing surface 24 of the bearing pin axis (see FIG. 7 ). The execution of the movement section 22 with the adjusting lever 26 corresponds to the embodiment according to FIG. 3 , In the movement section 22 of the bearing pin 21, an adjusting lever 26 is arranged. The adjusting lever 26 is rotatably connected via the lock 27 with the bearing pin 21. The bearing pin 21 is at least partially provided with a toothing 28 in the movement section 22. In this toothing 28 engages the adjusting lever 26 mounted adjusting member 29. For rotationally fixed mounting of the adjusting lever 26 is mounted on the adjusting lever 26 guide pin 30 is provided. The bearing pin 21 is mounted in its mounting portion 23 on both sides of the support surface 24 in the machine frame 5. As a result, the forces applied by the flexible sheet 7 on the bearing pin 21 forces are absorbed in two bearing positions of the machine frame 5 and the bending stress of the bearing pin 21 is reduced compared to the embodiment according to FIG. 3 ,

FIG. 7 shows a schematic representation of a bearing 20. The bearing pin 21 with the spiral bearing surface 24 is rotatably held in its bearing pin axis 25 stationary in the machine frame. The flexible sheet 7 rests tangentially on the bearing surface 24 of the bearing pin 21 with its supporting surface formed as a plane. This support point 40 determines the distance B _{(α + β) of} the bearing surface 24 of the bearing pin axis 25 measured in a rotated by the angle β to the direction of movement 37 of the flexible sheet 7 plane. However, this distance B _{(α + β) of} the flexible sheet 7 from the bearing pin axis 25 does not coincide with the radial distance A _{(α) of} the bearing surface 24 from the bearing pin axis 25 in the direction of movement 37 of the flexible sheet 7. Due to the fact that the flexible sheet 7 on one of the bearing surface 24 of the bearing pin 21 facing side has a support surface which is formed as a plane, the flexible sheet 7 is tangent to the spiral bearing surface 24 of the bearing pin 21 on the support point 40. The support point 40 of the flexible sheet 7 is rotated by an angle β to the line of movement 41 of the flexible sheet 7. The spiral bearing surface 24 of the bearing pin 21 is formed such that at a rotation of the bearing pin 21, the distance A _{(α) of} the flexible sheet 7 to a changes from the angle of rotation α linearly dependent amount. This results in the change of the distance A _(α) from a multiple of a constant with the change of the rotation angle a.

The spiral bearing surface 24 extends after FIG. 7 over half the circumference of the bearing pin 21. This results in a smallest possible distance B _{(α + β)} to B _min and a _maximum distance B _{(α + β)} to B _max . The difference between B _min and B _max results in the maximum possible adjustment of the flexible bend 7 on its movement line 41.

Legend

1

revolving

2

hopper

3

Fiber feeding device

4

drum

5

machine frame

6

Revolving flat arrangement

7

flexible bend

8th

Fiber collector system

9

customer

10

sliver

11

Sliver tray

12

endless belt

13

revolving flat

20

depository

21

bearing bolt

22

movement section

23

attachment section

24

bearing surface

25

Bearing pin axis

26

adjusting

27

lock

28

gearing

29

adjusting

30

guide pin

31, 32

Clamp bolt halves

33

locking screw

34

guide

35

pusher

36

Tangential motion slider

37

Movement direction flexible bend

40

support point

41

Movement line Flexibelbogen

A ( _α )

Distance of the flexible arch from the bearing pin axis

B _{(α + β)}

Radial distance of the bearing surface from the bearing pin axis

B _max

Largest distance B

B _min

Smallest distance B

D

First diameter of the bearing pin in fixing section

d

Second diameter of the bearing pin in mounting section

α

Angle of rotation of bearing pin

β

Angle between support point and movement line Flexible bend

Claims (14)

1. A support of a flexible bend (7) in a revolving flat card (1) comprising a cylinder (4) and a cylinder axis, wherein the support includes at least three bearing points (20), each of which has a bearing bolt (21) and an adjusting lever (26), wherein the flexible bend (7) is held, at each bearing point (20), on the bearing bolt (21) in such a way that a rotational motion (22) of the bearing bolt (21) brings about a displacement of the flexible bend (7) radially with respect to the cylinder axis, wherein the bearing bolt (21) has a bearing bolt axis (25), a fastening portion (23), a moving portion (22), and a contact surface (24) for the contact of the flexible bend (7), wherein the contact surface (24) is formed by a surface, which spirals around the bearing bolt axis (25), characterized in that the adjusting levers (26) are connected to a common slider (35).
2. The support according to claim 1, characterized in that the spiral shape is an Archimedean spiral and, therefore, a decrease or an increase in the radial spacing distance (B) of the contact surface (24) from the bearing bolt axis (25) during a rotation of the bearing bolt (21) is linear with respect to the rotational angle.
3. The support according to claim 1, characterized in that the spiral shape of the contact surface (24) of the bearing bolt (21) is provided in such a way that there is a linear dependence between the rotational angle (α) of the bearing bolt (21) and the spacing distance (A) between the bearing bolt axis (21) and the flexible bend (7) in the direction of movement (37) of the flexible bend (7).
4. The support according to one of the preceding claims, characterized in that the radial spacing distance (B) of the contact surface (24) from the bearing bolt axis (25) decreases or increases by 5% to 30% in a helical manner along the course of said contact surface during at least one-half the circumference of the bearing bolt (21).
5. The support according to one of the preceding claims, characterized in that the fastening portion (23) is disposed between the moving portion (22) and the contact surface (24) in the direction of the bearing bolt axis (25).
6. The support according to one of claims 1 to 4, characterized in that the fastening portion (23) is split by the contact surface (24) disposed within the fastening portion (23).
7. The support according to one of the preceding claims, characterized in that the adjusting lever (26) is held on the moving portion (22) of the bearing bolt (21).
8. The support according to one of the preceding claims, characterized in that the adjusting lever (26) is non-rotatably held on the bearing bolt (21) by means of a releasable locking mechanism (27).
9. The support according to one of the preceding claims, characterized in that at least part of the circumference of the moving portion (22) of the bearing bolt (21) is provided with a tooth system (28).
10. The support according to claim 9, characterized in that an adjusting element (29) is provided in the adjusting lever (26), which, in combination with the tooth system (28) on the circumference of the bearing bolt (21), forms a worm gear.
11. The support according to one of the preceding claims, characterized in that the contact surface (24) has a maximum radial spacing distance (B_max) from the bearing bolt axis (25) that is not greater than one-half the diameter (D) of the bearing bolt (21) in its fastening portion (23).
12. The support according to one of the preceding claims, characterized in that the adjusting lever (26) is held by means of a guide pin (30) in the slider (35) in a radially oriented guide groove (34).
13. The support according to one of the preceding claims, characterized in that the slider (35) is provided with a drive (36).
14. A revolving flat card (1) comprising a cylinder (4), which is provided with a cylinder clothing, and comprising a revolving flat assembly (6), which is formed of a plurality of interconnected revolving flats (13), which are guided on a flexible bend (7), characterized in that the flexible bend (7) is equipped with a support according to one of the claims 1 to 13.

Images