EP1936013A1 - Draw-off roller for a combing machine - Google Patents

Abstract

The tapered detachment roller has a cylindrical central section (M), with two successive conical sections (K1, K2) at each end. The second (K2) of these has greater taper than the first (K1). There are alternatively up to six conical end sections (K1-K6) in succession. Circumferential surfaces (U1-U4) of the conical sections (K1-K4) run in a line of curvature expressed by a formula provided in the disclosure. Further design details are elaborated.

Description

The invention relates to a tear-off roller of a combing machine on which a pressure roller rests, which is acted upon at its two ends by pressure medium transversely to the axis of rotation of the tear-off roller.

For the tear-off and soldering process on a combing machine, the end of a cotton combed out beforehand by a combing segment of a round comb is fed via the nipper unit to a subsequent detaching roller pair. The Abreisswalzenpaar is driven by a Pilgerschrittbewegung over which the previously formed nonwoven fabric (short: fleece) by a certain amount in the direction of the nipper unit (short: pliers) is returned. In the process, the end (tuft) of the wadding delivered by the tongs and combed out is laid on the end of the fleece conveyed back by a partial amount. Subsequently, the direction of rotation of the Abreisszylinderpaares reversed, whereby the end of the combed cotton, which partially overlaps with the end of the fleece, passes into the nip of the Abreisszlinderpaares. The clamped over the nip line fibers of the Watteendes be pulled out of the cotton wool end, or demolished.
In order to obtain a uniform deduction and further transport of the fibers over the entire width of the Abreisszylinderpaares, it is necessary that the applied clamping force in the nip of the Abreisszylinderpaares approximately uniform over the entire width of the Watteendes or the fleece.

In the conventional combers two successively arranged and jointly driven Abreisswalzen are usually provided, on each of which a pressure roller rests. The pressure rollers are acted upon in the region of their ends by a device with a compressive force. Mostly pneumatic pressure cylinders are used. The pressure rollers are usually provided with a softer sheathing (eg rubber) and are driven by friction from the tear-off rollers.
The first tear-off, which is loaded with a pressure roller, is responsible for the actual departure, while the second tear-off, which also with a Pressure roller is loaded, is responsible for the consolidation of the solder joint and the transport of the web. However, it is also conceivable a solution in which can be dispensed with the second Abreisswalzenpaar. Such a solution is z. B. from the published WO2006 / 012758 refer to. That is to say, the special embodiment of a tear-off roller claimed below also refers to solutions in which only one tear-off roll with an associated pressure roll is used.
By transmitting a compressive force on the pressure rollers in the region of their outer ends, a slight deflection of the pressure rollers. Since the pressure rollers are exposed to high accelerations due to the high comb numbers and the pilgrim step movement, it is necessary to keep their masses as small as possible. Therefore, they usually have a small diameter, which of course reduces the flexural rigidity along their length. As a result of this deflection, higher pressure loads occur, in particular in the edge region of the nonwoven fabric, than in the middle region. This leads to qualitative impairment of web formation in these peripheral areas.
To achieve a uniform across the width of the tear roller pressure force already several solutions have been proposed. Most proposals relate to a special design of the pressure rollers. In order to take into account the resulting deflection of the pressure roller when applying the pressure force, in the example of DE-PS 405360 proposed to form the pressure roller from a sleeve which is mounted on a spindle. In this case, the spindle runs conically in the region of both ends of the sleeve, whereby the, applied at both ends of the spindle pressure force is transmitted to the sleeve at a distance from the edge regions of the sleeve. A similar embodiment is also in the embodiment of EP-336 217 shown.
In the reference " The Wakoflex roller, a new roller concept "out" textile practice international 1988 June / pages 654-656 "Different types of roller systems are presented to achieve even pressure distribution across the width of the rollers, examples of pressure treatment of fabric webs, where the rollers used there are typically much longer than the breaker cylinders on the web Coming machine, too attempts to compensate for the deflection of the rollers by appropriate execution of the roller bearings.
In the DE-PS 644 120 a barrel-shaped tear-off roller with a barrel-shaped pressure roller is shown. A treadmill is placed around the tear-off roller. By the barrel-shaped design of the tear-off roller and the pressure roller a uniform pressure load over the width of the rollers should be secured.
Also, there are already experiences with designs of Abreisswalzen, in which at both ends in each case a conical section was provided. Although this brought an improvement but not yet the hoped-for success.

The previously described known solutions sometimes have very complex and special bearings, which are very expensive to manufacture and during assembly. Also barrel-shaped designs, or combinations of rollers are more expensive to produce than the production of cylindrical rollers. Further problems with the use of such rolls arise when they must be reground in the spinning mill. The spinning mills are usually not equipped with special grinding machines to z. B. be able to regrind barrel-shaped rollers.

The invention thus has the object to avoid the disadvantages of known designs and to propose the production of cost-effective Abreisswalzen for a comber, by means of which, in conjunction with each of a pressure roller, an approximately uniform pressure distribution over the length of the Abreisswalzen can be achieved. In a combing machine with z. B. eight combing heads sixteen such Abreisswalzen needed.

To solve this problem, it is proposed that the tear-off roller (one of several) is designed with a cylindrical center region and the ends adjoining on both sides are each provided with at least two successive conical sections, wherein - viewed in the direction of the respective end of the tear-off roller each subsequent conical section has a greater taper than the preceding conical section.

berechnet.Preferably, the successive conical portions may be formed such that their successive peripheral surfaces extend in a bending line, which is derived from the formula $$w\left(x\right)=\frac{{\mathit{ql}}^2}{24\mathit{Ely}}\left[\frac{x}{l}-2{\left(\frac{x}{l}\right)}^3+{\left(\frac{x}{l}\right)}^4\right]$$

calculated.

This formula is the reference "DUBBEL-Taschenbuch" page C20; Springer Verlag (ISBN 3-540-57650-9 / 18th edition) taken
In this case, "w (x)" means the deformation in the y-direction with respect to the x-axis which is parallel to the axis of rotation D, "I" the length of the roller, "q" the compressive load, "E" the elastic modulus (N / mm ² ) and "I _y " is the area moment in the y-direction.

With this proposed shaping of the Abreisswalzen the resulting deflection of the associated pressure rollers can be counteracted to ultimately obtain an approximately uniform Druckbelassung along the length of the rolls during the tearing and soldering. The pressure rollers used in this case may have a cylindrical shape, whereby a regrinding in the spinning can be easily performed.
With the proposed embodiment, in particular the pressure peaks existing in the area of the introduction of pressure in previous solutions can be reduced, as will be explained in more detail in subsequent embodiments. As a result, the edge regions of the fleece can be better controlled, since they are exposed to lower pressure loads.

Preferably, it is proposed that the adjoining the cylindrical portion ends of the tear-off roller can each have two to six consecutive conical sections.
In order to adapt the shaping of the tear-off roller to the positions of the initiation pressure force, it is further proposed that the length of the cylindrical section is greater than the length of the respectively adjacent first conical section and the lengths of the subsequent further conical sections are each smaller than the length of the respective first conical sections.

Preferably, the attachment of two, on both sides of the central portion conical sections is proposed, with the respective first conical portion adjoining the cylindrical portion, with a taper at an angle (α) in the range between 0 ° 2 'and 0 ° 10th 'is provided and the subsequent second conical section has a taper under a coil (β) in the range between 0 ° 12' and 0 ° 25 '.
To assist the tear-off process (secure clamping during the tear-off process), it is further proposed that the take-off roll be provided with a flute.
The flute can extend over the cylindrical and conical sections of the tear-off roller.
Preferably, the flute has a constant depth of flute over all sections of the tear-off roller. This ensures the same conditions with respect to the tearing force over the entire length of the tear-off.
The Kannelur can z. B. at an angle (β) to the axis of rotation of the tear-off,
Furthermore, it is proposed that the resting on the tear roller pressure roller is cylindrical and is provided with a sheath which has a lower degree of hardness than the degree of hardness of the surface of the tear-off roller. This ensures that a sufficient frictional force is present to rotate the pressure rollers via friction, even at higher speeds via the driven tear-off rollers under the action of the clamped fleece. In addition, provided with a softer surface pressure roller material fluctuations - seen over the roll length - in the fleece adapt or compensate.
In addition, it is proposed that the pressure roller resting on the tear-off roller-seen over its length-has a shape deviating from the cylindrical shape. It is conceivable that the pressure roller is also provided in the region of its ends with conical sections. However, deviation of the pressure rollers from the cylindrical shape should, if possible, be avoided in order to allow easy regrinding in the spinning mill (as already described).

Furthermore, to compensate for the deflection of the pressure roller resting on the tear roller pressure roller have a cylindrical sleeve which is fixed in its central portion on a central portion of a roll core.
Furthermore, an embodiment of a tear-off roller according to the invention is proposed, wherein no cylindrical central region is provided and, starting from the center of the tear-off roller, a plurality of conical sections are arranged at both ends whose peripheral surfaces taper towards the respective end of the tear-off roller. In this case, their peripheral surfaces run within a bending line, which is calculated from the formula described above. Thus, the contour of the tear-off roller can be optimally matched to the bending forces that occur, as well as a uniform pressure distribution is achieved. Of course, this version can also be provided with a continuous Kannelur.
There are also other embodiments of pressure rollers conceivable that ensure an approximately uniform pressure distribution over the length of the pressure roller in connection with the tear-off roller according to the invention and in particular pressure peaks in the edge region of the fleece are avoided even when heated during operation.

Fig. 1

eine schematische Seitenansicht einer Kämmmaschine

Fig. 2

eine Teilansicht einer bekannten Abreisswalze mit Druckwalze mit Druckverteilungsdiagramm

Fig. 3

eine erfindungsgemässe Ausführung einer Abreisswalze mit Druckwalze mit Druckverteilungsdiagramm

Fig. 4

eine vergrösserte Teilansicht nach Fig. 3

Fig. 4a

eine Teilansicht einer Schnittdarstellung A-A nach Fig. 4

Fig. 5

ein weiteres Ausführungsbeispiel nach Fig. 3

Fig. 6

ein weiteres Ausführungsbeispiel nach Fig. 3 mit anderer Druckwalze

Fig. 7

ein weiteres Ausführungsbeispiel nach Fig. 6

Fig. 8

eine vergrösserte Teilansicht einer erfindungsgemässen Ausführung einer Abreisswalze.

Further advantageous embodiments of the invention are shown and described in detail with reference to subsequent embodiments.
Show it:

Fig. 1

a schematic side view of a combing machine

Fig. 2

a partial view of a known Abreißwalze with pressure roller with pressure distribution diagram

Fig. 3

an inventive embodiment of a tear-off roller with pressure roller with pressure distribution diagram

Fig. 4

an enlarged partial view Fig. 3

Fig. 4a

a partial view of a sectional view AA after Fig. 4

Fig. 5

a further embodiment according to Fig. 3

Fig. 6

a further embodiment according to Fig. 3 with other pressure roller

Fig. 7

a further embodiment according to Fig. 6

Fig. 8

an enlarged partial view of an inventive embodiment of a tear-off roller.

Fig. 1 shows an embodiment of the prior art. In this case, the supplied from a nipper unit 1 (short: pliers) cotton web 2 is fed via a feed cylinder 3 a Abreisswalzenpaar 5. The Abreisswalzenpaar 5 consists of a tear-off roller 5a and a pressure roller 5d. From the open forceps 1, which is located in a forward position, outstanding tuft 7 (end of the cotton web) is placed on the rear end 8 of a Kammzugvlieses or nonwoven fabric 10 and with this due to the forward movement of the Abreisswalzenpaares 5 in the nip of Abreisswalzenpaares 5 transferred. About the clamping action in the nip, the fibers, which are not held back by the retaining force of the cotton web 2, or by the pliers (nip of the feed cylinder), torn from the composite of the wadding. In this tearing off the tuft 7 is additionally pulled through the needles of a Fixkammes 9. The Fixkamm 9 causes the combing out of the rear part of the withdrawn tuft as well as the retention of nits, impurities and the like. Due to the speed differences between the wadding web 2 and the withdrawal speed of the Abreisswalzenpaares 5, the withdrawn fiber package is warped to a certain length. Following the Abreisswalzenpaar 5 another Abreisswalzenpaar 6 is arranged, which also consists of a tear-off roller 6a and a pressure roller 6d. However, the actual tear-off is performed by the first Abreisswalzenpaar 5. In the tearing described, there is an overlap or doubling of the front end of the torn off or withdrawn fiber packet with the rear end 8 of the fiber web 10. As soon as the tearing off, or the soldering is completed, the pliers return to a rear position back, in which it is closed and the pliers protruding tuft 7 presents a comb segment 12 of a circular comb 13 for combing out. Before now the nipper unit 1 returns to its forward position, the Abreisswalzenpaare 5 and 6 perform a reversing, whereby the rear end 8 of the fiber web 10 to a certain Amount is returned. This is necessary to achieve a necessary for a subsequent soldering coverage.

Fig. 2 shows a known embodiment of a Abreisswalzenpaares 5 with a tear-off roller 5a and a pressure roller 5d. The tear-off roller 5a is mounted rotatably in the machine frame MS of the combing machine via a shaft journal 11 in bearings LA shown schematically. The drive of the tear-off roller 5a as well as the drive of the tear-off roller 6a not shown here take place via a gear G, which is connected to a drive AT (eg a motor). As is generally known, the tear-off rollers 5a, 6a are driven via the gear with a pilgrim step movement. Above the tear-off roller 5a, a pressure roller 5d is arranged, which is mounted via a shaft journal 17 in not shown receptacles and rests in the operating position on the tear-off roller 5 under a compressive load. This pressure load is generated by two pneumatic pressure cylinder Z, which are also stored in the receptacle, not shown. An embodiment of a storage of the pressure rollers 5a, 6a, or the pressure cylinder Z in a recording is z. B. from the DE-A1-4229448 refer to.
In the nip line KL between the tear-off roller 5a and the pressure roller 5d, the non-woven fabric 10 is clamped.
The pneumatic pressure cylinders Z are connected in operation via the line 14, or 15 via a valve V to a pressure source Q and pressurized with compressed air. The control of, or the valves V is carried out by a control unit ST, via which also the drive AT is controlled.
By introducing the pressure force in the area of the outer ends of the impression cylinder. 5d, 6d and by the corresponding length of the pressure rollers 5d, 6d creates a bending force on the pressure rollers, through which the pressure roller is bent over its length, as shown schematically from the change in the position of the axis of rotation DA in the position marked DA ' , As a result of this bending, a pressure distribution of the pressure force P applied to the nonwoven fabric arises, which can be seen from the diagram shown above the pressure roller 5d. It can be seen that the pressure force P1 in the edge regions of the nonwoven fabric 10 on largest, while the pressure load of the nonwoven fabric due to the deflection of the pressure roller in the central region with Pm is the lowest.
As a result, the effect occurs that the edge region R of the fibrous web 10 is undesirably deformed by the high loads (P1) prevailing there. As a result of this process shows that the edge region of the nonwoven fabric is uneven and dirty. This results in a visually uneven fiber web and can also lead to loss of quality (unevenness) in the fiber sliver formed below.

To eliminate these disadvantages is z. B. an embodiment proposed which in Figure 3 is shown in more detail. Except for the modified design of the tear-off roller 5a, the remaining elements correspond to the elements which already in the embodiment of Fig.2 were shown. Therefore, these parts are no longer in the embodiment of Figure 3 described. The tear-off roller 5a, as well as the tear-off roller 6a, not shown, are provided, following a cylindrical middle section M, at both ends with two conical sections K1 and K2.
To compensate for the occurring bending force on the impression cylinder, the lengths of the central portion M, the first and second cone K1, K2 have different lengths. The cylindrical middle section M has the greatest length with L1. The length L2 of the adjoining cone K1 is smaller than the length L1 of the central portion M and greater than the length L3 of the adjoining cone K2.
As in particular from the enlarged partial view in Figure 4 can be seen, the first cone K1 has a smaller taper angle α than the taper angle β of the second and outer cone K2. In this case, the taper angle α can be between a range of 0 ° 2 'and 0 ° 10', while the taper angle β can be performed in a range between 0 ° 12 'and 0 ° 25'.

By this inventive design of the Abreisswalzen 5a (6a), the occurring bending of the pressure roller 5d (6d) can be substantially compensated, as shown in the diagram above the pressure roller in Figure 3 can be seen. It is the Force P2 in the edge region R of the fibrous web 10 only slightly larger than the compressive force Pm in the central region, whereby the previously in the example of Fig.2 described disadvantages are compensated. That is, the resulting deflection of the pressure roller 5d, especially after heating during operation, are compensated by the shape of the tear-off roller 5a. With appropriate design of the cone K1 and K2 can even be achieved that the force P2 in the edge region even smaller than the pressing force Pm.

How out Fig. 4 can be seen, the tear-off roller 5a (6a) provided with a Kannelur K, which can extend obliquely at an angle x to the axis of rotation D of the tear-off roller. From the partial view of the sectional view in 4a it can be seen that the Kannelur has a Kannelurtiefe KT. In order to keep the tear-off effect constant over the entire length L of the tear-off roller 5a (6a), it is possible for the flute depth KT to be kept at a constant level even in the area of the cone K1 and K2. Although this is somewhat more expensive in terms of production technology, it results in the previously described constant tear-off effect over the entire length of the pair of detaching rollers.
Depending on the size of the taper angles α, β of the cone K1, K2, it is also conceivable to let the flute extend from the middle cylindrical part M at a parallel distance over the entire length L of the tear-off roller 5a. In this case, the flute depth - towards the ends of the tear-off roller - would decrease in the region of the cone K1, K2. If the respective taper angle is kept relatively small, this reduction in the Kannelurtiefe is relatively small and can be neglected.
Fig. 5 shows another embodiment similar to Fig. 3 However, with the difference that instead of two outer cone on a central part M of the tear-off roller on each side of a central part M three cone K1, K2 and K3 are provided. Here, too, the respective lengths L1 to L4 decrease outwardly to the respective end of the tear-off roller 5a (6a). Likewise, the taper angle α, β and δ starting from the cone K1 to the cone K3 is formed increasing. The taper angle δ for the cone K3 is in the Figure 5 for reasons of clarity not shown, but is in accordance with the in Figure 4 shown angles α, β to see.

Although the attachment of the three cones K1 to K3 shown here is somewhat more complicated in terms of production technology, the adaptation of the shape of the tear-off roller can be adapted even more precisely to the bending line of the respective pressure roller. This means that the pressure force P3 in the edge region R corresponds approximately to the pressure force Pm in the middle region M or may even be lower.
For further adjustment of the compressive force in the edge regions R to the compressive force Pm in the central region, embodiments may come into play, which have up to six cones on each side of the central cylindrical section M. Here, however, one must decide between the actual benefit and the manufacturing effort.

Fig. 6 shows a further embodiment, wherein the tear-off roller 5a according to the embodiment of Figure 3 is executed. In contrast, however, the pressure roller 5e is designed differently than the pressure roller 5d. The pressure roller 5e here consists of a sleeve 20 (which is provided, for example, with a rubber coating), which is mounted on a core 21 in its central region. The core 21 is mounted on a shaft 22, via which the pressure roller 5e is mounted in recordings not shown. In this embodiment, the initiation of the compressive force P in the center region of the tear-off roller, whereby the bending of the pressure roller 5e is lowered in the edge region R and in combination with the outer cone K1, K2 of the tear roller an approximately uniform compressive force (clamping force) over the length L of the tear-off roller can be achieved.
Furthermore, in the embodiment of the Figure 7 an embodiment shown, wherein the tear-off roller 5a is also provided with two cone K1, K2 on both sides of the middle part M. The pressure roller 5h, which cooperates with this tear-off roller 5a, has in each case two cones K5, which taper towards the end of the pressure roller, following a cylindrical middle part 25. In each case a shaft journal 26 is mounted in the end regions of the pressure roller 5h, via which the pressure roller 5h is mounted in receptacles, not shown. In cooperation with the tear-off roller 5a, which is provided with two conical sections K1, K2 on both ends, the provided cone K5 of the pressure roller 5d can additionally reduce the cause increased pressure load P5 in the edge region of the nonwoven fabric 10, so that the pressure distribution over the entire width of the nonwoven fabric is approximately equal.

berechnet. Bei dieser Ausführung ist kein zylindrischerIn Fig. 8 an enlarged partial view of a tear-off roller 5a is shown, wherein the peripheral surfaces U1 to U4 of, from the center M1 of the tear-off roller 5a, respectively in the direction of its two ends juxtaposed conical sections K1 to K4 in a bending line BL extending from the formula $w\left(x\right)=\frac{{\mathit{ql}}^2}{24\mathit{Ely}}\left[\frac{x}{l}-2{\left(\frac{x}{l}\right)}^3+{\left(\frac{x}{l}\right)}^4\right]$

calculated. This version is not cylindrical

Section provided. That is, the tear-off roller 5a tapers in front of its center M1 on both sides evenly towards its ends. As indicated schematically, this tear-off roller can also be provided with a flute K, as in the exemplary embodiment of FIG Figure 4 was shown and described. The explanation of the formula values has already been made in the input description. Of course, this embodiment may also be provided with a cylindrical central portion (not shown).

There are still many, not shown variants in the execution of the pressure rollers possible, which can cooperate with the invention trained Abreisswalzen.
However, it is desirable to maintain the cylindrical shape of the pressure rollers, if possible, to ensure easy re-grinding of the pressure rollers in the spinning mill.
The proposed inventive design of the Abreisswalzen the elimination of the pressure peaks in the edge region and the wear of the rollers can be reduced, thereby increasing their life.
In addition, it is also possible to increase the Kammspielzahl without the wear increases to an undesirable degree.

Claims (13)

Removal roller (5a, 6a) of a comber on which a pressure roller (5d, 6d) rests, which is acted upon at both ends by pressure means (Z) transversely to the axis of rotation (D) of the tear-off, characterized in that the tear-off roller (5a, 6a ) has a cylindrical central region (M) and the ends adjoining on both sides are each provided with at least two successive conical sections (K1, K2), wherein - viewed in the direction of the respective end of the tear-off roller (5a, 6a) - the respectively subsequent conical Section (K2) has a larger taper (α, β), as the previous conical section (K1). Tear-off roller (5a, 6a) according to Claim 1, characterized in that the ends of the tear-off roller (5a, 6a) adjoining the cylindrical section (M) each have two to six successive conical sections (K1-K6). Tear-off roll (5a, 6a) according to claim 2, characterized in that the circumferential surfaces (U1-U4) of the successive conical sections (K1-K4) run in a bending line (BL), which consists of the formula: $$w\left(x\right)=\frac{{\mathit{ql}}^2}{24\mathit{Ely}}\left[\frac{x}{l}-2{\left(\frac{x}{l}\right)}^3+{\left(\frac{x}{l}\right)}^4\right]$$

results. Tear-off roller (5a, 6a) according to any one of claims 1 to 2, characterized in that the length (L1) of the cylindrical portion (M) is greater than the length (L1) of each adjoining first conical portion (K1) and the lengths (L2, L3) of the subsequent further conical sections (K2, K3) are each smaller than the length (L1) of the respective first conical sections (K1). Tear-off roller (5a, 6a) according to claim 4, characterized in that on both sides of the central portion (M) in each case two conical sections (K1, K2) are provided are, wherein each of the first conical portion (K1), which is directly adjacent to the cylindrical portion (M), provided with a taper at an angle (α) in the range between 0 ° 2 'and 0 ° 10' and the subsequent second conical section (K2) has a taper under a coil (β) in the range between 0 ° 12 'and 0 ° 25'. Tear-off roller (5a, 6a) according to one of the preceding claims, characterized in that the withdrawal roller (5a, 6a) is provided with a flute (K). Tear-off roll (5a, 6a) according to claim 6, characterized in that the flute (K) extends over the cylindrical and conical portions (M, K1, K2) of the tear-off roll (5a, 6a). Tear-off roller (5a, 6a) according to claim 7, characterized in that the flute (K) extends over all sections (M, K1, K2, K3) of the tear-off roller (5a, 6a) with a constant flute depth (KT). Tear-off roller (5a, 6a) according to claim 7 or 8, characterized in that the flute (K) extends at an angle (x) to the axis of rotation (D) of the tear-off roller (5a, 6a). Tear-off roller (5a, 6a) according to one of the preceding claims, characterized in that the pressure roller (5d, 6d) resting on the tear-off roller (5a, 6a) is cylindrical and provided with a sheath (U) having a lower degree of hardness, as the degree of hardness of the surface of the tear-off roller (5a, 6a). Tear-off roll (5a, 6a) according to Claim 1, characterized in that the pressure roll (5d, 6d) lying on the tear-off roll (5a, 6a) - seen over its length (Ld) - has a form deviating from the cylindrical shape. Tear-off roll (5a, 6a) according to claim 1, characterized in that on the tear-off roller (5a, 6a) resting pressure roller (5d, 6d) has a cylindrical sleeve (20) which in its central portion on a core (21) of a shaft (22) is attached. Removal roller (5a, 6a) of a comber on which a pressure roller (5d, 6d) rests, which is acted upon at both ends by pressure means (Z) transversely to the axis of rotation (D) of the tear-off, characterized in that the tear-off roller (5a, 6a ), starting from its center (M1), at its two ends at least two to six consecutive conical sections (K1, K2), wherein - seen in the direction of the respective end of the tear roller (5a, 6a) - the subsequent conical Section (K2, K3, K4) has a greater taper than the preceding conical section and the peripheral surfaces (U1-U4) of the successive conical sections (K1-K4) in a bending line (BL), which consist of the formula: $$w\left(x\right)=\frac{{\mathit{ql}}^2}{24\mathit{Ely}}\left[\frac{x}{l}-2{\left(\frac{x}{l}\right)}^3+{\left(\frac{x}{l}\right)}^4\right]$$

results.

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