EP3514273A1 - Drive device for a combing machine - Google Patents

Abstract

The present invention relates to a drive device for a comber, with a gear (51) driven via a main motor (128A), the gear (51) having a tear-off roller drive train for the pilgrim movement of tear rollers (34), a round-comb drive train for driving a non-uniform one Round comb (16), and a tong drive train for the reciprocating movement of a tong unit (10), and wherein there is an operative connection between the main motor (128a) and the drive trains (70, 92, 100). According to the invention, the tear-off roller drive train has a tear-off roller auxiliary shaft (70) on which a first drive gearwheel (130) sits in a rotationally fixed manner; , and the pliers drive train has a pliers auxiliary shaft (100) on which a third drive gear (134) sits in a rotationally fixed manner, so that the operative connection between the main motor (128a) and the first drive gear (130) and between the second drive gear ( 132) and the first drive gear (130) and between the third drive gear (134) and the second drive gear (132) is provided, a device for separating the operative connection between the second drive gear (132) and the first drive gear (130) by a Displacement of the second drive gear (132) or the round comb auxiliary shaft (92) in the direction of a longitudinal axis of the round comb auxiliary shaft (92) is provided.

Description

The present invention relates to a comber driving apparatus having a main engine driven transmission, the transmission comprising a stripping roller drive train for pilgrim movement of stripping rollers, a circular comb drive train for nonuniformly driving a circular comb, and a plier drive train for reciprocation a nipper assembly, and wherein there is an operative connection between the main motor and the drive trains.

In a combing machine with a large number of combing points, each nipper unit, which has a lower nipper plate and an upper nipper rotatably mounted thereon, is presented by a lap roll with a sliver arranged around the nipper unit for combing out a sliver. During a Kämmspiels the nipper unit moves from a rearward open position to a front closed position, during this reciprocation of the nipper unit opens and closes the upper nipper, wherein in the closed state of the nipper unit, the lower nipper plate with the upper nipper forms a clamping point while presenting a hanging tuft to a combing segment of the circular comb. After combing with the circular comb, the nipper unit opens, in which the upper nipper lifts off from the lower nipper plate and the combed tuft is fed via a rotatably mounted in the nipper unit feed cylinder a downstream Abreisswalzenpaar for soldering the combed fiber slivers. The combed slivers formed at the individual combing points are then transferred on a conveyor table side by side to a subsequent drafting system in which they are stretched and then combined to form a common combing machine belt. The sliver produced at the drafting system is then placed on a funnel wheel in a pot.

The soldering process on the tear-off rollers depends on the position of the nipper unit and the position of the tear-off rollers. During the soldering operation, the tear-off roller moves first in the direction of the nipper unit and then in the opposite direction Direction to solder an already combed out and trapped by the Abreisswalzen fiber end with a combed out of the circular comb fiber end. The distance, which is not roof tile-like laid and soldered, is referred to as soldering distance and can be defined by the movement of the Abreisswalzen.

The soldering of the fiber packages to the desired nonwoven fabric in particular has the requirement that the tile-like stacked fiber packages have a uniform result. This uniformity of the sliver is determined in practice by the capacitive measurement on the belt, wherein the stratification of the individual fiber packets is measured. A disadvantage for the yarn quality is the folding of the fiber tips by adjusting a control disc on a known combing machine. However, this has the consequence that metrologically deep inequalities (CV value) are measured in the band, but with this result, a yarn quality is present, which is not recommended for further processing.

Another requirement for the nonwoven fabric is the mass distribution in the nonwoven fabric and the cut. Care should be taken when brazing the fiber bundles to ensure that there are small mass variations in the nonwoven fabric, as this would significantly affect the uniformity.

The object of the present invention is therefore to provide a drive device for Abreissalzen a combing machine, which makes it possible to optimize the uniformity of the sliver with respect to the soldering process, so that the yarn quality is maintained for a wide selection of fiber masses submitted.

The object is achieved by a drive device for tear-off rollers of a comber having the features of independent patent claim 1.

The proposal is for a combing machine drive apparatus having a main engine driven transmission, the transmission comprising a rider roll drive train for rider roll movement of ripping rolls, a ridge drive train for nonuniformly driving a ridge, and a pincers drive train for reciprocating a nipper assembly has, and wherein there is an operative connection between the main engine and the drive trains.

According to the invention, the pull-off roller drive train has a pull-off roller auxiliary shaft on which a first drive gear rotatably rests, the circular comb drive train has a round-comb auxiliary shaft on which a second drive gear sits non-rotatably, and the pincer drive train has a pincer auxiliary shaft on which a third drive gear is non-rotatably seated, so that the operative connection between the main motor and the first drive gear and between the second drive gear and the first drive gear and between the third drive gear and the second drive gear is provided, wherein a device for separating the operative connection between the second drive gear and the first drive gear is provided by a displacement of the second drive gear or the circular comb auxiliary shaft in the direction of a longitudinal axis of the circular comb auxiliary shaft.

The separation of the operative connection has the advantage that the Abreisswalzen drive shaft relative to the circular comb drive shaft and the forceps drive shaft can be decoupled to make a phase shift of the Abreisswalzen movement. This means that the rip-off roller movement either sooner or later is presented to the combed fiber tuft for brazing. In this way, it is possible to adjust each type of fiber length provided with respect to the uniformity of the nonwoven fabric with the separator. Also, mass fluctuations in the nonwoven fabric are optimally adjustable and the proportion of folded fiber tips during the soldering process is reduced.

Preferably, a rotation of the Abreisswalzen auxiliary shaft relative to the circular comb auxiliary shaft is provided by the main motor after separation of the operative connection between the second drive gear and the first drive gear.

Particularly preferably, the rotation of the Abreisswalzen auxiliary shaft is provided in steps of 0.9 ° to 4.5 °.

More preferably, the second drive gear and the third drive gear are formed such that the displacement of the second drive gear or the circular comb auxiliary shaft causes no release of the operative connection between the third drive gear and the second drive gear.

Preferably, the device for displacement of the second drive gear or the circular comb auxiliary shaft on a hydraulic, electrical or mechanical drive.

Particularly preferred as a hydraulic drive, a hydraulic cylinder is provided which is connected to the circular comb auxiliary shaft or the second drive gear.

More preferably, a first rotation angle sensor on the Abreisswalzen auxiliary shaft and a second rotation angle sensor on the forceps auxiliary shaft are provided. The rotation angle sensors are designed to monitor the rotational angular position of the respective drive shaft or auxiliary shaft.

Particularly preferably, a control unit is provided which is connected to the main motor and the device for shifting the second drive gear or the circular comb auxiliary shaft and the rotation angle sensors. The control unit monitors the rotational angular position of the respective drive shaft and allows the control of the displacement of the second drive gear and the rotation of the Abreisswalzen auxiliary shaft.

More preferably, the rotation of the Abreisswalzen auxiliary shaft is provided by a predetermined value by the control unit in conjunction with the main motor, wherein via the control unit, a comparison of the first rotation angle sensor is provided with the second rotation angle sensor.

Particularly preferably, the control unit has reference data for the second rotation angle sensor and / or for rotation in a memory. The stored reference data associated with the second rotation angle sensor may be compared via the control unit with currently measured data from the first rotation angle sensor to determine the exact position of rotation of the detachment roller auxiliary shaft.

Furthermore, the invention relates to a combing machine with a drive device for a transmission.

Moreover, the invention relates to a method for adjusting a comber having a drive device with a driven via a frequency-controlled main motor transmission with a Abreisswalzen drive train for pilgrim movement of a Abreisswalze with a first drive gear on a Abreisswalzen auxiliary shaft, with a circular comb drive train for non-uniform driving a circular comb a second drive gear on a circular comb auxiliary shaft and a tong drive train for reciprocating a nipper assembly with a third drive gear on a pliers auxiliary shaft, wherein an operative connection between the main motor and the drive wheels, whereby the first drive gear through the main motor and the second drive gear is driven by the first drive gear and the third drive gear is driven by the second drive gear.

• Stillsetzen der Antriebsvorrichtung,
• Verschiebung des zweiten Antriebszahnrades auf der Rundkamm-Hilfswelle oder der Rundkamm-Hilfswelle in Richtung einer Längsachse der Rundkamm-Hilfswelle zur Trennung der Wirkverbindung zwischen dem ersten Antriebszahnrad und dem zweiten Antriebszahnrad,
• Verdrehen der Abtreisswalzen-Hilfswelle gegenüber der Rundkamm-Hilfswelle und der Zangen-Hilfswelle mit dem Hauptmotor,
• Verschiebung des zweiten Antriebszahnrades auf der Rundkamm-Hilfswelle oder der Rundkamm-Hilfswelle in Richtung einer Längsachse der Rundkamm-Hilfswelle zur Wiederherstellung der Wirkverbindung zwischen dem ersten Antriebszahnrad und dem zweiten Antriebszahnrad.

According to the invention, the following method steps are provided:

• Stopping the drive device,
• Displacement of the second drive gear on the circular comb auxiliary shaft or the circular comb auxiliary shaft in the direction of a longitudinal axis of the circular comb auxiliary shaft for separating the operative connection between the first drive gear and the second drive gear,
• Twisting the stripping roller auxiliary shaft against the circular comb auxiliary shaft and the pliers auxiliary shaft with the main motor,
• Displacement of the second drive gear on the circular comb auxiliary shaft or the circular comb auxiliary shaft in the direction of a longitudinal axis of the circular comb auxiliary shaft for restoring the operative connection between the first drive gear and the second drive gear.

Preferably, in the displacement of the second drive gear on the circular comb auxiliary shaft or the circular comb auxiliary shaft in the direction of a longitudinal axis of the circular comb auxiliary shaft, the operative connection between the second drive gear and the third drive gear is not separated.

Further advantages of the invention will be apparent from an embodiment described below and shown.

Fig. 1

einen Querschnitt durch eine Kämmmaschine;

Fig. 2

eine Kombination von drei Getriebe-Modulen mit einem gemeinsamen Antriebsmotor;

Fig. 3

eine schematische Darstellung einer Abreisswalzen-Kurvenscheiben-Vorrichtung;

Fig. 4

eine graphische Darstellung einer Abreisswalzen-Bewegung;

Fig. 5

eine schematische Darstellung einer Zangen-Kurvenscheiben-Vorrichtung;

Fig. 6

eine graphische Darstellung einer Zangen-Bewegung;

Fig. 7

eine graphische Darstellung der Abreisswalzen-Bewegung gemäss Fig. 4 und der Zangen-Bewegung gemäss Fig. 6 sowie phasenverschobene Abreisswalzen-Bewegungen;

Fig. 8

eine schematische Veranschaulichung der Enden eines Faservlieses an den Abreisswalzen in Abhängigkeit der phasenverschobenen Abreisswalzen-Bewegung;

Fig. 9

eine erfindungsgemässe Trennvorrichtung zur Phasenverschiebung der Abreisswalzen-Bewegung;

Fig. 10

eine Einstellvorrichtung zur manuellen Verdrehung einer Abreisswalzen-Kurvenscheibe gegenüber einer Abreisswalzen-Hilfswelle mittels einer Hülse;

Fig. 11

eine vergrösserte Darstellung der Einstellvorrichtung gemäss Fig. 10;

Fig. 12

eine vergrösserte Darstellung einer alternativen Ausführung einer Eistellvorrichtung.

Show it:

Fig. 1

a cross section through a comber;

Fig. 2

a combination of three transmission modules with a common drive motor;

Fig. 3

a schematic representation of a Abreisswalzen cam plate device;

Fig. 4

a graphical representation of a Abreisswalzen movement;

Fig. 5

a schematic representation of a forceps cam device;

Fig. 6

a graphical representation of a forceps movement;

Fig. 7

a graphic representation of the Abreisswalzen movement according to Fig. 4 and the forceps movement according to Fig. 6 as well as phase-shifted pull-off roller movements;

Fig. 8

a schematic illustration of the ends of a nonwoven fabric on the Abreisswalzen in dependence on the phase-out Abreisswalzen movement;

Fig. 9

an inventive separation device for phase shift of the Abreisswalzen movement;

Fig. 10

an adjustment device for the manual rotation of a Abreisswalzen cam against a Abreisswalzen auxiliary shaft by means of a sleeve;

Fig. 11

an enlarged view of the adjustment according to Fig. 10 ;

Fig. 12

an enlarged view of an alternative embodiment of an Eistellvorrichtung.

Fig. 1 schematically shows a cross section of a Kämmstelle 2 of a combing machine 4. In practice, eight such Kämmstellen 2 are arranged side by side. Each Kämmstelle 2 consists of a nipper unit 10 (in short: pliers called), which performs a reciprocating motion of the forceps 10 via front wings 12 and rear wings 14. The front wings 12 (only one shown) are rotatable on a circular comb shaft 16 and mounted on a front tongs axis 18 of the forceps 10. The rear swing arm 14, which is rotatably mounted on a rear tong axis 20 of the forceps 10, is rotatably connected to a driven forceps shaft 22. A feed cylinder 24, which is rotatably mounted within the forceps 10, a cotton wool 26 is supplied. The cotton wool 26 is unwound from a cotton roll, not shown, which rests on winding rollers, also not shown for the rolling process.

In the in Fig. 1 shown position, the pliers 10 is opened, ie a plier 11 is pivotally mounted relative to a lower jaw 13 via a Oberzangenwelle 27 and thus lifted from the lower jaw 13 and the forceps 10 is in a forward position, in which the out of the forceps 10 Faserbart 28 is attached to a fiber end 30 of an already formed nonwoven fabric 32 and soldered thereto. The fiber fleece 32 is held by a pair of Abreisswalzen 34, which perform a rotational movement indicated by the arrows for the soldering and tearing off and thus the nonwoven fabric 32, and the fiber end 30 moves in the transport direction T.

In a rear, not shown, end position of the forceps 10, this is closed, wherein the tuft 10 projecting from the tongs 10 is combed out by a combing segment 36, or by a combing set of a rotatably mounted circular comb 38. The combing segment 36 is in an upper position during the combing process. The combing segment 36 is usually provided with Garniturzähnen which engage during the combing process in the tuft 28.

The circular comb 38, which is rotatably supported by the circular comb shaft 16 in the machine frame, is located within a substantially closed suction duct 40, which opens into a channel 42. The channel 42 is, as shown schematically, in communication with a vacuum source 44, by means of which the separated material is fed to a collection point, not shown.

The separated material is short fibers, shell parts, and other contaminants, which are combed out of the tuft 28 by the combing segment 36 during the combing process. Part of the dissected good is going through transferred the applied negative pressure via the vacuum source 44 and the resulting air flow directly to the channel 42. The rest of the part, in particular the combed fibers remains in the combing segment 36, or settles between the Garniturzähnen and is by the rotational movement of the circular comb 38 down in the in Fig. 1 transported position shown. In this case, the combing segment 36 passes into the area of action of a brush 48 likewise rotatably mounted in the suction duct 40 via a brush shaft 46, which brush is provided with distributed bristles 50 on its circumference.

In Fig. 2 is a combination 51 of a first gear 52 for generating a pilgrim movement for the Abreisswalzen 34 (see Fig. 1 ), a second gear 54 for non-uniform driving of the circular comb 38 (see Fig. 1 ) and a third gear 56 for reciprocating the pliers 10 (see Fig. 1 ) intended. The three gear 52, 54, 56 are provided in a modular design, wherein the combination 51 of the three gear modules 52, 54, 56 is enclosed by a housing 60.

The first transmission module 52 has a first drive train 62 with a first drive shaft 64, which transmits via a differential gear 66 a continuous rotational movement to a ring gear 74. The transmission module 52 also includes a second driveline 68 having a breakaway roll auxiliary shaft 70 on which is disposed a pull roll cam means 72 for producing a forward and backward movement.

The differential gear 66 is formed as a planetary gear, wherein the first drive train 62 drives a sun gear 78 via a ring gear 74 in conjunction with Planentenrädern 76 in order to transmit the continuous rotational movement of the differential gear 66 to the Abreisswalzen 34. Regardless of the forward and backward movement is formed by the Abreisswalzen cam plate device 72, wherein the Abreisswalzen cam plate device 72 has two on the Abreisswalzen auxiliary shaft 70 rotatably arranged Abreisswalzen cams 80 which interact with two Abreisswalzen cam rollers 82nd interact. The two Abreisswalzen cam rollers 82 are a Abreisswalzen rocker arm 84 with a Planententräger 86 of the differential gear 66 connected so that the forward and backward movement of the Abreisswalzen cams 80 is superimposed on the planet carrier 86 with the continuous rotational movement of the ring gear 74 to transmit a pilgrim movement on the Abreisswalzen 34.

The second gear module 54 has a circular comb auxiliary shaft 92 which is connected via a non-circular gear stage 94 of two intermeshing non-circular gears 96a, 96b with the circular comb shaft 16, the non-circular gear stage 94 is a continuous rotational movement of the circular comb auxiliary shaft 92 in a non-uniform rotational movement the circular comb shaft 16 converts.

It should be noted at this point that the diameter of the circular comb shaft according to the prior art is 30 mm and 35 mm. By increasing the combing machine speed, the multiples of the natural frequency are superimposed with the combing machine speed, so that an undesired resonance of the round comb waves is excited. To prevent this it is proposed to minimize the natural frequency by stiffening the ridge corrugation. Therefore, it is ideally proposed to select a circular comb shaft diameter of 35 mm to 45 mm, preferably 40 mm.

The third gear module 56 is designed for the reciprocating movement of the forceps 10 with a forceps cam device 98, wherein in the embodiment according to Fig. 2 the forceps cam device 98 has two forceps cams 102 (only one shown) rotationally fixed on a forceps auxiliary shaft 100 which interact with two forceps cam followers 104 (only one shown). The two pincer rollers 104 are connected to the driven pincer shaft 22 via a pincer rocker arm 106 (see FIG Fig. 1 ), so that the movement profile, in particular the reciprocating movement of the forceps cam 102 on the forceps 10 (see Fig. 1 ) is transmitted.

In the embodiment according to Fig. 2 the combination 51 of transmission modules 52, 54, 56 is driven by a common motor 128. On the Abreisswalzen auxiliary shaft 70 of the second drive train 68 is rotatably seated a Abreisswalzen drive gear 130, on the circular comb auxiliary shaft 92 is rotatably seated a circular comb drive gear 132 and on the pliers auxiliary shaft 100 rotatably seated a pliers drive gear 134, wherein all drive gears 130, 132, 134 have the same size and are engaged with each other. By forming the drive gears 130, 132, 134 with the same dimension, the same speed is transmitted to all transmission modules via the common motor 128. An intermediate gear 136, which is engaged with the Abreisswalzen drive gear 130 is rotatably mounted on a motor auxiliary shaft 138 and the motor auxiliary shaft 138 is guided through the housing 60 to the outside and there is non-rotatably a motor idler gear 140. The engine Intermediate gear 140 is drivingly connected to a motor gear 144 via a timing belt 142, and the motor gear 144 is fixedly mounted on a motor shaft 146 of the common motor 128.

Alternatively, instead of the drive gears 130, 132, 134, a toothed belt drive may be used.

On a shaft (eg 70, 92, 100) with constant combing machine speed, at least one sensor in the form of a speed sensor (incremental with reference or absolute) can be mounted outside the housing 60. According to Fig. 3 is purely schematically the Abreisswalzen cam plate device 72 as already in connection with Fig. 2 discussed. On the Abreisswalzen auxiliary shaft 70 are rotationally fixed two Abreisswalzen cams 80a, 80b. The purely schematically illustrated Abreisswalzen rocker arm 84 has two Abreisswalzen cam rollers 82a, 82b, which are spaced apart at an angle α, wherein the first Abreisswalzen cam 80a with the first Abreisswalzen cam roller 82a and the second Abreisswalzen cam 80b with the second break roll cam 80b cooperates. The second tear roller cam roller 82b prevents the first tear roller cam roller 82a from being lifted off the first tear roller cam 80a. The Abreisswalzen cam rollers 82a, 82b have a diameter of 90 mm and the Abreisswalzen cams 80a, 80b each have a disc width of 15 mm to 30 mm, preferably 20 mm. The storage of Abreisswalzen cams 80 can be done either via roller bearings or plain bearings. When using rolling bearings whose diameter is in the range of 90 mm to 120 mm. When using plain bearings whose diameter is preferably in the range of 60 mm to 90 mm. In particular in small spaces, the use of slide bearings is preferably accessed.

The Abreisswalzen cams 80a, 80b each have a specific outer circumference, on which the respective Abreisswalzen cam roller 82a, 82b rests. By the mechanical connection of the respective cam roller 82a, 82b with the Abreisswalzen auxiliary shaft 70, a back and forth movement 87 of the Abreisswalzen cam 80 is transmitted to the Abreisswalzen 34, as in connection with Fig. 2 executed in detail and in Fig. 4 shown purely schematically.

In Fig. 4 is on the abscissa (horizontal X-axis) a single revolution, ie from 0 ° to 360 °, the Abreisswalzen cam 80 and on the ordinate axis (vertical Y-axis) a cam deflection angle of 0 ° to 35 ° for the Abreisswalzen Cam 80 shown. The solid line is the forward and backward movement profile 87 as related to Fig. 2 and Fig. 3 explained. From 0 ° to about 60 °, a negative course of motion is provided between about 60 ° and 110 °, there is no change in the course of motion, from about 110 ° to about 290 °, a positive course of motion sets in and from 290 ° to 360 ° is again a negative course of motion provided. This Abreißwalzen movement course corresponds to the forward and backward movement 87 for the Abreisswalzen, which by the Abreisswalzen-cam plate device 72 according to Fig. 3 is caused.

According to Fig. 5 is purely schematically the forceps cam device 98 shown. Two pliers cam disks 102a, 102b are non-rotatably mounted on the pliers auxiliary shaft 100.

The purely schematically illustrated pliers rocker arm 106 has two pliers cam rollers 104a, 104b, which are spaced apart at an angle β, wherein the first pliers cam 102a with the first pliers cam 104a and the second pliers cam 102b with the second caliper cam 104b cooperates. The second pincer roller 104b prevents the first pincer roller 104a from being lifted off the first pincer cam 102a. The forceps cam rollers 104a, 104b have a diameter of 90 mm and the forceps cam plates 102a, 102b each have a disc width of 15 mm to 30 mm, preferably 20 mm. The bearing of the pliers cam 102 can be done either via rolling bearings or plain bearings. When using rolling bearings whose diameter is in the range of 90 mm to 120 mm. When using plain bearings whose diameter is preferably in the range of 60 mm to 90 mm. In particular in small spaces, the use of slide bearings is preferably accessed.

The pliers cam disks 102a, 102b each have a specific outer circumference on which the pliers cam rollers 104a, 104b rest. Due to the mechanical connection of the pincer rollers 104a, 104b with the pincer shaft 22, a pincer movement profile 134 of the pincer cams 102 is transmitted to the driven pincer shaft 22, as in connection with FIG Fig. 2 executed in detail and in Fig. 6 shown purely schematically.

In Fig. 6 is on the abscissa axis (horizontal X-axis) a single revolution, ie from 0 ° to 360 °, the pliers cam 102 and on the ordinate axis (vertical Y-axis) a cam deflection angle of 0 ° to 35 ° for the pliers Cam 102 shown. At about 150 ° is like in Fig. 1 described the forceps 10 in the forward position and the upper nipper 11 is seated on the lower nipper 13 and is closed. At 0 ° and at 360 °, the forceps 10 is in the rearward position with a forceps deflection angle of about 31 °.

In Fig. 7 are the forward and backward 87 according to Fig. 4 and the forceps movement 134 according to Fig. 6 superimposed. By a phase shift of the forward and backward movement 87 starting from the state according to Fig. 4 , as in Fig. 7 with a double arrow, the optimum time can be determined when the Abreisswalzen 34, the nonwoven fabric 32 in the direction of the pliers 10 move back (pilgrim step) to the soldering process with the combed tuft 28, as in Fig. 1 described perform. This situation has the advantage that between the individual fiber packages less mass fluctuations and less cutting for the formed fiber fleece 32 occur and during the soldering less enveloped fiber tips before.

In Fig. 8 is enlarged, the pliers 10 and downstream of the Abreisswalzenpaar 34 according Fig. 1 shown, wherein in a known manner the combed fiber tuft 28 is supplied via the feed cylinder 24 to the Abreisswalzenpaar 34 to the soldering operation with the end 30 of the already formed fiber web 32 by the Abreisswalzen movement 87 as in Fig. 2 described and in Fig. 7 schematically illustrated execute. The Abreisswalzenpaar 34 performs the so-called pilgrim step movement for the tearing off and the soldering process in the comber, ie, before a further tearing off the already formed nonwoven fabric 32 is returned by one step in the direction of the pliers 10 to the end 30 of the Abreisswalzenpaar projecting end 30 with the combed fiber end 28 to connect and then the nonwoven fabric 32 is moved forward again by two steps in the conveying direction T. Regarding Fig. 7 can be presented by the phase shift of the Abreisswalzen movement 87 the combed tuft 28 a shorter end (dashed line) of the fiber web or a longer end (dash-dotted line) of the fiber web for the soldering process. Accordingly, the overlap region between the free end of the fiber fleece 30 at the front end of the tear-off rollers 34 and the combed fiber tuft 28 can be optimally adjusted to the respectively presented fiber length, whereby, as already stated above, the fiber packets in the fiber fleece 32 have less mass fluctuations.

A technical implementation of the phase shift of the forward and backward movement 87 takes place either via a separating device as in Fig. 9 described or manual over a sleeve as in Fig. 10 described.

How out Fig. 9 recognizable, in contrast to Fig. 2 , the detachable roller auxiliary shaft 70 of the second drive train 68 is guided through the housing 60 to the outside and has outside the housing 60 at a front end of the Abreisswalzen auxiliary shaft 70, a first rotation angle sensor 148 a. Also, the pliers auxiliary shaft 100 is guided by the housing 60 to the outside and has outside the housing 60 at a front end of the pliers auxiliary shaft 100, a second rotation angle sensor 148b. The common motor 128a is driven by a first frequency converter 129a, and the frequency converter 129a and the two rotation angle sensors 148a, 148b are connected to a control unit 131.

In Fig. 9 It can also be seen that the circular comb drive gear 134 has a step 133 in an end region facing the tear-off roller drive gear 130, so that only a partial region of the front-side outer surface of the tear-away drive gear 130 interacts with the circular-comb drive gear 132, while the circular-comb drive gear 134 Drive gear 132 cooperates with the pliers drive gear 134 over the entire end face outer surface.

In order to rotate the breaker roll cam device 72 with respect to the tong cam device 98, a device disconnects the breaker drive gear 130 and the forceps drive gear 132 by a displacement of the forceps drive gear 132 in the direction of one Longitudinal axis of the circular comb auxiliary shaft 92 is provided. The shift is in Fig. 9 indicated by a double arrow. In the present embodiment, the displacement of the pliers drive gear 132 by means of a hydraulic cylinder 150. The hydraulic cylinder 150 is connected via a directional control valve 154 of two flow paths with a hydraulic pump 152 and a reservoir 156. The control unit 131 controls, via a valve controller 155, the two flow paths of the directional valve 154 for the reservoir 156 and the hydraulic pump 152. The hydraulic pump 152 is connected to a pump drive gear 158, the pump drive gear 158 having a brush drive gear 160 and a motor -Drive gear 162 is operatively connected via a belt 164. A second frequency converter 129b is connected to a second motor 128b and thus drives the hydraulic pump 152 and the brush 48. The second frequency converter 129b and the valve controller 155 are connected to the control unit 131 together with the two rotation angle sensors 148a, 148b and the first frequency converter 129a.

The operation of the present inventive separation of the operative connection between the Abreisswalzen-cam plate device 72 and the forceps cam device 98 is such that the control unit 131, the hydraulic pump 152 and the valve controller 155 is activated, so that the reservoir 156 moves the hydraulic cylinder 150 and this the first non-circular gear 96 a together with the circular comb auxiliary shaft 92, on which the circular comb drive gear 132 rotatably seated, in the direction of the longitudinal axis of the circular comb auxiliary shaft 92 shifts, so that the circular comb drive gear 132 is no longer engaged with the puller roller drive gear 130, but continues to engage with the plier drive gear 134. Thus, the puller cam plate device 72 is decoupled from the second gear module 54 and third gear module 56 and may be rotated. The rotation of the breaker roll cam device 72 is via the first frequency converter 129a in communication with the common motor 128a, in such a manner that the break roll auxiliary shaft 70 is rotated in steps of 0.9 ° to 4.5 °. The first rotation angle sensor 148a is for detecting the rotation angle state of the detachment roller auxiliary shaft 70 and comparing it with the unchanged rotation angle state of the pliers auxiliary shaft 100. Upon rotation of the detachable roller auxiliary shaft 70, the control unit 131 compares the values of the first rotation angle sensor 148a with the unchanged values of the second rotation angle sensor 148b, and thus can determine how many degrees of rotation have been made with the common motor 128a. Only when the desired rotation is set with the common motor 128a, the control unit 131 again gives a signal to the second frequency converter 129b and the valve controller 155 to activate the hydraulic cylinder 150, so that the circular comb drive gear 132 again with the Abreisswalzen drive gear 130 is engaged. As a result, the rip-off roller movement 87 is now shifted in time relative to the pincer movement 134, as already associated with FIGS. 7 and 8 explained.

How out Fig. 10 recognizable, in contrast to Fig. 2 , the detachable roller auxiliary shaft 70 of the second drive train 68 is provided with an adjustment device 165. The adjusting device 165 has a sleeve 166 which is rotatably mounted on the Abreisswalzen auxiliary shaft 70 and releasably connected to the Abreisswalzen auxiliary shaft 70. The sleeve 166 is connected to the Abreisswalzen cam 80 via a drag. The adjustment device 165 is arranged outside the housing 60.

In Fig. 11 is an enlarged view of the adjustment device 165 according to Fig. 10 shown. The housing 60 is shown simplified only by the dashed line. For the dragging of the sleeve 166 with the Abreisswalzen-cam 80 is a the Abreisswalzen cam 80 facing the end of the sleeve 166 formed as an annular shoulder, wherein radially outside a plurality of receptacles 168 introduced are. The breaker cam 80 has inserted pins 170 which cooperate with the receptacles 168.

The breaker roll cam 80 is coupled to the break roll auxiliary shaft 70 via a spring pack 174, which creates a clamping effect when the sleeve 166 is stretched over the break roll auxiliary shaft 70 in the axial direction by a sleeve 166 projecting on the mandrel 176, the in the Abreisswalzen cam 80 inserted spring element pack 174 so displaced in a transverse position, so that presses on the spring element pack 174, the Abreisswalzen cam 80 against the Abreisswalzen auxiliary shaft 70. The sleeve 166 is connected to the Abreisswalzen auxiliary shaft 70 with screw 178, wherein one of the Abreisswalzen-cam 80 opposite end of the sleeve 166 blind hole-like holes 180, whereby the screw 178 reach through.

At the Abreisswalzen cam 80 facing away from the end of the sleeve 166, an annular receptacle 182 is formed, on which an adjusting plate 184 is detachably arranged. This causes a concealment of the screw 178, which are screwed into the blind hole-like holes 180. The adjusting disc 184 has on the periphery a pointer 186 which serves to indicate the position of the Abreisswalzen cam 80 relative to the Abreisswalzen auxiliary shaft 70 by means of a housing 60 mounted on the scale 188.

To monitor the presence of the adjusting disc 184 on the sleeve 166, a sensor 190, preferably a reed contact sensor, is provided on the housing 60. This is connected to a control unit, not shown, and thus indicates the operator of the combing machine, whether the adjusting disc 184 has been removed after adjustment

In Fig. 12 shown an alternative embodiment of the adjustment device 165, wherein the sleeve 166 is connected to the Abreisswalzen cam 80 via screw 178. The entrainment of the sleeve 166 with the Abreisswalzen cam 80 and the attachment of the sleeve 166 on the Abreisswalzen auxiliary shaft 70 are in the same manner as already in connection with Fig. 11 explained, executed. Also, the assembly of the adjusting disc 184 on the sleeve 166 and the pointer 186 on the circumference of the adjusting disc 184 for indicating the rotation of the Abreisswalzen cam 80 relative to the Abreisswalzen auxiliary shaft 70 via the scale 188 are formed the same. Similarly, the sensor 190 is disposed on the housing 60 to detect the presence of the adjustment disc 184.

Alternatively, the Abreisswalzen cam 80 may be releasably secured by means of a hydraulic clamping set on the Abreisswalzen auxiliary shaft 70. For this purpose, for example, a shrink disk of the HYD type from STÜWE could be used. In this connection, the shrinking disk HYD has a pressure chamber in which a hydraulic oil can be introduced via a hydraulic pump to enable a tensioning of the shrinking disk between the detaching roller cam and the detaching roller auxiliary shaft.

Legend

2

Kämmstelle

4

comber

10

Nipper unit (short tongs)

11

A nipper

12

front rocker

13

lower nipper

14

rear swingarm

16

Circular comb shaft

18

Front tongs shaft

20

Rear forceps shaft

22

Powered forceps shaft

24

feed cylinder

26

wadding

27

A nipper shaft

28

tuft

30

fiber end

32

non-woven fabric

34

detaching roller

36

comb segment

38

circular comb

40

extraction well

42

channel

44

Vacuum source

46

brush shaft

48

brush

50

bristles

51

Combination of transmission modules

52

First transmission module

54

Second gear module

56

Third gear module

58

Fourth transmission module

60

casing

62

First drivetrain

64

First drive shaft

66

Differential gear (tarpaulin gearbox)

68

Second drive train

70

Detaching auxiliary shaft

72

Detaching-cam device

74

ring gear

76

planet

78

sun

80

Detaching-cam

82

Detaching type Cam

84

Detaching rocker arm

86

planet carrier

87

Back and forth movement

92

Circular comb-auxiliary shaft

94

Circular comb differential gear

96

non-circular gear

98

Pliers cam device

100

Pliers auxiliary shaft

102

Pliers cam

104

Clamp follower

106

Pliers rocker

128

Common engine, drive motor

129

frequency converter

130

Detaching drive gear

131

control unit

132

Circular comb drive gear

133

step

134

Clamp drive gear

136

Intermediate gear

138

Motor auxiliary shaft

140

Motor intermediate gear

142

toothed belt

144

Motor-gear

146

motor shaft

148

Rotation angle sensor

150

hydraulic cylinders

152

hydraulic pump

154

way valve

155

valve controller

156

reservoir

158

Pump drive gear

160

Brush drive gear

162

Motor drive gear

164

belt

165

adjustment

166

shell

168

admission

170

spigot

174

Spring element Packet

176

mandrel

178

screw

180

blind hole-like holes

182

annular recording

184

adjusting disc

186

pointer

188

scale

190

sensor

Claims (13)

A combing machine drive apparatus comprising a transmission (51) driven by a main motor (128A), the transmission (51) comprising a ripper roll drive train for pilgrim movement of rip rollers (34), a ridge drive train for non-uniformly driving a ridge (16), and a pliers drive train for reciprocating a pliers unit (10), and wherein an operative connection between the main motor (128a) and the drive trains (70, 92, 100), characterized in that the Abreisswalzen drive train a Abreisswalzen- Auxiliary shaft (70) on which a first drive gear (130) sits non-rotatably, the circular comb drive train has a circular comb auxiliary shaft (92) rotatably on a second drive gear (132) sits, and the pliers drive train a pliers auxiliary shaft (100), on the rotationally fixed a third drive gear (134) sits, so that the operative connection between the main motor (128 a) and the first a drive gear (130) and between the second drive gear (132) and the first drive gear (130) and between the third drive gear (134) and the second drive gear (132) is provided, wherein a device for separating the operative connection between the second drive gear ( 132) and the first drive gear (130) by a displacement of the second drive gear (132) or the circular comb auxiliary shaft (92) in the direction of a longitudinal axis of the circular comb auxiliary shaft (92) is provided. Drive device according to claim 1, characterized in that a rotation of the Abreisswalzen auxiliary shaft (70) relative to the circular comb auxiliary shaft (92) by the main motor (128a) after separation of the operative connection between the second drive gear (132) and the first drive gear (130) is provided. Drive device according to claim 2, characterized in that the rotation of the Abreisswalzen auxiliary shaft (70) is provided in steps of 0.9 ° to 4.5 °. Drive device according to one of claims 1 to 3, characterized in that the second drive gear (132) and the third drive gear (134) are formed such that the displacement of the second drive gear (132) or the circular comb auxiliary shaft (92) no release of Actuated connection between the third drive gear (134) and the second drive gear (132) causes. Drive device according to one of claims 1 to 4, characterized in that the device for displacing the second drive gear (132) or the circular comb auxiliary shaft (92) has a hydraulic, electrical or mechanical drive. Drive device according to claim 5, characterized in that a hydraulic cylinder (150) is provided as the hydraulic drive, which is connected to the circular comb auxiliary shaft (92) or the second drive gear (132). Drive device according to one of claims 1 to 6, characterized in that a first rotation angle sensor (148a) on the Abreisswalzen auxiliary shaft (70) and a second rotation angle sensor (148b) on the forceps auxiliary shaft (100) is provided Drive device according to claim 7, characterized in that a control unit (131) is provided, which with the main motor (128a) and the device for shifting the second drive gear (132) or the circular comb auxiliary shaft (92) and the rotation angle sensors (148a, 148b ) connected is. Drive device according to claim 8, characterized in that the rotation of the Abreisswalzen auxiliary shaft (70) by a predetermined value by the control unit (131) in conjunction with the main motor (128a) is provided, via the control unit (131) a comparison of the first Rotation angle sensor (148a) with the second rotation angle sensor (148b) is provided. Drive device according to claim 9, characterized in that the control unit (131) has in a memory reference data for the second rotation angle sensor (148b) and / or for the rotation. Combing machine with a drive device for a transmission according to one of claims 1 to 10. A method for adjusting a combing machine having a drive device with a gear (51) driven by a frequency-controlled main motor (128) with a stripping roller drive train for pilgrim movement of a stripping roller (34) with a first drive gear (130) on a stripping roller auxiliary shaft (70), comprising a circular comb drive train for non-uniformly driving a circular comb (16) with a second drive gear (132) on a circular comb auxiliary shaft (92) and a pliers drive train for reciprocating a nipper assembly (10) with a third drive gear (134) on a pliers auxiliary shaft (100), wherein an operative connection between the main motor (128a) and the drive wheels (130, 132, 134), whereby the first drive gear (130) through the main motor (128a) and the second drive gear (132) driven by the first drive gear (130) and the third drive gear (134) by the second drive gear (132), characterized by the following process steps: - stopping the drive device, - Displacement of the second drive gear (132) on the circular comb auxiliary shaft (92) or the circular comb auxiliary shaft (92) in the direction of a longitudinal axis of the circular comb auxiliary shaft (92) for separating the operative connection between the first drive gear (130) and the second drive gear (132) Twisting the stripping roller auxiliary shaft (70) against the circular comb auxiliary shaft (92) and the pliers auxiliary shaft (100) with the main motor (128a), - Displacement of the second drive gear (132) on the circular comb auxiliary shaft (92) or the circular comb auxiliary shaft (92) in the direction of a longitudinal axis of the circular comb auxiliary shaft (92) for restoring the operative connection between the first drive gear (130) and the second drive gear (132). A method according to claim 12, characterized in that during the displacement of the second drive gear (132) on the circular comb auxiliary shaft (92) or the circular comb auxiliary shaft (92) in the direction of a longitudinal axis of the circular comb auxiliary shaft (92) the operative connection between the second drive gear (132) and the third drive gear (134) is not disconnected.

Images