EP3514272A1 - Drive device for detaching rollers of a comber - Google Patents

Abstract

The invention relates to a drive device for tear-off rollers (34) of a comber (4) with a housing (60a) enclosing a gear (51a), the gear (51a) having a first drive train (62) with a first drive shaft (64), which transmits a continuous rotary movement to the tear-off rollers (34) via a ring gear (74) of a differential gear (66) and wherein the gear (51a) has a second drive train (68) with a tear-off roller auxiliary shaft (70), on which a tear-off roller Cam device (72) is arranged to generate a forward and backward movement, the continuous rotary movement of the ring gear (74) together with the forward and backward movement of the tear-off roller cam device (72) transmitting a pilgrim step movement to the tear-off rollers (34) , According to the invention, an adjusting device (158) is provided for setting a transmission ratio between the continuous rotary movement and the forward and backward movement.

Description

The present invention relates to a drive device for Abreisswalzen a combing machine with a gear enclosing housing, wherein the transmission has a first drive train with a first drive shaft which transmits via a differential gear a continuous rotational movement on the Abreisswalzen and wherein the transmission a second drive train with a Abreisswalzen Auxiliary shaft on which a Abreisswalzen-cam plate device for generating a forward and backward movement is arranged, wherein the continuous rotational movement of the differential gear together with the back and forth movement of the Abreisswalzen cam device transmits a pilgrim movement on the Abreisswalzen.

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 tuft. 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, in order to solder a fiber end which has already been combed out and clamped by the tear-off rollers to a fiber end combed out of the round comb. 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 tear-off rollers.

The soldering of the fiber bundles to the desired sliver has in particular the requirement that the roof-like stacked fiber packets 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.

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.

Proposed is a drive device for Abreisswalzen a combing machine with a gear enclosing housing, wherein the transmission has a first drive train with a first drive shaft which transmits a ring gear of the differential gear continuous rotational movement on the Abreisswalzen and wherein the transmission a second drive train with a Abreisswalzen Auxiliary shaft, on which a Abreisswalzen-cam plate device for generating a forward and backward movement is arranged, wherein the continuous rotational movement of the ring gear together with the back and forth movement of the Abreisswalzen-cam plate device transmits a pilgrim movement on the tear-off rollers.

According to the invention, an adjusting device is provided for setting a transmission ratio between the continuous rotational movement and the forward and backward movement. The continuous rotational movement caused by the ring gear of the differential gear causes a transmission of a linear motion on the Abreisswalzen and the Abreisswalzen cam device transmits a forward and backward movement to the differential gear, wherein the combination of the linear movement in connection with the back and forth movement a resulting pilgrim movement transfers to the tear-off rollers. Here, the ring gear of the differential gear on a gear ratio, which defines the linear movement, which is transmitted to the Abreisswalzen. Accordingly, the inventive adjustment allows a change in the linear movement through the ring gear of the differential gear by adjusting the gear ratio, the back and forth movement caused by the Abreisswalzen cam device remains unchanged. This has the advantageous effect that the tear-off rolls, depending on the set transmission ratio, supplies the end of the fiber fleece to the combed fiber end sooner or later in time for the soldering operation. This in turn means that the soldering distance, ie the area which is not overlapping, becomes larger or smaller. Thus, advantageously, depending on the fiber mass presented, the soldering distance can be set variably, whereby the yarn quality is not adversely affected, since the fiber tips do not have to be transferred at any time, as is the case in the prior art, in order to ensure optimum uniformity of the yarn To get Bandes.

Preferably, the first drive shaft of the first drive train, a first pulley and the Abreisswalzen auxiliary shaft of the second drive train or a drive connected to the Abreisswalzen auxiliary shaft motor auxiliary shaft on a second toothed belt, wherein the two toothed belt wheels are guided through the housing to the outside of the housing and in connection with a toothed belt are connected to a motor and the adjusting device is designed such that the setting of the transmission ratio is effected by the first toothed belt is formed as a Wechselzahnriemenrad.

Alternatively, the Abreisswalzen auxiliary shaft for the forward and backward movement via a first drive motor and independently of the first drive shaft for the ring gear of the differential gear via a second drive motor are driven, wherein the adjustment device is formed by the second drive motor.

Particularly preferably, the setting of the transmission ratio is infinitely variable.

More preferably, the second drive motor is a servomotor with a servo amplifier.

Particularly preferably, the setting of the transmission ratio between 2.25 and 3.8 is provided. By adjusting the transmission ratio of the differential gear, the linear movement of the ring gear can rotate faster or slower, so that in conjunction with the back and forth movement of the Abreisswalzen-cam plate device, an optimal soldering distance can be adjusted.

Preferably, the second drive motor is synchronized via a control unit with the first drive motor. The synchronization is advantageous so that the forward and backward movement caused by the Abreisswalzen cam plate device and the linear movement caused by the differential gear are optimally matched.

More preferably, the differential gear is a planetary gear, wherein the first drive train via the ring gear in conjunction with Planentenrädern drives a sun gear to transmit the continuous rotational movement of the ring gear on the Abreisswalzen and independently formed the forward and backward movement by the Abreisswalzen-cam plate device wherein the Abreisswalzen-cam plate device comprises at least one on the Abreisswalzen auxiliary shaft rotatably arranged Abreisswalzen-cam in interaction with at least one Abreisswalzen cam roller, and wherein the Abreisswalzen cam roller cooperates via a Abreisswalzen rocker arm with a planet carrier of the planetary gear.

Particularly preferably, in addition to adjusting the transmission ratio between the Abreisswalzen-cam disk device and the ring gear of the differential gear and a manual or automatic rotation of the Abreisswalzen-cam relative to the Abreisswalzen auxiliary shaft is provided. This combination of settings has the advantage that a better yarn quality can be achieved than in known combers and a higher reliability is given because failures due to unevenness in the band can be excluded.

Furthermore, according to the invention, a combing machine with a drive device for detaching rollers of a combing machine is provided.

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 vier Getriebe-Modulen mit einem gemeinsamen Motor;

Fig. 3

eine weitere Ausführung einer Kombination von Getriebe-Modulen;

Fig. 4

vier Getriebe-Module, wobei jedes Getriebe-Modul einen eigenen Antriebsmotor aufweist;

Fig. 5

vergrösserte Darstellung einer Zange und nachgeschalteter Abreisswalzen gemäss Fig. 1;

Fig. 6

eine schematische Darstellung der Faservliesbildung im Bereich der Abreisswalzen;

Fig. 7

eine graphische Darstellung einer Abreisswalzen-KurvenscheibenVorrichtung;

Fig. 8

eine graphische Darstellung einer Vor- und Zurückbewegung;

Fig. 9

eine graphische Darstellung von drei verschiedenen Linearbewegungen eines Differentialgetriebes;

Fig. 10

eine graphische Darstellung von drei verschiedenen resultierenden Pilgerschrittbewegung als Überlagerung der Vor- und Zurückbewegung gemäss Fig. 8 in Verbindung mit den drei verschiedenen Linearbewegungen des Differentialgetriebes gemäss Fig. 9

Fig. 11

eine erfindungsgemässe Einstellung eines Lötabstandes durch Wechselräder;

Fig. 12

eine weitere erfindungsgemässe Einstellung des Lötabstandes durch einen frequenzgesteuerten Motor.

Show it:

Fig. 1

a cross section through a comber;

Fig. 2

a combination of four transmission modules with a common engine;

Fig. 3

another embodiment of a combination of transmission modules;

Fig. 4

four transmission modules, each transmission module having its own drive motor;

Fig. 5

enlarged view of a pair of pliers and downstream pull-off rollers according to Fig. 1 ;

Fig. 6

a schematic representation of the fiber web formation in the region of the tear-off rollers;

Fig. 7

a graphical representation of a Abreisswalzen cam device;

Fig. 8

a graphic representation of a back and forth movement;

Fig. 9

a graphical representation of three different linear movements of a differential gear;

Fig. 10

a graphic representation of three different resulting pilgrim step movement as a superposition of the forward and backward movement according to Fig. 8 in conjunction with the three different linear movements of the differential gear according to Fig. 9

Fig. 11

an inventive setting a soldering distance by change wheels;

Fig. 12

a further inventive setting of the soldering distance by a frequency-controlled motor.

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 rotatably mounted on a circular comb shaft 16 and 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, that is, a collet 11 is pivotally mounted relative to a lower jaw 13 via a upper jaw pin 25 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 tuft 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 located during the combing process in an upper Position. 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. A portion of the combed material is transferred by 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 ), a third gear 56 for reciprocating the pliers 10 (see Fig. 1 ) and a fourth gear 58 for opening and closing the upper nipper 11 (see Fig. 1 ) intended. The four transmissions 52, 54, 56, 58 are provided in a module construction, wherein the combination 51 of the four transmission modules 52, 54, 56, 58 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 a pull roll cam device 72 is arranged to generate a forward and backward movement 87.

The differential gear 66 is formed as a planetary gear, wherein the first drive train 62 via the ring gear 74 in conjunction with Planentenrädern 76 drives a sun gear 78 to transmit the continuous rotational movement of the ring gear 74 to the tear-off rollers 34. Independently of this, the forward and backward movement 87 is formed by the breakaway roll cam device 72, the pull roll roll plate device 72 having two breakaway roll cams 80 rotatably mounted on the break roll auxiliary shaft 70 that interact with two pull roll cams 82 cooperate. The two Abreisswalzen cam rollers 82 are connected via a Abreisswalzen rocker arm 84 with a planet carrier 86 of the differential gear 66, so that the forward and backward movement 87 of the Abreisswalzen cams 80 is superimposed on the planet carrier 86 with the continuous rotational movement of the ring gear 74 to to transmit a pilgrim movement on the tear-off rollers 34.

The first drive train 62 is drive-connected according to the present embodiment with a table calender 88 and with transport rollers 90, and is in this way a part of the first gear module 52. It is of course also possible Tischkalander 88 and transport rollers 90 via a separate Drive powertrain.

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 change the natural frequency by stiffening the Minimize round comb shafts. 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.

The fourth transmission module 58 is for the opening and closing of the upper nipper 11 (see Fig. 1 ) is formed with an upper nipper cam device 108, wherein in the embodiment according to Fig. 2 the upper nipper cam 108 has two upper nipper cams 110 rotatably mounted on the nipper auxiliary shaft 100 (only one shown) that interact with two upper nib followers 112 (only one shown). The two top caliper rollers 112 are rotatably mounted via a screw connection to a top caliper rocker arm 114, wherein the top caliper rocker arm 114 is connected via a coupling rod 116 in conjunction with an upper nipper shaft clamp 118 with the upper nipper shaft 27. The upper nipper rocker arm 114 and the upper nipper shaft clamp 118 are connected by screw 122 with the coupling rod 116, wherein the coupling rod 116 is formed of three elements 116 a, 116 b, 116 c and so the tongs auxiliary shaft 100 via a four-joint 124 with the Upper tongs shaft 27 connects.

In the embodiment according to Fig. 2 the combination 51 of transmission modules 52, 54, 56, 58 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. This has an advantage, in particular, when a transmission module or a combination of at least two transmission modules are arranged between two groups of combing points, such as, for example, later in FIG Fig. 6 explained in more detail. 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 (e.g., 70, 92, 100) with constant combing machine speed, at least one sensor in the form of a speed sensor (incremental with reference or absolute) is mounted outside the housing 60.

In the present embodiment, a control unit 131 is connected to a first sensor 133a, a second sensor 133b and a frequency converter 129, wherein the frequency converter 129 drives the common motor 128.

The first sensor 133a is a speed sensor and mounted outside of the housing 60 on the pliers auxiliary shaft 100 to determine the absolute machine position.

The second sensor 133b is preferably an induction sensor or tachometer and mounted outside of the housing 60 on the rear tongs shaft 22. The second sensor 133b is adapted to the distance of the lower nipper 13 in the front end position according to Fig. 1 to determine the Abwalwalzen 34, which is the so-called Ecartement in combing machines.

Fig. 3 11 shows an exemplary embodiment of a first combination 51a with the first gear module 52 for the pilgrim movement of the tear-off rollers 34 and the second gear module 54 for non-uniform movement of the circular comb shaft 16, wherein the gear modules 52, 54 are enclosed by a first housing 60a are. A first frequency converter 129a in conjunction with a first drive motor 128a is connected to the first combination 51a in the same manner as in FIG Fig. 2 described drive-connected.

The third gear module 56 for the reciprocating motion of the driven forceps shaft 22 and the fourth transmission module 58 for the movement of the upper forceps shaft 27 are combined in a second combination 51b and enclosed by a second housing 60b. The pliers auxiliary shaft 100 is passed through the second housing 60b and externally connected directly to a second drive motor 128b. The forceps cam device 98 and the top caliper device 108 are disposed in the same manner on the forceps auxiliary shaft 100 as previously associated with FIG Fig. 2 described.

The first drive motor 128a and the second drive motor 128b are synchronized with each other via the control unit 131, the drive motors 128a, 128b being asynchronous motors drivingly connected to a corresponding frequency converter 129a, 129b.

In an alternative embodiment, the drive motors 128a, 128b are servomotors, each in communication with a servo amplifier 129a, 129b.

The circular comb auxiliary shaft 92 is guided by the housing 60a to the outside and a third sensor 133c in the form of a speed sensor is mounted outside the housing 60a on the circular comb auxiliary shaft 92. The third sensor 133c is drivingly connected to the control unit 131 and has the task of transmitting the rotational position of the circular comb auxiliary shaft 92 to the control unit 131, so that via the control unit 131 the second frequency converter 129b in conjunction with the second drive motor 128b, the position of the forceps 10 and the upper nipper 11 with respect to the rotational position of the Abreisswalzen 34 and the circular comb auxiliary shaft 92 can set optimally for the combing process and soldering.

In contrast to the embodiment according to Fig. 2 is in Fig. 4 each individual transmission module 52, 54, 56, 58 enclosed by a respective housing 60c, 60d, 60e, 60f. The first transmission module 52 for generating the pilgrim movement for the tear-off rollers 34 and the second transmission module 54 for non-uniformly driving the circular comb shaft 16 are formed in the same manner as in FIG Fig. 2 described.

In the embodiment according to Fig. 4 For example, when the pliers auxiliary shaft 100 is provided only for the plier cam device 98, and the pliers cam device 108 is provided with an upper pliers auxiliary shaft 148.

The third transmission module 56 with the pliers-cam device 98 according to the embodiment in Fig. 4 has two pliers cam disks 102 rotatably mounted on the pliers auxiliary shaft 100 (only one shown) which cooperate with two pliers cam rollers 104 (only one shown). The two pincer rollers 104 are connected via the pincer rocker arm 106 with the driven pincer axis 22, so that the movement profile, in particular the reciprocating movement of the pincer cams 102 on the forceps 10 (see Fig. 1 ) is transmitted.

The fourth transmission module 58 with the upper nipper cam device 108 according to the embodiment in Fig. 4 has two upper nipper cams 110 rotatably mounted on the upper nipper auxiliary shaft 148 (only one shown) interacting with two upper nib rollers 112 (only one shown). The two upper nipper cam rollers 112 are directly connected to the upper nipper shaft 27 via the upper nipper rocker arm 114, so that the movement profile, in particular the reciprocating movement of the upper nipper cam disks 110 on the upper nipper 11 (see Fig. 1 ) is transmitted.

In the embodiment according to Fig. 4 is the Abreisswalzen auxiliary shaft 70 of the second drive train 68 through the housing 60c, the circular comb auxiliary shaft 92 through the housing 60d, the pliers auxiliary shaft 100 through the housing 60e and the upper caliper auxiliary shaft 148 through the housing 60f to outside the housing 60c, 60d, 60e, 60f where the respective auxiliary shaft 70, 92, 100, 148 in the form of a drive shaft of a corresponding outside of the housing 60c, 60d, 60e, 60f arranged drive motor 128c, 128d, 128e, 128f are driven. The drive motors 128c, 128d, 128e, 128f are asynchronous motors or, alternatively, servomotors which are respectively driven by a frequency converter or alternatively servo amplifiers 129c, 129d, 129e, 129f, the drive motors 128c, 128d, 128e, 128f being synchronized with each other via the control unit 131 , In this way, the drive motors 128c, 128d, 128f in conjunction with the respective cam devices 72, 98, 108 can continuously adjust the desired gear ratio to the puller rollers 34, the driven tong shaft 22, and the upper tong shaft 27.

In Fig. 5 is enlarged, the pliers 10 and downstream of the Abreisswalzenpaar 34 according Fig. 1 shown, wherein in a known manner, the combed fiber package 28 is fed 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 forward and backward movement 87 as in Fig. 2 described perform. 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. As a result, this leads to a roof tile-like structure of the fiber fleece 32, as in FIG Fig. 6 very simplified and shown schematically. Each fiber packet 28 supplied by the forceps 10 is attached to the free end 30 of the nonwoven fabric 32 and connected to each other via the pilgrim movement of the tear-off rollers 34, this process being generally referred to as soldering.

According to Fig. 6 In the case of the roof-tile-like construction of the fiber fleece 32, there is an overlapping region 150 between the end 30 of the fiber fleece 32 and the combed fiber end 28 and a non-overlapping region 152, where no overlap exists between these two fiber ends 28, 30. With the rip-off roller cam device 72, as related to Fig. 2 described in detail, the Abreisswalzen movement 87 is adjustable, so that the non-overlapping area 152, which is referred to as a so-called soldering distance, can be precisely defined. The variable setting of the soldering distance has the advantage that an optimal uniformity of the fiber fleece 32 can be achieved. In this case, it is particularly important that no fiber tips must be transferred in order to achieve a convenient Geleichmässigkeit the nonwoven fabric 32. In this context, it should be mentioned that although a metrically deep unevenness could be achieved, the fiber tips would have to be transferred for this purpose, which would, however, be a considerable disadvantage for the yarn quality. A significant advantage for the variable setting of the soldering distance is the fact that the tearing and soldering process can be adapted to different staple lengths.

According to Fig. 7 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. The mechanical connection of the respective cam roller 82a, 82b with the detachable roller auxiliary shaft 70, a Abreisswalzen movement profile 87 of the Abreisswalzen cam 80 transferred to the Abreisswalzen 34, as related to Fig. 2 executed in detail.

In Fig. 8 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. 5 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 tear-off roller movement pattern corresponds to the forward and backward movement 87 for the tear-off rollers, which is caused by the tear-off roller cam device 72.

Fig. 9 purely schematically illustrates a first linear movement 154 caused by the ring gear 74 of the differential gear 66 according to Fig. 2 and Fig. 10 shows a first resulting pilgrim movement 156 on the tear-off rollers 34 caused by the forward and backward movement 87 according to Fig. 8 in conjunction with the first linear movement 154 according to Fig. 9 ,

With a constant forward and backward movement 87 according to Fig. 8 and change the linear motion 154a (dashed), 154b (dotted) as well as in FIG Fig. 9 As shown in FIG. 14, modified resulting pilgrim stepping 156a (dashed), 156b (dotted) results as well as in FIG Fig. 10 shown. In this context, the steeper the course of the linear movement 154, the greater the soldering distance 152 according to Fig. 6 be set and vice versa. In Fig. 10 Correlated solder spacings 152, 152a, 152b are plotted as a function of the resulting pilgrim step movements 156, 156a, 156b. In this way, thus, the desired soldering distance 152 can be adjusted via the resulting pilgrim step movement 156, whereby an optimal uniformity for the nonwoven fabric 32 is obtained without shifting the fiber tips for this purpose, as is the case in the known prior art.

Fig. 11 shows a first transmission module 51a according to the invention in comparison to Fig. 3 for the in Fig. 10 shown resulting pilgrim movement 156 of the tear-off rollers 34, wherein the first drive train 62 for the inventive variable soldering distance 152 in comparison to the embodiments according to FIGS Fig. 2 . Fig. 3 and Fig. 4 is adjusted.

According to Fig. 11 an adjusting device 158 is provided for adjusting a transmission ratio between the continuous rotational movement, in the sense of the linear movement 154 of the ring gear 74 of the differential gear 66 and the forward and backward movement 87 caused by the Abreisswalzen cam plate device 72nd

In a preferred embodiment of the present invention, as in Fig. 11 1, the first drive shaft 64 is connected to an adjustment shaft 164 via a connecting wheel 160 and a double gear 162a, 162b arranged on a rotation axis 161, wherein the adjustment shaft 164 is guided through the housing 60a to outside the housing 60a and there rotatably a first toothed belt wheel 166 is attached. The adjusting shaft 164 has an outer toothing 168, so that a first part 162a of the double gear interacts with the outer toothing 168 and a second part 162b of the double gear interacts with the connecting wheel 160. On the detachable roller auxiliary shaft 70 of the second drive train 68, the stripping roller drive gear 130 is fixed against rotation with an intermediate gear 136 engaged with the detaching roller drive gear 130 being fixed for rotation on the motor auxiliary shaft 138 and the motor assist shaft 138 The motor idler gear 140 and the first toothed belt wheel 166 are drive-connected via the toothed belt 142 to the motor gear 144, the motor gear 144 being fixed against rotation on the motor shaft 146 of the motor 128a is attached. Preferably, the motor 128a is connected via a frequency converter 129a to a control unit, not shown.

The adjusting device 158 according to the invention is designed in such a way that the setting of a transmission ratio is effected by the first toothed belt wheel 166 is a change gear pulley (shown in phantom). Preferably, an adjustment of the transmission ratio between 2.25 and 3.8 is provided with the change gear pulleys. The changed gear ratio causes a change in the continuous linear motion 154 of the ring gear 74, as in FIG Fig. 9 explained.

According to Fig. 12 is the adjuster 158 compared to Fig. 11 not formed with a Wechselzahnriemenrad but outside the housing 60a, a frequency converter 129g is connected in conjunction with an asynchronous motor 128g with the adjusting shaft 164. Preferably, with the frequency converter 129g in conjunction with the asynchronous motor 128g and the control unit 131, the setting of the transmission ratio continuously between 2.25 and 3.8 possible. As already in Fig. 3 3, the third sensor 133c in the form of the speed sensor is mounted outside the housing 60a on the circular comb auxiliary shaft 92 and connected to the control unit 131. In this way, the speed of the circular comb and the variable setting of the soldering distance on the tear-off rollers can be optimally matched. All other elements are identical as related to Fig. 11 described.

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 axis

20

Rear pliers axis

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

88

Tischkalander

90

transport rollers

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

108

Upper tong cam device

110

A nipper-cam

112

Upper Clamp follower

114

Upper Clamp rocker

116

Coupling rod (three elements)

118

A nipper shaft bracket

122

screw

124

Four joint

128

Common engine, drive motor

129

frequency converter

130

Detaching drive gear

131

control unit

132

Circular comb drive gear

133

Sensor (speed sensor)

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

Upper Clamp auxiliary shaft

150

Covering area

152

Coverless area

154

First linear movement (soldering distance)

156

First resulting pilgrim step movement

158

adjustment

160

connection gear

161

axis of rotation

162

double gear

164

adjusting

166

First toothed belt wheel

168

external teeth

Claims (10)

Drive device for tear-off rollers (34) of a combing machine (4) with a housing (60a) enclosing a transmission (51a), wherein the transmission (51a) has a first drive train (62) with a first drive shaft (64) which is driven via a ring gear (51). 74) of a differential gear (66) transmits a continuous rotational movement to the tear-off rollers (34) and wherein the gearbox (51a) has a second drive train (68) with a tear-off roller auxiliary shaft (70) on which a tear-off roller cam device (72 ) is arranged to produce a forward and backward movement, wherein the continuous rotational movement of the ring gear (74) together with the forward and backward movement of the Abreisswalzen cam device (72) transmits a pilgrim movement on the Abreisswalzen (34), characterized in that an adjusting device (158) is provided for setting a transmission ratio between the continuous rotational movement and the V movement back and forth. Drive device according to claim 1, characterized in that the first drive shaft (64) of the first drive train (62) comprises a first toothed belt wheel (166) and the Abreisswalzen auxiliary shaft (70) of the second drive train (68) or one with the Abreisswalzen auxiliary shaft (70 ) drive-connected motor auxiliary shaft (138) have a second toothed belt wheel (140), wherein the two toothed belt wheels (166, 140) each through the housing (60 a) to outside of the housing (60 a) are guided and in conjunction with a toothed belt (142 ) are connected to a motor (128a) and the adjusting device is designed such that the setting of the transmission ratio is effected by the first toothed belt wheel (166) is designed as Wechselzahnriemenrad. Drive device according to claim 1, characterized in that the Abreisswalzen auxiliary shaft (70) for the forward and backward movement via a first drive motor (128a) and independently the first drive shaft (64) for the ring gear (74) of the differential gear (66) via a second drive motor (128g), wherein the adjusting device (158) is formed by the second drive motor (128g). Drive device according to claim 3, characterized in that the setting of the transmission ratio is infinitely variable. Drive device according to claim 4, characterized in that the second drive motor (128g) is a servomotor with a servo amplifier (129g). Drive device according to one of claims 1 to 5, characterized in that the setting of the transmission ratio between 2.25 and 3.8 is provided. Drive device according to one of claims 4 to 6, characterized in that the second drive motor (128g) via a control unit (131) with the first drive motor (128a) is synchronized. Drive device according to claim 1, characterized in that the differential gear (66) is a planetary gear, wherein the first drive train (62) via the ring gear (74) in conjunction with Planentenrädern (76) drives a sun gear (78) to the continuous rotational movement of Irrespective of this, the forward and backward movement is formed by the breakaway roll cam device (72), wherein the breakaway roll cam device (72) has at least one on the break roll auxiliary shaft (70) rotationally fixed Abreisswalzen cam disc (80) interacts with at least one Abreisswalzen cam roller (82), and wherein the Abreisswalzen cam follower (82) via a Abreisswalzen rocker arm (84) with a tarpaulin support (86) of the planetary gear ( 66) cooperates. Drive device according to claim 2 and 8, characterized in that in addition to adjusting the transmission ratio between the Abreisswalzen-cam plate device (72) and the ring gear (74) of the differential gear (66) and a manual or automatic rotation of the Abreisswalzen-cam (80) is provided opposite the detaching roller auxiliary shaft (70). Combing machine with a drive device according to one of claims 1 to 9.

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