EP2426239A1 - Round comb of a combing machine - Google Patents

Abstract

The comb has a base body (20) secured on a shaft (15) in a torque-proof manner. The base body has a hollow profile i.e. aluminum extruded profile, with an outer arcuate portion (23) for retaining a combing set (G). An inner portion (22) lies opposite to the outer portion. A semicircular trough (21) is opened in a direction of the shaft and extends in a longitudinal direction of the hollow profile. The body and an attaching part (S3) are provided on the trough. The body and a mass balancing element (AG1) are braced against each other transverse to the longitudinal direction of the shaft.

Description

The invention relates to a circular comb for a comber with a base body which is rotatably mounted on a shaft and carries on its outer circumference a Kämmgarnitur, wherein - seen in the radial direction of the shaft - attached to the, the Kämmgarnitur opposite side of the shaft a mass balance element is.

Such circular combs are used for combing machines for combing a fiber mass presented (cotton, wool, etc.), wherein the presentation of the pulp in the form of wound on sleeves wafers (short: winding) or in the form of individual slivers can be done.
The Kammspielzahlen (Kammspiel / Minute) have increased significantly in recent years, which also brings an increase in productivity.
The requirements for such a circular comb have been increased, for. B. when the circular comb no longer has a continuous speed, but is driven by a discontinuous rotational movement to better tune the system to the combing process. Such an embodiment is z. B. in the Japanese Patent Publication No. 58-57529 shown and described.
By this discontinuous movement high demands are placed on the drive of the circular comb, especially when the relatively large mass of the circular comb accelerates, or must be delayed.
The combing machine used in the circular combs consist of a round-head carrier, which is provided with a clamping hub, with which it is rotatably mounted on a driven circular comb shaft. On a partial circumference of the circular comb carrier a combing segment is fixed, with which the presented by a nipper unit end of the fiber mass (also called fiber tuft) is combed out. Such a device is z. B. from the published DE 101 63 663 A1 and DE 25 03 976 B2 refer to.
The combing segment can be composed of several parts, wherein z. B. a base body may be provided on which a Kammgarnitur is attached. In In this case, the base body is releasably connected to the circular comb carrier. There may also be several comb segments.
Since the combing segment is mounted on one side on the circular comb carrier, balancing of the mass on the opposite side of the combing segment requires mass balancing, so that no imbalance arises, or mass vibrations are avoided. In the solutions used hitherto, the circular comb carrier has been produced as a cast part, the casting being provided with an additional mass on the opposite side of the fastening point of the combing segment.
Although the mass of the combing segment is compensated by this embodiment, the circular comb carrier thus formed itself has a large and heavy mass, which must be permanently accelerated and decelerated in the event of a discontinuous circular comb movement. By using a discontinuous speed of the circular comb, it is possible to work with higher Kammspielzahlen. With the accelerations and delays generated in this case, additional stresses are incurred on the drive unit. In addition, it can lead to undesirable vibrations of the device in unfavorable cases, which in turn can reduce the service life.
In order to increase the Auskämmwirkung Kämmsegmente have been proposed, which extend over a circumferential angle of 130 ° and more, such as. B. from the published EP 1 383 948 B1 can be seen. This increase also increases the mass of the basic body on which the Kämmgarnituren are attached. From the GB 205,128 an embodiment of a circular comb is known, wherein the base body which carries the combing, is integrally formed and is supported at its two ends directly on the circular comb shaft. By means of screws, which protrude through a flange of a counterweight, the base body is clamped on the circular comb shaft.
The counterweight is provided here with a saddle-shaped approach, over which it is pushed onto a circular comb shaft and clamped by screws with the circular comb shaft. The saddle-shaped projection is located between the two support ends of the base body, whereby the center region of the base body is without support. In the combing position, the distance between the tips of the combing set and the lower tong plate is to be kept very small in order to be combed out of the closed position Tongs outstanding tuft almost completely grasp. That is, in order to ensure the dimensional accuracy of the body in this central area and thus to keep the Kämmverhältnisse over the entire width of the Kämmgarnitur constant, the body is in the execution of the GB 205,128 to train relatively massively. This in turn has the consequence that the moment of inertia becomes very large, which has a negative effect on the energy to be applied and the bearings, especially when working with high Kammspielzahlen and discontinuous speeds, as is the case today. At the time of publication (1923) of GB 205,128 were the Kammspielzahlen still many times smaller, so the moment of inertia in this area did not play such a big role.

The invention is therefore based on the object to propose a round comb, which improves known solutions and has a low moment of inertia than known solutions even at high speeds. At the same time a constant stability of the circular comb should be ensured over its entire width.
The solution to this problem is by proposing that the base body consists of a hollow profile, which has an outer circular arc-shaped portion for receiving the Kämmgarnitur and having an opposite inner portion, with an open towards the shaft, semicircular trough, which extending in the longitudinal direction of the hollow profile and over which the base body is supported on the shaft and fastening means are provided, with which the base body and the mass balance element are braced against each other transversely to the longitudinal direction of the shaft.
With this design of the body is possible that the thickness of the profile, in particular - in relation to the axis of rotation of the circular comb shaft - in the outer region, which carries the combing set, can be kept small, especially as the profile over its entire length on the circular comb shaft supported. Thus, the mass and thus the mass moment of inertia can be kept low in this area. As a result, it is possible to increase the circumferential angle of the combing set on the circular comb compared with known solutions, without it being a substantial Increasing the moment of inertia over the known solutions comes.
Furthermore, it is proposed that the mass balance element has a convex portion pointing in the direction of the shaft, via which it rests on a partial circumferential surface of the shaft. Thus, a compact design is achieved, the profile of the base element and the mass balance element can surround the circular comb shaft all around and can be joined together to form a closed unit around the circular comb shaft.
Advantageously, it is further proposed that the hollow profile of the base body is provided with extending in its longitudinal direction and within the hollow profile webs, which divide the hollow profile into triangular cavities. Thus, the wall thickness of the hollow profile can be kept low, since the transmission of forces on the triangular cavities can be optimally transmitted (due to the statics and the honeycomb arrangement) to the support on the circular comb shaft. By the further proposal that the shaft is provided with a plurality of transverse openings extending transversely to the longitudinal axis of the shaft, through which the fastening means protrude, it is ensured that the moment of inertia is only insignificantly increased by the attachment of the fastening means, since they project through the axis of rotation of the shaft ,

Preferably, the fastening means are screws which protrude into threaded bores of the hollow profile. This allows a simple and secure attachment of the hollow profile and the counterweight on the circular comb shaft. The introduction of force by the screws takes place here directly in the region of the clamping surfaces with which the hollow profile and the counterweight rest on the circular comb shaft.
In order to keep the inertia at a low level, the hollow profile of the base body is made of a material with a low specific weight. The hollow profile of the body can, for. B. be made of an aluminum extruded profile.
However, if threaded holes are provided in this part for direct attachment of fasteners (eg, screws), it may happen that it deforms in the threaded holes when large tensile forces absorbed therein Need to become. To exclude this is further proposed that within the hollow section in the region of the inner portion at least one additional means is mounted, which is provided with threaded holes for receiving the fastening means, wherein the additional means has a higher strength than the hollow profile.
To fix the angular position of the base body and the mass balance element on the circular comb shaft is further proposed that the fasteners are screws and at least one of the screws is a dowel whose screw shaft protrude through mating holes of the mass balance element, the shaft and the body, said at the end of the dowel mounted threaded pin is received in the threaded hole of the additional agent.

In order not to produce uncontrolled air currents through the outer contour of the circular comb and to protect the circular comb itself against contamination (such as fiber fly) is further proposed that the outer surfaces of the hollow profile and the mass balance element form a closed peripheral surface.

In order to comply with an exact positioning of the combing segment and the compensating element relative to a pivotable nipper unit, it is proposed that the mass balance element and the shaft are provided with grooves through which the mass balance element and the shaft using springs in a fixed position in the circumferential direction of the shaft is positioned. The angular position of the circular comb shaft and the position of the drive shaft of the nipper unit can hereby be exactly matched to each other.
To keep clean the interior of the hollow profile is proposed that at both ends of the hollow profile for closing the cavity covers are attached.
So that the hollow profile of the main body (eg for replacement) can be removed from the circular comb shaft independently of the mass balancing element, it is proposed that the mass balancing element is connected to the shaft via additional fastening means. That is, after loosening the fasteners, which the mass balance element and the body against the circular comb shaft tense, the body can be removed from the circular comb shaft, while the mass balance element is still held on the round comb shaft via the additional fastening means. This facilitates assembly and disassembly.

Fig.1

eine schematische Teil-Seitenansicht eines Kämmkopfes einer Kämmmaschine

Fig.2

eine schematische Seitenansicht eines erfindungsgemäss ausgebildeten Rundkammes.

Fig.3

eine Seitenansicht X nach Fig.2

Fig.4

ein weiteres Ausführungsbeispiel nach Fig.2

Fig.4a

ein weiteres Ausführungsbeispiel nach Fig.4

Fig.5

ein weiteres Ausführungsbeispiel (Teilansicht) nach Fig.4, bzw. Fig.4a

Fig.5a

eine vergrösserte Teilansicht nach Fig.5

To reduce the moment of inertia is further proposed that - seen in the direction of rotation of the circular comb - the thickness of the outer portion of the body is formed stepwise decreasing.
Preferably, this is achieved by suggesting that the peripheral surface (U) of the outer portion (23) of the main body (20) carrying the combing (G) has at least one shoulder (A1) on the combing paragraph (Z1). The height of the heel is adapted to the different tooth depths between the successive clothing sections. Any reduction in mass, in particular in the outer region of the rotating at high speed circular comb, has a significant effect on a reduction of the mass moment of inertia. This is particularly advantageous when the circular comb is driven at a discontinuous speed and thus its drive is exposed to accelerations and decelerations.
Further advantages of the invention will be shown and described in more detail in subsequent embodiments.
Show it:

Fig.1

a schematic partial side view of a combing head of a combing machine

Fig.2

a schematic side view of an inventively designed circular comb.

Figure 3

a side view X after Fig.2

Figure 4

a further embodiment according to Fig.2

4a

a further embodiment according to Figure 4

Figure 5

a further embodiment (partial view) after Figure 4 , respectively. 4a

5a

an enlarged partial view Figure 5

FIG. 1 shows a schematic side view of a combing K of a combing machine. In known combers z. B. eight such Kämmköpfe K next to each other arranged. The Kämmkopf K, of which only a part of the elements is shown, has a nipper unit 1, which is about the pivot arms 9, 12 about the axes 10, 15 pivoted back and forth within the scope of the combing machine. The axis 10, which is also called pliers shaft, is driven by a drive, not shown in detail, to give the nipper unit 1 a reciprocating motion. The axis 15 corresponds to the circular comb shaft on which a circular comb R is fixed in rotation. The circular comb shaft 15 with its central axis A is also driven by a drive, not shown, continuously or discontinuously. The attached below the nipper unit 1 on the circular comb shaft 15 round ridge R consists in the known solution shown two spaced apart fixed on the circular comb shaft 15 scars N1, N2, on the outer periphery on the one hand a base body 18 and on the other hand a mass balance AG is attached. The attachment of the mass balance element (short compensation element called) takes place as shown schematically on the screws S, via which it is attached to the hubs N1, N2. The main body 18 is also firmly connected via schematically illustrated screws S1 with the scars N1, N2. Above the main body 18, which extends as the compensation element AG over the entire width B of the circular comb R, a set G is attached. The angle A of the combing G marked with an angle a in known combing machines is approximately 90 degrees and is also referred to as a "combing angle".

The nipper unit is formed from a nipper frame 5, to which a lower nipper plate 6 is attached. On the nipper frame 5, an upper nipper plate 2 is pivotally mounted about a pivot axis 4 and pivot arms 3. In the illustrated embodiment, the nipper unit 1 is closed, wherein the outstanding from the nip of the nipper unit fiber tuft FB is detected by the clothing G and combed out. The loading arms (eg springs), which are not shown, engage on the pivoting arms 3, which on the one hand control the pivoting movement of the upper tong plate 2 and on the other hand generate a necessary clamping force in the nip unit of the nipper unit 1. Also in the clamp frame 5, a feed roller 16 is rotatably mounted above the lower tong plate 6, which z. B. is driven in steps by a not shown latch drive. About this feed roller 16 is supplied to the nipper unit 1 cotton wool W (or individual slivers) of the nip of the nipper unit supplied. After combing out of the fiber tuft FB, the nipper unit 11 is pivoted in the direction of a subsequent Abreisswalzenpaare AW. During this pivoting operation, the nipper unit opens and the combed end of the wadding W or the tuft FB is placed on the end of a previously formed fiber fleece V V and soldered under the action of the nip of Abreisswalzen AW with this and transported away in the conveying direction F.

FIG. 2 shows an embodiment of an inventively designed circular comb R, wherein the base body 20 shown here is formed as a hollow profile, which is supported on a semi-circular trough 21 on a partial circumference of the circular comb shaft 15. The trough 21 is located on an inner portion 22 of the base body 20, on which an outer portion 23 is supported via the ribs R1 to R4. Between the ribs R1 to R4 and the inner and outer portions 22, 23, cavities H1 to H3 are formed. Such as B. from the FIG. 3 can be seen, is the trough 21 over the entire width B of the circular ridge R on the peripheral surface of the circular comb shaft 15. The sections 22, 23 and the ribs R1 to R4 extend across the width B of the circular ridge R. In order to additionally reduce the mass of the base body 20, it would be conceivable the ribs R1 to R4 with over the width B of the circular ridge R distributed openings , or openings to provide. This might require an additional level of manufacturing.

The illustrated embodiment of the base body 20 as a hollow profile, in particular the thickness d of the outer portion 23 of the base body 20 can be made low, without the required stability and strength of the body is substantially reduced. Thereby, the main body 20 in the area (outer portion 22) farthest from the rotation axis A of the circular comb shaft 15 can be formed with a relatively small mass. This also significantly reduces the moment of inertia. As a result, the meshing angle α1 can be increased compared to known solutions (α), without resulting in an excessive moment of inertia with respect to known solutions. Ie. it would be z. B. possible to increase the angle α1 to 130 ° and more without causing an increase in the mass moment of inertia, which in the FIG. 1 shown embodiment with a Kämmwinkel α in the amount of 90 ° is present. On the outer peripheral surface U of the outer portion 23 of the base body 20, a K G is attached.

In the present example, the base body 20 is formed in the region of the inner portion 22 V-shaped. Ie. the webs 22a and 22b extending outwardly from the trough 21 form a V-shaped receptacle for the mass compensation element (also referred to as a compensation element) AG1 which is likewise located on a partial circumference and along the width B on the shaft 15. Between the outer contour of the compensating element AG1 and the webs 22a, 22b, a small distance AB is provided. This ensures that the base body 20 in the region of the trough 21 and the compensating element AG1 in the region of its trough-shaped, convex portion 25 completely come to rest on the outer circumference of the circular comb shaft 15. The outer contour K of the compensation element AG1 adjoins the outer contour of the ribs R1, R4 of the main body 20, whereby a closed peripheral surface of the circular ridge R (without paragraphs) is formed. This ensures that the unwanted air circulation can not occur due to the external shape of the circular ridge R. In addition, a setting of impurities (fiber flakes) in the peripheral region of the circular ridge is largely prevented.

For attachment of the base body 20 and the compensation element AG1 on the circular comb shaft 15 (called shaft for short), the shaft is provided with several through the width B of the circular ridge R seen through holes 27 through which screws S3 protrude. The head of the respective screw S3 is located in a recess 26 of the compensation element AG1. Furthermore, a through hole 28 is provided in the compensation element AG1, which is aligned with the bore 27 of the shaft 15. The end of the respective screw S3 has a thread 30, which projects into a threaded bore 31, which is provided in the region of the trough 21 of the main body 20. By tightening the screws S3 and screwing into the threaded hole 31, the base body 20 and the compensation element AG1 are pressed against each other and clamped on the shaft 15 via the trough 21 and the trough-shaped portion 25 on the shaft 15 firmly.

As shown schematically in dashed lines in FIG FIG. 3 is shown, the compensating element AG1 may be provided with a longitudinal groove which forms a tongue and groove joint 33 using a spring with an opposite longitudinal groove in the shaft 15, via which the angular position of the compensating element AG1 and thus also of the main body 20 can be maintained exactly , This can ensure that a predetermined angular position of the combing segment G can be exactly defined for the corresponding position of the nipper unit 1.

Like also out FIG. 3 can be seen, several such screw with the screws S3 over the width B of the circular ridge R are arranged. This ensures that the base body 20 and also the balance weight AG1 rests uniformly and over the entire width B of the circular ridge R on the shaft 15, or is supported.

As schematic FIG. 3 can be seen, the compensation element AG1 is provided with further through holes 34 and recesses 35 through which screws S2 protrude. The ends of the respective screws are provided with a thread, which opens into a threaded bore 36 which is provided in the shaft 15. This threaded bore 36 is not continuous and extends only over part of the diameter of the shaft 15. These additional screw with the screws S2 allow the independent fixing of the balancing weight AG1 on the shaft 15. D. h., The base body 20 with the attached thereto Kämmgarnitur G can be completely removed by loosening the screws S3 of the shaft 15, while the balance weight AG1 are still attached to the shaft 15 via the screw S2. This allows a simple and quick replacement of the main body 20 with the Kämmgarnitur G without the compensating element AG1 must also be dismantled.

On the end sides of the base body 20 is in each case a cover 38, 39 fixed via schematically indicated screw 40, in particular to foreclose the cavities H1 to H3 of the main body 20 to the outside. These covers 38, 39 can be made of lightweight material (plastic), since these only have the task of preventing the ingress of soiling (eg fiber fly) into the cavity of the main body 20.

In the further embodiment according to FIG. 4 is a modified version after FIG. 2 shown. Here, the base body 20 with respect to the embodiment of FIG. 2 additional ribs R5, R6, through which triangular cavities H1, H2, H3, H5 and H6 are formed to increase the stability. In the region of the trough 21, the main body 20 is provided with a through-bore 42, through which the screw S3 protrudes. The end of the respective screw S3 is provided with a thread 30 which projects into a threaded bore 45 which is mounted in an insert 46. The insert 46 is held in a recess 44 in its position relative to the base body 20. The insert 46 has a higher strength (specific gravity) than the main body 20, whereby a deformation of the thread 45 is avoided by the tensile force of the screws S3. The risk of deformation can z. B. occur when the thread 30 is mounted directly in the base body 20, which may be made of a specific lighter active ingredient.

Fig. 4a shows a further embodiment, which substantially the embodiment of the Figure 4 equivalent. It differs only by the use of a fitting screw S3a, via which the angular position of the base body 20 and the balance weight AG1 on the circular comb shaft 15 can be exactly fixed. By using the fitting screw S3a eliminates the fixation by a tongue and groove joint 33, as in Figure 3 was indicated and described. That means one who lives in Figure 3 shown screws S3 is replaced by a fitting screw S3a. The remaining screws S3 ( Figure 3 ), as in Figure 4 shown by through holes 28, 27 and 42 protrude, whose diameter is slightly larger than the diameter of the protruding screw shank.

In the area of the fitting screw S3a, the balance weight AG1 has a fitting bore 48, the circular comb shaft has a fitting bore 49, and the base body 20 has a fitting bore 50 in which the bolt shank 52 is received and forms a play-free fit therewith.
The screw head 51 of the fitting screw S3a is located in a recess 26 of the balance weight AG1. The end of the fitting screw S3a is provided with a threaded pin 53, which (as in the example of Figure 4 shown) in a threaded bore 45 of an insert 46 projects.
The further embodiment of the Fig.5 (Fig.5a ) shows an embodiment of a circular ridge R, the base body 20 is provided in the region of the peripheral surface U of its outer portion 23 with a shoulder A1 with a height h. According to this, the combing set G fastened on this circumferential surface U (which as a rule consists of a plurality of parallel clothing strips) is likewise provided with a shoulder Z1, which corresponds in its dimension to the shoulder A1 and faces the latter. The range of paragraphs A1 / Z1 is particularly from the enlarged partial view in 5a shown and shown in more detail.
The first section G1 of the Kämmgarnitur G has a coarser teeth with a greater tooth depth t1, compared to a finer toothing of a second section G2 with a smaller tooth depth t2. How out 5a to subtract the section G1, to which the second section G2 connects, in the region of the paragraph A1.
The thickness d2 of the subsection 23b ( Figure 5 ) of the outer portion 23 of the base body 20 corresponds approximately to the thickness d, in the 4 and 4a However, the thickness d1 of the portion 23a in the region of the first portion G1 of the Kämmgarnitur G is less than the thickness d2 of the portion 23b in the region of the second portion G2 of the Kämmgarnitur G.
Thus, a reduction of the mass can be achieved in the portion 23a of the outer portion 23 of the base body, whereby the mass moment of inertia of the circular comb is reduced overall. This in turn allows a further increase in speed without exceeding critical ranges.
With the in Figure 5 The solution shown achieves an optimized design of the main body as a function of the existing tooth depths of the trimmings. It would also be conceivable depending on the design of the clothing to provide more than one step (paragraph) on the outer peripheral surface U of the body.
Of course, further embodiments are possible within the scope of the invention.

Claims (14)

Round comb (R) for a combing machine with a base body (18, 20) which is rotatably mounted on a shaft (15) and on its outer circumference wearing a Kämmgarnitur (G), wherein - seen in the radial direction of the shaft - on, the Kämmgarnitur (G) opposite side of the shaft (15) a mass balance element (AG, AG1) is fixed, characterized in that the base body (20) consists of a hollow profile, which has an outer circular arc-shaped portion (23) for receiving the Kämmgarnitur (G ) and with an inner portion (22) opposite this, with a semi-circular depression (21) open in the direction of the shaft, which extends in the longitudinal direction of the hollow profile and over which the base body (20) rests on the shaft, and fastening means ( S3) are provided, with which the base body (20) and the mass balance element (AG1) against each other transversely to the longitudinal direction of the shaft (15) are clamped. Round comb (R) according to claim 1, characterized in that the mass balance element (AG1) has a in the direction of the shaft (15) facing convex portion (25) via which it rests on a partial peripheral surface of the shaft (15) Round comb (R) according to any one of claims 1 or 2, characterized in that the hollow profile of the base body (20) in its longitudinal direction and within the hollow profile extending webs (R2, R3, R5, R6) is provided which the hollow profile in triangular (H1, H2, H3, H5, H6) divide cavities. Round comb (R) according to one of claims 1 to 3, characterized in that the shaft (15) is provided with a plurality of transverse openings (28) extending transversely to the longitudinal axis of the shaft (15), through which the fastening means (S3) project. Round comb (R) according to claim 4, characterized in that the fastening means are screws (S3) which project into threaded bores (31) of the hollow profile (20). Round comb (R) according to claim 4, characterized in that within the hollow profile (20) in the region of the inner portion (22) at least one additional means (46) is mounted, which with threaded holes (45) for receiving the fastening means (S3, S3a ), wherein the additional means (46) has a higher strength than the hollow profile (20). Round comb (R) according to claim 6, characterized in that the fastening means are screws (S3, S3a) and at least one of the screws (S3a) is a dowel screw (S3a) whose screw shank (52) passes through mating holes (49, 49, 50). the mass balance element (AG1), the shaft (15) and the base body (20) protrude, wherein the threaded pin attached to the end of the dowel is received in the threaded bore (45) of the additional means (46). Round comb (R) according to one of claims 1 to 3, characterized in that the outer surfaces of the hollow profile (20) and the mass balance element (AG1) form a closed peripheral surface. Circular comb according to one of the preceding claims, characterized in that the hollow profile of the base body (20) is an extruded aluminum profile. Circular comb according to claim 2, characterized in that the mass balance element (AG1) and the shaft (15) are provided with grooves (33) over which the mass balance element and the shaft using springs (33) in a fixed position in the circumferential direction of the shaft ( 15) is positioned. Circular comb according to claim 8, characterized in that at both ends of the hollow profile (20) for closing the cavity (H1-H5) covers (38, 39) are attached. Round comb according to claim 4, characterized in that the mass balance element (AG1) is connected via additional fastening means (S2) with the shaft (15). Round comb according to one of claims 1 to 12, characterized in that - seen in the direction of rotation (L) of the circular comb (R) - the thickness (d1, d2) of the outer portion (23) of the base body (20) step-shaped (A1) decreasing is. Round comb according to claim 13, characterized in that the peripheral surface (U) of the outer portion (23) of the base body (20), which carries the combing (G), at least one shoulder (A1), which, provided on the combing paragraph paragraph (Z1) faces.

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